EP1492674A1

EP1492674A1 - Characterization, detection of a reference number, and selection of suitable winding materials for rollers of a printing press

Info

Publication number: EP1492674A1
Application number: EP02762256A
Authority: EP
Inventors: Karl Erich Albert Schaschek; Ralf Christel; Oliver Frank Hahn; Bernd Kurt Masuch; Kurt Johannes Weschenfelder
Original assignee: Koenig and Bauer AG
Current assignee: Koenig and Bauer AG
Priority date: 2002-04-11
Filing date: 2002-08-28
Publication date: 2005-01-05
Anticipated expiration: 2022-08-28
Also published as: RU2004106149A; DE10296772D2; EP1492674B1; DE50214420D1; AU2002328265A1; CN1575234A; DE20213169U1; RU2291058C2; ATE466729T1; WO2003086760A1; JP2005519794A

Abstract

Disclosed are a method for characterizing a layer (06), a method and a device for detecting a reference number, and a method for selecting a suitable layer to be applied to rollers (01, 02, 11, 12 16) or for selecting suitable roller geometries of a printing press, according to which a reference number characterizing the layer is formed or used. Said reference number characterizes the unwinding behavior independently of a measuring device or an application in a special printing unit.

Description

description

Characterization, determination of a key figure and selection of suitable lifts on rollers of a printing press

The invention relates to a method for characterization, a method and a device for determining a characteristic number, and a method for selecting suitable lifts on rollers or suitable geometries of rollers of a printing press according to the preamble of claims 1, 4, 6, 8, 24 and 26th

In printing presses, in particular in rotary printing presses, color is applied between one or more rollers of an inking unit, between the inking unit and printing unit cylinders, possibly between printing unit cylinders and from a printing unit cylinder against a counter-pressure cylinder (hereinafter referred to as rollers) on a web, e.g. B. paper web, applied. For this purpose, the transfer of the color of two adjacent rollers, which possibly interact via the web, preferably takes place in each case between a roller with a “hard ^” surface and a roller with a “wefcher ^” surface.

Since a certain surface pressure is required for the ink transfer, at least the roller with a soft surface experiences a deformation in the area thereof. This deformation of the z. B. as an elastomeric cover (elevator, rubber blanket, metal printing blanket, sleeve, coating) soft surface causes a change depending on the material behavior and size of an indentation (e.g. due to the distance between the rollers, different thicknesses of the web, etc.) the effective diameter of this roller when rolling on the cooperating roller, ie it leads to changes in the surface pressure and in the development. In the case of mechanically or electronically synchronized driven rollers, this can lead to different surface speeds depending on the material used and the indentation and thus to slippage in the nip point. The slip that arises in this way results in a tangential force component as a result of friction and therefore reduced print quality (pushing, doubling), a disruptive power transmission and a reduced service life of printing forms or elevators.

DE 43 15456 A1 discloses a printing blanket which has an incompressible and a compressible elastomeric layer, the latter increasing the tolerances in the printing process. With an optimized layer structure, it is achieved that in certain provision areas of the interacting cylinders there is almost no change in surface length, i. H. a difference in the angle of rotation of two cylinders rolling on each other is independent of the indentation in these areas. The angle of rotation difference can be determined on the basis of a laboratory model for different elevators and different accessories, a driven first cylinder and a free-running, and the elevator-containing second cylinder being placed against one another.

In an article published by the applicant as part of the TAGA Proceedings 2001 on page 211 with the title "The effect of printing blankets on the rolli conditiong condition of printing cylinders", a key figure for characterizing the rolling behavior of an elastic elevator is known. This enables the designer to A device for determining the rolling behavior has an externally driven and a friction-driven roller, the angular speeds of which can be measured by opto-electronic angle decoders.

The invention has for its object to provide a method for characterization, a method and a device for determining a characteristic number, and methods for selecting suitable lifts on rollers or suitable geometries of rollers of a printing press. The object is achieved by the features of claim 1, 4, 6, 8, 24 and 26 respectively.

The advantages that can be achieved with the invention consist in particular in that a quantitative description of the elevators with regard to their conveying or rolling behavior is made possible, and that the marking thus generated is independent of a geometry of a measuring device and of a geometry of a printing unit. The characteristic number used to characterize the elevator is adjusted for the specific geometries and can be applied alternately to a measuring device or the printing unit. The description is no longer purely qualitative (e.g. positive, negative), but can be used quantitatively.

The method for characterizing an elevator on the basis of the characteristic number creates a clearly defined language between the manufacturer of the elevators and the designer of the printing press, which on the one hand provides a tailor-made design of the printing press when desired. predetermined elevator, and on the other hand allows a targeted selection of an elevator for a predetermined configuration of the printing press. Both can be clarified in advance, a complicated test program that would otherwise have to be carried out on the printing press for the special configuration and each type of elevator can be omitted.

An advantageous solution is therefore to select an elevator for a given pair of cylinders in such a way that when it is pressed in, because of its incompressible portion, it extends to such an extent that the reduced distance to the pivot point is just being compensated for. Such a requirement can be determined by means of the method and a corresponding elevator can be selected.

Conversely, it is therefore advantageous to select the geometry of the printing unit for a specific, given elevator such that it is more variable at least in one area Indentation the rolling behavior does not depend or only depends to a small extent on the indentation.

The measured values required to form the key figure are, for. B. determined by means of a measuring device having two rollers. To measure the distance or the change in distance (indentation), the measuring device advantageously has a lever that translates the adjustment movement. A higher transmission ratio can also be achieved via an eccentric which moves the cylinder, the lever being rigidly connected to the bearing ring to be pivoted.

The key figure obtained for an elevator can be applied to a wide variety of printing unit configurations and is independent of the geometry of the measuring device used. Only the algebraic rule between geometry and key figure has to be defined and known.

Another advantage is the option of configuring a printing unit that is optimized with regard to the rolling behavior. For example, a transfer cylinder of double circumference with an elevator with a code number α from 0.989 to 0.999, a transfer cylinder with a single circumference with an elevator with code number α from 0.980 to 0.995, is designed if it cooperates with an impression cylinder in each case of essentially the same size. The specified key figures α must be observed for a relative indentation in at least one area that is relevant in practice.

The above-mentioned design of the printing unit is particularly advantageous in the case of transmission and impression cylinders which are driven independently of one another. This minimizes the engine load, engine design and control effort.

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

Fig. 1 passage of a compressible rubber blanket through the nip;

Fig. 2 passage of an incompressible rubber blanket through the nip;

3 measured transmission ratios with variation of the press-in;

Fig. 4 Qualitative representation of the gear ratios;

Fig. 5 embodiment for a printing unit;

Fig. 6 embodiment for a printing unit;

Fig. 7 embodiment for a printing unit;

Fig. 8 embodiment for a printing unit;

Fig. 9 embodiment of a measuring device;

10 Detailed side view according to FIG. 9.

A work machine, e.g. B. a printing press, has rolls rolling on each other 01; 02, which form a roller gap 03 in the area of their contact. 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 FIGS. 1 and 2, the cylinders 01; 02 represents a forme cylinder 01 with an effective diameter D _wP2 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 _wG zκ a soft, elastomeric layer 06 with a thickness t. The core 04 and layer 06 together form an effective diameter D _wG z 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 rolling and possibly includes a printing form (not shown) applied to the outer surface of a base body. The cylinder 01 with a hard surface can also be designed as an impression cylinder 01 which interacts with the transfer cylinder 02.

Depending on the provision of the two cylinders 01; 02, d. H. their axial spacing "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. This indentation S causes the above-mentioned problems in the development of the two cylinders 01; 02, depending on the material properties (compressible and / or elastic behavior) of layer 06.

The present invention is based on the approach of providing a description, independent of the specific applications or measuring devices, for the roll-off device, such a layer 06, on the basis of which a suitable layer 06 is selected, or a dimensioning of the rollers 01; 02 can be made. Assuming an ideally compressible layer 06 (e.g. cork or the like) and an ideally incompressible layer 06 (e.g. solid rubber), the limits for the development behavior can be set. The real layer 06 as an inhomogeneous composite material consisting, for. B. from tissue, air cushion layer, adhesive and rubber cover plate, i.e. both compressible and incompressible components, is within the above-mentioned limit cases.

The solution now lies in determining or determining the relative position of the measured or the desired behavior to the two theoretically ascertainable extreme behaviors - purely compressible, purely incompressible. In the following an example for the analytical calculation of the idealized borderline cases is given. The conveying speed of layer 06 in roller gap 03 is considered for the two ideal limit cases.

In the ideally compressible case, the indentation S of the layer 06 in the nip 03 compresses the layer 06. The speed v ₀ on the undisturbed surface of the layer 06 is reduced to the speed v in the constriction _zone due to a reduced effective diameter D _wGZ (FIG. 1). The effective diameter D _wG z decreases in the area of the connecting line between the two cylinder centers by twice the amount of the indentation S:

D _wGZ = D _GZK + 2 * (t - S) Holy

For a speed or transmission ratio I expressing a leading and / or lagging speed from the speeds n _GZ ; n _PZ or frequencies w _GZ ; w _PZ of cylinder 01; 02

I = - n ^ ∞ ₇ . = - - ß ∞ ~ ₇ - m .i ^" t. Ω = - V = ^~ 2 * V - - r [2, 3i] n _PZ ω _PZ r D

results in the compressible case with the surface speed v _{p of} the forme cylinder 01

In the case of "true rolling", ie the cylinders roll freely on one another, the surface velocities v _p ; vi of the two cylinders 01; 02 are the same. The low slip due to the bearing friction of the cylinder driven via friction is neglected ideally compressible case as _ 6 GZ_ _ D _wPZ _ D _wPZ r ₅ ] ^comp ω _pz D _wGZ D _GZK + 2 * (t -S)

being represented.

When transporting incompressible media through narrowing of the cross-section, the continuity equation applies, which means that the mass flow rate always remains constant. Applied to the indentation S of the layer 06 in the pressure gap 03, this means an increase in the conveying speed in the constriction or the contact zone of the rolling cylinders 01; 02 (Fig. 2).

The mass flow rate in front of the nip 03 (through a cross-sectional area A0) and in the narrowing of the pressure nip (through a cross-sectional area A1) is constant.

A _Q * v _Q = A _l * v _l (continuity) [6]

The cross-sectional area A ₀ ; Ai can be determined from a length L and the thickness t or the thickness t-S reduced by the indentation S.

A ₀ = L * t A = L * (tS) U]

Assuming a linear velocity profile in the constriction zone between a speed inside v _Gi and outside v _{Ga of} the layer 06, and that the peripheral speeds are determined by the surface speeds of the cylinders 01; 02 are determined, the integration for the conveying speed results in the average speed. Thus the continuity equation [6] can be written as follows

With the relationship [3] for the angular frequency ω and several transformations we get as Speed or gear ratio for the incompressible limit case the following relationship:

3 shows the transmission ratios I for some measurements. For each layer 06, ie for different rubber blankets 06, the speed ratios n _GZ / n _{PZ were recorded} for four different impressions S and the gear ratio I was calculated therefrom.

The connection of the measuring points gives a good approximation of straight lines, all of which begin at the intersection of the limit cases also entered. The z. T. recognizable offset to the intersection is due to the different thicknesses t of the rubber blankets 06 used.

Fig. 4 shows the speed or gear ratios I in the ideal compressible, ideal incompressible and real case in a schematic representation. , , - ^' - ^""

To characterize a layer 06, e.g. B. a rubber blanket 06, a measurement to determine the real transmission ratio l _rea ι is now carried out on a suitable measuring device (see below) for at least one measuring point (an indentation S). The geometries of the measuring device are known, so that with knowledge of the strength t, the theoretical transmission ratios I for the ideally compressible and the ideally incompressible case can already exist or be formed. Now, a measure α based on a ratio between the z. B. in the measurement with a corresponding measuring device actually occurring transmission ratios I to the idealized limit cases, each at the same indentation S, formed. Due to the at least sectionally idealized and linearized relationships, the characteristic number α defined in this way is a constant for all impressions S, or for at least the area under consideration, which is the rolling behavior (Stretching or compression) of layer 06 describes objectively.

The key figure α can be defined as follows, for example,

= - = ^{eal ~ mkomp} rαi

R T comp - T incomp

where A represents the difference between real and theoretical incompressible, and B represents the difference between theoretical compressible and theoretical incompressible gear ratio I for the same indentation S. In the definition of the characteristic number α according to [9], α = 0 for the case of a real layer 06 which behaves in an ideally incompressible manner, and becomes α = 1 for a real layer 06 which behaves in an ideally compressible manner.

The characteristic number α can also be formed by a different type of algebraic rule, which describes the relative position of the measured real gear ratios I to the position of the extreme theoretically determinable gear ratios I. Another standardization can be selected, for example by means of multipliers, a spreading of the value range or a shift by addition / subtraction. The differences in the quotient can also be reversed, and the numerator and denominator can be reversed. What is essential, however, is knowledge of the algebraic rule [9] on which the characteristic number α is based, in order to be able to use a rubber blanket 06 marked accordingly for the suitable configuration of the cylinders 01; 02, or from the configuration of the cylinder 01; 02 to get to the suitable rubber blanket 06.

Instead of speed ratios I, it is also possible to use leading or lagging, ratios of angular velocities or other comparable quantities describing leading or trailing, with appropriate adaptation of the regulations.

In the process of determining a layer 06 characterizing the geometry cleaned the measuring device, and at least in sections constant index α, the delivery behavior (z. B. based on the resulting gear ratio l _rea ι) is measured depending on the indentation S, and the position of this measuring point (or several measuring points) relative to the corresponding , determined for the measuring device theoretically ascertainable extreme points. The measured and theoretically determined gear ratios l _rea ι; l _grain ; Ijn _kom p are related, at least in sections, to each other, in particular to each other according to an algebraic rule [9]. In the simplest case, the characteristic number can be determined on the basis of a single measured value for an indentation S.

Conversely, the expected gear ratio I of the cylinders 01; can now be used for a rubber blanket 06 with the known index α, measured by the manufacturer, for example, the associated algebraic rule and the known cylinder _geometries (diameters D _G2K ; D _PZ ). 02 or an expected slip for the respective indentation S. can be calculated in advance. According to the regulation - after relationship [9]:

* - real ~ ^a comp ~ ^'■ * incomp)'^" * ^"'■ * incomp [' 0]

The characteristic number α thus enables the change in the effective diameter D _{wGZ of} the transfer _cylinder 02 to be quantified at a specific indentation S and thus in the case of an angularly synchronous run of the cylinders 01; 02 also a calculation of the slip that occurs.

In a method for the design of cylinders 01; 02, for example in order to avoid slippage or unnecessary forces in the drive, on the basis of the known, at least sectionally constant characteristic number α for the intended layer 06 of a thickness t, and with the predefined format (diameter D _GZK ; D _wPZ ) one of the cylinders 01; 02 the diameter D _wPZ ; D _GZ κ of the other cylinder 02; 01 determined. So can for example for a rubber blanket 06 with a known characteristic number α, a desired profile (vertical height and slope in the diagram) in the relationship between the transmission ratio I and indentation S, and with a known diameter D _wPZ z. B. the forme cylinder 01, the required diameter D _{GZK of} the core 03, or the total diameter D _wGZ κ + 21 of the transfer _cylinder 02 can be determined.

In this way, the development or deformation behavior (stretching or compression) of layer 06 (rubber blanket 06, sleeve, metal printing blanket, coating / elevator / jacket of an ink roller) described by the characteristic number α can also be used to select the diameter D _GZ κ ' , D _wG z ", D _{wPZ flow in} for ideal processing. Using the index α for a given rubber blanket 06, diameters D _GZK ; D _wGZ ; D _{wPZ can} be designed in such a way that optimum processing is achieved. In further training, the diameters D _GZK ; D _wG z; D _{wPZ can} also be optimized in such a way that the deviation from the optimal processing is minimal for a range of different blankets 06. For the use of different blankets 06 or for the use of a special blanket 06 in an existing printing unit the number and / or thickness of documents between the outer surface and the rubber blanket 06 for adjusting the diameter D _{GZ are} determined in advance of the pressing and are taken into account when setting up.

Conversely, a suitable layer 06, e.g. B. a rubber blanket 06, based on predetermined printing _{unit geometries} (diameter D _GZK ; D _wPZ ), by first determining algebraically extreme cases for the conveying _behavior as a function of the indentation S, then a desired course (slope, vertical height in the diagram) for the Funding behavior of a real layer 06 is determined at least in sections, and then the key figure α adjusted for the specific geometry for the required layer 06, e.g. B. a rubber blanket 06 is formed by a relative position of the desired course or a value to the algebraically determined courses or values is determined at least for a value of the indentation S. A rubber blanket 06 corresponding to code number α can now be selected if it was formed using the same algebraic rule for the description of the relative position. Were for the measurement and determination of the index α on the rubber blanket 06 and for the determination of the desired index α based on the geometry of the cylinder 01; 02 different algebraic rules are used, they can be converted into each other if the rules are known.

When the cylinder _geometry changes, the straight lines of the theoretically determined transmission ratios l _k0m p; 'tilted' in _om p in the way and the point of intersection with the I-axis shifted, so that with a fixed index α (retained rubber blanket 06) the absolute position of the straight line for the real transmission ratio l _rea ι is changed while the relative position preserved.

With a change in the index α (choice of a rubber blanket 06 with a different characteristic),. however, the cylinder _geometries in the printing unit remain the same, the straight lines of the theoretically determined transmission ratios remain l _k0m p; li _nkom p received, the relative for the real transmission ratio l _rea ι is tilted and receives a different slope.

An elevator 06 with a suitable characteristic number α for a specific printing unit geometry therefore generally does not fit for a geometry different from this, in particular a different ratio of the diameters D _GZr ; D _wPZ .

In an advantageous embodiment with largely beistellungsunabhängiger handling elevator 06 and printing unit geometry are coordinated such that at least in a relevant for practical range for the indentation S or a relative indentation S *, the slope in Fig. 4 between ratio l _rea ι and indentation S is essentially zero, ie dl _rea ι / dS »0. The relative indentation S * is defined here via the ratio S / t, ie the indentation S in relation to the original, not indented thickness t of layer 06. A corresponding range for the relative indentation S * can be viewed in general terms, e.g. B. between 6% and 10%, but in particular between 6.5% and 9%. However, it can be advantageous to differentiate between the “type” of the nip point for the areas. For the nip point between a transfer cylinder 02; 11 and a forme cylinder 01; 12, the area relevant in practice is, for example, from 6% to 7 %, while it lies between 9% and 10% for the nip point between a transmission cylinder 02; 11 and a satellite cylinder 16. The gradient dl _rea | / dS should be at least less than or equal to 0.01 1 / mm in these areas, in particular less than or equal to 0.005 1 / mm. Thicknesses t considered for an advantageous type of elevator 06 are, for example, 1.6 to 2.5 mm, while for a second advantageous type with a lower spring force or surface pressure and / or a smaller slope of a spring characteristic (surface pressure / indentation) the thicknesses are e.g. 3.5 to 5 mm.

The printing units or printing units shown in FIGS. 5 to 8 are all shown linearly for the sake of simplicity, i. H. the axes of rotation of the cylinders involved are in the representations old in one plane. However, the cylinders of the printing units can also be arranged at an angle to one another, so that the following explanations are equally applicable to linear as well as angular arrangements of the cylinders or cylinder groups.

5 and 6 show a printing unit 07 configured in an advantageous manner and designed as a so-called double printing unit 07. The transfer cylinder 02 of a first pair of cylinders 01; 02 acts on a substrate 08, e.g. B. a web 08 with a counter cylinder 11, also designed as a transfer cylinder 11, to which a forme cylinder 12 is also assigned. All four cylinders 01; 02; 11; 12 are mechanically driven independently of one another by means of different drive motors 13 (FIG. 5). In a modification, forme and transfer cylinders 01; 02; 11; 12 each coupled in pairs by a paired drive motor 13 (on the forme cylinder 01; 12, on the transfer cylinder 02; 11 or parallel) driven (Fig. 6).

The forme cylinder 01; 12 and the transfer cylinder 02; 11 are in a first embodiment as cylinder 01; 02; 11; 12 double circumference, ie with a circumference of essentially two standing printed pages, in particular of two newspaper pages. They have effective diameters D _wGZ ; D _wPZ 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 06 with a characteristic number α of 0.989 to 1,000, for. B. 0.989 to 0.999, in particular from 0.993 to 0.997. This configuration enables a largely slip-free rolling or driving of the cylinders 01; 02; 11; 12 largely guaranteed without torque transfer. The speed ratio l _rea ι is preferably selected such that when the indentation S or the relative indentation S * varies, at least within the aforementioned ranges for the relative indentation S * of the corresponding cylinder pair, by a maximum of 0.002, in particular 0.001, of 1, 000 / n deviates. In this context, the variable n represents the ratio between the number of printed pages in the circumferential direction on the transfer cylinder 02; 11 for the number of equally large printed pages in the circumferential direction of the forme cylinder 01; 12. Since in this embodiment the cylinders 01; 02; 11; 12 are both double in size, n = 1 applies and the maximum deviation is 0.002, in particular 0.001 out of 1,000.

In a second embodiment, the forme cylinders 01; 12 and the transfer cylinder 02; 11 as cylinder 01; 02; 11; 12 simple scope, ie with a scope of essentially a standing print page, in particular from a newspaper page. They have effective diameters D _wGZ ; 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 06 with a characteristic number α of 0.980 to 1,000, e.g. B. 0.980 to 0.995, in particular from 0.983 to 0.993. The speed ratio l _real is again preferably chosen such that it varies when the indentation S or the relative indentation S * varies, at least within the above range mentioned range for the relative indentation S ^{* of} the corresponding cylinder pair, by a maximum of 0.002, in particular 0.001, of 1,000 / n, ie 0.002, in particular 0.001, of 1,000.

In a third embodiment, not shown, the forme cylinders 01; 12 as cylinder 01; 12 simple circumference with effective diameters D _wPZ between 150 to 190 mm, and the transfer _cylinder 02; 11 as cylinder 02; 11 double circumference with effective diameters D _wG 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 06 with a code number α from 0.987 to 1,000, in particular from 0.997 to 1,000. The speed ratio l _rea ι is again preferably selected such that when the indentation S or the relative indentation S * varies, at least within the above-mentioned range for the relative indentation S * of the corresponding cylinder pair, a maximum of 0.002, in particular 0.001, of 1, 000 / n, here with n = 2, ie 0.002, in particular 0.001, deviates from 0.500.

7 and 8, a printing unit 14 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 14. The transfer cylinder 02 acts here with a cylinder 16 not leading an ink, e.g. B. an impression cylinder 16, in particular a satellite cylinder 16, 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 16 on the other side. The one for the forme cylinder 01 in the previous considerations The effective diameter D _{wPZ used} in the equations for the interaction between the transmission and satellite _cylinders 16 is to be replaced accordingly as the diameter D _{wSZ of} the satellite _{cylinder 16.} In one embodiment (FIG. 7) with at least independently driven transmission 02 and satellite cylinders 16, the or more satellite cylinders 16 on their own drive motor 13, while the pair of form and Transfer cylinder 01; 02 are mechanically coupled by a common drive motor 13 (FIG. 7), or are each mechanically driven independently of one another by a separate drive motor 13 (FIG. 8).

Forme cylinder 01, transfer cylinder 02 and satellite cylinder 16 are in a first embodiment for FIG. 6 as cylinder 01; 02; 16 double circumference with effective diameters D _wGZ ; D _wPZ ; D _wSZ between 260 to 400 mm, in particular 280 to 350 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 at least one elevator 06 with a characteristic number α from 0.990 to 0.999, in particular from 0.993 to 0.997. This configuration enables a largely slip-free rolling or driving of the cylinders 01; 02; 16 largely guaranteed without moment transfer.

In a second embodiment for FIG. 7 or 8, forme cylinder 01, transfer cylinder 02 and satellite cylinder 16 are cylinders 01; 02; 16 simple circumference, ie with a circumference of essentially a standing print page, in particular from a newspaper page. They are DWG _Z with effective diameters; D _wPZ ; D _wS z between 120 to 180 mm, in particular 130 to 170 mm. On the outer surface of the core 04, the transfer cylinder 02 has at least one elevator 06 with a characteristic number α from 0.980 to 0.995, in particular from 0.983 to 0.993.

In a third embodiment, not shown for FIG. 7 or 8, the forme cylinder 01 is a cylinder 01 of simple circumference with effective diameters D _wPZ between 120 to 180 mm, in particular 130 to 170 mm, and transmission cylinder 02 and satellite cylinder 16 as cylinder 02; 16 double circumference with effective diameters D _WG Z; Dwsz between 260 to 350 mm, in particular 280 to 320 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 each have at least one elevator 06 with a characteristic number from 0.985 to 0.995, in particular from 0.990 to 0.995. In a fourth embodiment (not shown) for FIGS. 7 or 8, forme cylinder 01 and transfer cylinder 02 are cylinders 01; 02 simple scope with effective diameters D _wPZ ; D _wGZ between 120 to 180 mm, in particular 130 to 170 mm, and the satellite cylinder 16 as cylinder 02; 16 double circumference with effective diameters D _wSZ between 260 to 350 mm, in particular 280 to 320 mm. On the outer surface of the core 04, the transfer cylinder 02; 11 each have at least one elevator 06 with a characteristic number α from 0.985 to 0.995, in particular from 0.990 to 0.995. Are form and satellite cylinders 01; 16 different dimensions, so a compromise that is ideal for the case can only be found in the two nip points, depending on the requirements.

As already explained above, the characteristic number of an elevator 06 is determined by measuring the elevator 06 on a suitable device and subsequent processing using an algorithm. FIG. 9 shows an exemplary embodiment of a measuring device in plan view and in FIG. 10 in a larger side view as it is particularly suitable for determining the characteristic number - ^" .

The measuring device has at least two cylinders 17; 18 or rollers 17; 18, which are rotatably mounted in a frame 19, in particular on both sides. At least one of the two cylinders 17; 18, here the cylinder 17, has a largely incompressible and non-elastic, hard outer surface. At least one of the two cylinders 17; 18 is mounted in such a way that a center distance a between the axes of rotation of the two cylinders 17; 18 is changeable. In the exemplary embodiment, the cylinder 17, which has a “hard” lateral surface and corresponds to the forme or satellite cylinder 01; 12; 16, is mounted on the end face with a pin in an eccentric bushing 21 in the frame 19. The other cylinder 18 in the example is conventional stationary in frame 19. The bearings of the cylinders 17, 18 are stiff and free of play. For the former, the bearings are made correspondingly solid. The play is either due to a tapered seat of the bearing or due to thermal shrinking. It can however, the soft cylinder 18 is also movable and the hard cylinder 17 is fixed, or both cylinders 17; 18 be movably mounted. The mobility can u. U. also by pivoting a cylinder 17 mounted in levers or in a linear guide; 18 be realized.

In an advantageous embodiment, the eccentric bushing 21 has an eccentricity e of twice or four times the thickness t of the layer 06 that is usually to be measured with the device (n 2 * t to 4 * t) and is, for. B. between 3 and 8 mm, in particular between 4 and 6 mm, a type of layers 06, and between 8 to 16 mm, in particular between 10 and 14 mm, for a stronger type. The position of the eccentricity e closes with a plane E in a basic position forming an angle γ of 75 to 120 °, in particular 85 to 110 °. That position of the cylinders 17; 18 viewed in relation to one another, in which a line contact of the two lateral surfaces occurs, essentially without indentation S.

In an advantageous embodiment, the eccentric bushing 21 is rotated in each case via a lever 22 ^" rigidly connected to the eccentric bushing 21 ^" , which can be pivoted about the pivot axis of the eccentric bushing 21 by means of an actuator 23. The actuator 23 can fundamentally be different, for example as a motor-driven one In the present embodiment, the actuator 23 is designed as a cylinder 23 which can be pressurized with pressure, which is articulated on the frame 19 and whose piston rod 24 is articulated to the lever 22 (or vice versa).

The actuator 23 pivots the lever 22 against the pivoting movement of the eccentric bushing 21 to smaller center distances a of the cylinders 17; 18 limit stop 26. This stop 26 is designed to be adjustable in the direction of its travel limit for the lever 22, but can be fixed in the desired position relative to the frame 19. In the example, a threaded bolt 27, e.g. B. a threaded spindle or a screw with a fine thread, on the end face of the stop 26. By turning the threaded bolt 27, manually or by motor, the stop 26 can be moved further towards or away from the lever 22.

The movement or the position of the eccentric bushing 21 or the lever 22 is determined in an advantageous embodiment by means of a path measurement 28. In the present example, this measurement is carried out by means of a dial gauge 28 arranged fixed to the frame, the free and movable plunger of which cooperates with the lever 22. The arrangement of a dial gauge 28 is advantageous, wherein one revolution of the pointer corresponds to a linear movement of the plunger of less than 0.05 mm, in particular less than or equal to 0.02 mm. The distance measurement 28 can, however, instead of a mechanical design in other ways, for. B. be carried out electrically and / or magnetically. The measured value can then either be converted from a mechanical into an electrical signal or, as a directly obtained electrical signal, can be sent to a data processing (not shown).

For a high measuring accuracy, an arrangement is advantageous, according to which a distance b tapped on the lever 22 between the pivot axis A and the measuring point of the displacement measurement is large compared to the eccentricity e. In an advantageous embodiment, the ratio distance b to eccentricity e is greater than or equal to 20, in particular greater than or equal to 50. The movement of the cylinder 17 is derived from the eccentricity e, the distance b, the resolution of the displacement measurement and the known line for pivoting the axis of rotation defined on its lateral surface. The measuring accuracy of such a measuring device has a reproducibility in the indentation S of less than or equal to 0.005 mm.

In one development, the stop is designed to be movable by a motor, the position of the stop 26 being present or predetermined as an electrical signal. At the same time, the measured value of the path measurement 28 is in the form of an electronic signal. In this embodiment, one or more positions for the cylinder 17 or one or more can be automatically generated via data processing or control Center distances a are approached.

In a further embodiment, not shown, the setting of the stop 26 and the distance measurement 28 is carried out by only one means, such as. B. by a driven by an angle-adjustable electric motor threaded spindle with fine thread. Via the angular position, data processing receives the information about the position or vice versa.

To determine the indentation point, d. H. the position in which only a line contact between the two cylinders 17; 18 without indentation S, the measuring device has z. B. one or more light sources, not shown, on one side of the gap between the cylinders 17; 18 on. When the two cylinders 17; 18 can thus determine the indentation point through the light gap when no more light is falling through the gap. The light can be detected in manual mode on the other side of the gap by the human eye or in automatic mode, for example by one or more detectors. In the automatic process, the signal is forwarded to the data processing (not shown). Through the use of light described, an accuracy for setting the indentation point of less than or equal to 0.005 mm, in particular less than or equal to 0.002 mm, can be achieved.

To detect the rolling behavior of the two cylinders 17; 18 is one of the two cylinders 17; 18 by an external drive 29, for. B. an electric motor 29, rotatably driven. In Fig. 9, the electric motor 29 drives, for example, via a drive wheel 36, for. B. a pulley 36, via a gear 37, for. B. a belt 37, in particular a toothed belt 37, on a drive wheel 38, for. B. a pulley 38 on the hard cylinder 17, while the soft cylinder 18 is driven only via friction. The electric motor 29 can also, for. B. drive over the belt 37 the soft cylinder 18 while the hard cylinder 17 is driven by friction. In an advantageous embodiment, the electric motor can be exchanged with the hard or the soft cylinder 18; 17 connectable. In one development, one of the cylinders 17; 18 or even both an axially driving, position-controlled or at least speed-controlled electric motor 29. The negative influence on the rolling behavior by driving a cylinder 17; 18 Over friction is reduced by using extremely low friction bearings. A maximum deviation in the measured transmission ratio I from the "true" transmission ratio I of at most 0.01% can thus be achieved.

The angular velocity or the respective angular position of the two cylinders 17; 18 is by means of the cylinder 17; 18 or a respective pin arranged rotary encoder 31; 32, e.g. B. an opto-electronic angle decoder, measurable.

In order to interrupt the contact between the two cylinders 17; 18 to avoid, the hard cylinder 17 advantageously has a continuous, uninterrupted lateral surface in the area rolling with the soft cylinder 18. However, this can also be achieved in that any “replacement printing plates” located on the lateral surface are offset from one another — in the circumferential direction (for example 180 °), or, if the hard cylinder 17 only has a finite replacement printing plate, the resulting impact or channel is closed flush with the lateral surface by a cover 33 (see example in FIG. 9). The same applies to the soft cylinder 18, wherein in FIG. 9 two elevators 06 offset from one another by 180 ° in the circumferential direction with a maximum Cover 34 extending over half the cylinder length are shown. This arrangement of the elevators 06 ensures constant contact of one of the elevators 06 with the hard cylinder 17.

For different impressions S is by the encoder 31; 32 and a downstream electronics, the angular velocity of both cylinders 17; 18 and the possible advance or retardation recorded with high precision. The drive takes place interchangeably via the hard or the soft cylinder 17; 18. For the adjustment of the center distance a, the movable cylinder 17; 18 in its eccentric socket through their Twisting moves. The adjustment described above is in particular designed to be more comfortable than with a printing press. Now the indentation point is determined on the basis of the light gap between the jacket surfaces (e.g. a fluorescent tube under the roller gap). Due to the sensitive adjustment (stop 26), the indentation S is now set and measured precisely (distance measurement 28).

With the known geometries of the cylinder 17; 18 and the measuring point or the measuring points for an indentation S (for S> 0) is based on algebraic regulations, such as. B. equations [5], [8] and [9] determined the characteristic number α as described above.

LIST OF REFERENCE NUMBERS

01 roller, cylinder, forme cylinder, impression cylinder

02 roller, cylinder, transfer cylinder

03 nip

04 core 05

06 shift, rubber blanket, elevator

07 Printing unit, double printing unit

08 printing material, web 09

10

11 roller, cylinder, transfer cylinder, impression cylinder

12 rollers, cylinders, form cylinders

13 drive motor

14 printing unit, three-cylinder printing unit 15

16 roller, cylinder, impression cylinder, satellite cylinder

17 roller, cylinder

18 roller, cylinder

19 frame 20

21 eccentric bushing

22 levers

23 actuator, cylinder

24 piston rod 25

26 stop

27 threaded bolts

28 position measurement, dial gauge 29 drive, electric motor 30

31 encoders

32 encoders

33 cover

34 Cover 35

36 drive wheel, pulley

37 Gears, belts, timing belts

38 drive wheel, pulley

D _W GZ diameter

D _wPZ diameter

D _W GZK diameter

Dwsz diameter

ω angular frequency w _GZ frequency w _PZ frequency

a distance

A difference

A ₀ cross-sectional area

Ai cross-sectional area b distance

B difference e eccentricity

E level α key figure γ angle (e, E)

I speed ratio, gear ratio l _rea ι speed ratio, gear ratio, measured, real

' _k omp speed ratio, gear ratio, compressible lin om _p speed ratio, gear ratio, incompressible

L Length n Variable n _GZ speed n _PZ speed

S indentation

S * indentation, relative t strength v ₀ speed | Velocity v _p surface velocity v _G j velocity v _Ga velocity

Claims

Expectations

1. A method for selecting a layer (06) on a roller (01; 02; 11; 12; 16), whereby - first of all, from the given printing unit geometry, the theoretically resulting for the purely compressible and the purely incompressible case

Extreme values for the speed ratio (lo _mP ; li _nk omp) are determined at least in sections as a function of an indentation (S), a desired relative position for the speed ratio (l _rea ι) of a real one

Layer (06) to the extreme values for the speed ratio (lo _mP; li _nk o _m p) is at least partially set, and in sections by means of at least in terms of setting the desired

A characteristic number (α) for the desired layer (06), adjusted for the specific geometry, is formed using an algebraic rule for the theoretically determined courses for the extreme values (lo _mP ; li _nkom p).

2. The method according to claim 1, characterized in that the characterizing

, Characteristic number (α) of the layer (06) is first formed by measurement on a measuring device and subsequent adjustment to the geometry of the measuring device by the same algebraic rule.

3. The method according to claim 1, characterized in that the algebraic rule the relative position of the measured speed ratio (l _rea ι) relative to the two extreme values for the speed ratio (I _ko mpi li _n o _m p) for the relevant indentation (S) expresses.

4. Printing unit with at least two co-operating rollers (01; 02; 11; 12; 16), wherein at least one of the rollers (02; 11) has an elastic layer (06) on its outer surface and the other roller (01; 12; 16 ) has a largely undeformable outer surface, characterized in that the layer (06) has at least one area of a relative indentation (S *) one of its elastic properties has a descriptive index (α) from 0.980 to 0.999, the index being determined by the algebraic rule

I real -7 incomp

^~ I comp -I incomp

is formed, l _k0 mp; li _nk o _m p a speed ratio for the extreme cases of a purely compressible or purely incompressible layer (06), and l _rea ι represents a desired speed ratio.

5. Printing unit according to claim 4, characterized in that the

Speed ratio l _rea ι at least in a range of a relative indentation (S *) of the layer (06) deviates by a maximum of 0.002, in particular 0.001, from 1,000 / n, where n is the ratio between the number of printed pages in the circumferential direction the roller (02; 11) with the layer (06) to the number of printed pages on the other roller (01; 12; 16).

6 .. printing unit with at least two co-operating rollers (01; 02; 11; 12; 16), at least one of the rollers (02; 11) on its outer surface an elastic layer (06) and the other roller (01; 12; 16) has a largely undeformable outer surface, characterized in that the layer (06) and the geometries of the two rollers (01; 02; 11; 12; 16) are mutually coordinated such that a speed ratio (l _rea ι) of the rollers (01; 02; 11; 12; 16) in the case of variation at least in a range of a relative indentation (S *) of the layer (06) deviates by at most 0.002 from 1,000 / n, where n is the ratio between the number of printed pages in Represents circumferential direction on the roller (02; 11) with the layer (06) to the number of printed pages on the other roller (01-; 12; 16).

7. Printing unit according to claim 6, characterized in that the

Speed ratio (l _rea ι) of the rollers (01; 02; 11; 12; 16) with variation at least in a range of the relative indentation (S *) of the layer (06) by at most 0.001 deviates from 1,000 / n, where n represents the ratio between the number of printed pages in the circumferential direction on the roller (02; 11) with the layer (06) to the number of printed pages on the other roller (01; 12; 16).

8. Printing unit with at least two co-operating rollers (01; 02; 11; 12; 16), at least one of the rollers (02; 11) on its outer surface an elastic layer (06) and the other roller (01; 12; 16 ) has a largely undeformable outer surface, characterized in that the layer (06) and the geometries of the two rollers (01; 02; 11; 12; 16) are mutually coordinated in such a way that for at least one area of a relative indentation (S * ) the differential quotient (dl _rea ι / dS) between speed ratio (l _rea ι) and indentation (S) deviates from zero by a maximum of 0.01 1 / mm.

9. Printing unit according to claim 6 or 8, characterized in that the layer (06) for the area of the relative indentation (S *) has a characteristic number (α) describing its elastic properties of 0.980 to 1,000, the characteristic number being characterized by the algebraic rule

a - real incomp comp / i, ncomp

is formed, l _Kornp ; li _nk o _m p a speed ratio for the extreme cases of a purely compressible or purely incompressible layer (06), and l _rea ι represents a desired speed ratio.

10. Printing unit according to claim 4 or 6, characterized in that at least for the range of a relative indentation (S *) the differential quotient (dl _rea ι / dS) between the speed ratio (l _rea ι) and indentation (S) by a maximum of 0.01 1 / mm deviates from zero.

11. Printing unit according to claim 10, characterized in that the Differential quotient (dl _rea | / dS) is essentially zero.

12. Printing unit according to one or more of claims 4 to 10, characterized in that the area of the relative indentation (S *) for the nip point between a roller designed as a transfer cylinder (02; 11) and a roller (01; 12) 01; 02; 11; 12) is from 6% to 7%.

13. Printing unit according to one or more of claims 4 to 10, characterized in that the area of the relative indentation (S *) for the nip point between a roller (02; 11) and a roller (02; 11) designed as a satellite cylinder (16). 11) is from 9% to 10%.

14. Printing unit according to claim 4 or 9, characterized in that the two rollers (01; 02; 11; 12; 16) each have an effective diameter (D _wGZ ; D _wPZ ) of 260 to 350 mm, and the layer (06) has a key figure (α) of 0.989 to 1,000.

15. Printing unit according to claim 4 or 9, characterized in that the two rollers (01; 02; 11; 12; 16) each have an effective diameter (D _wGZ ; D _wPZ ) of 120 to 180 mm, and the layer (06) has a characteristic number (α) of 0.980 to 0.990.

16. Printing unit according to claim 4 or 9, characterized in that the roller (02; 11) having the elastic layer (06) has an effective diameter (D _wGZ ; D _wPZ ) of 260 to 400 mm and the other roller (01; 16 ) an effective diameter (D _wGZ ; D _wPZ ) of 150 to 190 mm, and the layer (06) has a characteristic number (α) of 0.987 to 1,000.

17. Printing unit according to claim 4, 6 or 8, characterized in that the roller (02; 11) having the elastic layer (06) as a transfer cylinder (02; 11) and the roller (01; 12) having the largely undeformable lateral surface is designed as a forme cylinder (01; 12).

18. Printing unit according to claim 4, 6 or 8, characterized in that the roller (02; 11) having the elastic layer (06) as the transfer cylinder (02; 11) and the roller (16) having the largely undeformable lateral surface as the satellite cylinder ( 16) is executed.

19. Printing unit according to claim 4, 6 or 8, characterized in that the two rollers (01; 02; 11; 12; 16) are designed as co-operating rollers (01; 02; 11; 12; 16) of an inking unit.

20. Printing unit according to claim 19, characterized in that one of the rollers (01; 02; 11; 12; 16) is motorized and the other of the rollers (01; 02; 11; 12; 16) is driven only by friction.

21 pushing unit according ^"to claim 17, characterized in that the transfer cylinder (02; 11) interacts with a third, designed as satellite cylinder (16) roll (16) which mechanically by a drive motor (13) independent of the two first rollers (01; 02; 11; 12) is driven.

22. Printing unit according to claim 4, 6, 8, 17, 18 or 19, characterized in that the two rollers (01; 02; 11; 12) are driven in pairs by a common drive motor (13).

23. Printing unit according to claim 4, 6, 8, 17, 18 or 19, characterized in that the two rollers (01; 02; 11; 12; 16) are mechanically driven independently of one another by means of two drive motors (13).

24.Device for determining a rolling behavior of an elastic layer (06), an axis distance (a) between a roller (18) carrying the layer (06) and a roller (17) having an essentially non-deformable lateral surface, and a speed ratio ( l _rea ι) between the two rollers (17; 18) can be determined, characterized in that at least one of the two rollers (17; 18) is mounted in eccentric bushes (21) in a frame (19).

25. The device according to claim 24, characterized in that with the eccentric bushing (21) a lever (22) translating the movement of the roller (17) is rigidly connected, the movement of which can be determined by a distance measurement (28).

26. Device for determining a rolling behavior of an elastic layer (06), wherein a center distance (a) between a roller (18) carrying the layer (06) and a roller (17) having an essentially non-deformable outer surface can be changed, and a speed ratio ( l _rea ι) between the two rollers (17; 18) can be determined, characterized in that a change in the center distance

, (a) on a lever (22) which translates the movement of the roller (17) can be determined by a distance measurement (28).

27. The device according to claim 25, characterized in that at least one of the two rollers (17; 18) is mounted in eccentric bushings (21), with each of which a lever (22) is rigidly connected.

28. The apparatus of claim 24 or 27, characterized in that a ratio between a distance (b) of a pivot axis (A) from a measuring point of the displacement measurement (28) on the lever (22) and an eccentricity (e) is greater than or equal to 20 ,

29. The device according to claim 24 or 27, characterized in that the eccentricity (e) with a plane (E) defined by the axes of rotation of the rollers (17; 18) in a position of the rollers (17; 18) in which a line contact the both lateral surfaces to each other, enclose an angle of 75 to 120 °.

30. The device according to claim 24 or 26, characterized in that a respective angular velocity and / or angular position can be determined by a rotary encoder (31; 32) provided for each roller (17; .18).

31. The device according to claim 24 or 26, characterized in that one of the rollers (17; 18) by an external drive (29), and the other roller (18; 17) is driven only by friction with the former.

32. Apparatus according to claim 31, characterized in that the drive (29) is interchangeably assigned to one or the other roller (17; 18).

33. Apparatus according to claim 25 or 26, characterized in that the distance measurement (28) is designed as a dial gauge (28) with a resolution of less than or equal to 0.05 mm / 360 °.

34. Device according to claim 25 or 26, characterized in that a position-adjustable stop (26) is provided for the lever (22).

35. Apparatus according to claim 25 or 26, characterized in that the lever (22) is pivotable by means of an actuator (23).

36. Device according to claim 34 and 35, characterized in that the lever (22) can be adjusted against the stop (26) by means of an actuator (23) designed as a cylinder (23) which can be pressurized with pressure medium.

37. Apparatus according to claim 24 or 26, characterized in that a light source is provided on one side of the gap between the rollers (17; 18) to determine an indentation point.