RU2291058C2 - Method of taking characteristics, determining parameter and selecting of tympans for rollers of press-printing machine - Google Patents

Abstract

FIELD: printing.

SUBSTANCE: invention relates to method of taking characteristics of layer 06, method and device for determining parameter (α) and method of selecting of suitable layer for rollers 01, 02, 16 and choosing of appropriate geometry of rollers of printing machine making it possible to determine and use parameter characterizing the layer and describing character of rolling of machine rollers irrespective of measuring device or use in some particular printing device.

EFFECT: provision of quality indices for tympans in relation of their transport properties.

49 cl, 10 dwg

Description

The present invention relates to a method of characterization, to a method and apparatus for determining a parameter, as well as to a method for selecting suitable decals on the rollers, respectively, the appropriate geometry of the rollers of the printing machine according to the restrictive part of claims 1, 4, 6, 8, 24, respectively 26 claims.

In printing machines, in particular in rotary printing machines, ink is applied between one or more rollers of the inkjet apparatus, between the inkjet apparatus and the printing cylinders, respectively, between the printing cylinders and transferred from the printing cylinder through the backpressure cylinder (hereinafter referred to as rollers) to the web, for example paper web. To this end, the transfer of paint occurs between two adjacent, interacting, and in some cases interacting also through the web, rollers, preferably between one roller with a "hard" surface and one roller with a "soft" surface.

Since a known specific pressure is required for ink transfer, at least a roller with a soft surface undergoes deformation in the region of this surface. This deformation of soft surfaces made, for example, in the form of an elastomeric tire (dekel, rubber sheet, metal offset sheet, sleeve, coating), depending on the nature of the material and the depth of the dent (due, for example, to the distance between the rollers, to the different thickness of the sheet, etc.) a change in the effective diameter of the roller when it rolls along the roller interacting with it, i.e. leads to changes in specific pressure and the nature of the break-in. For rollers rotated by the drive during synchronization of rotation using mechanical and electronic devices, this can lead, depending on the material used and the depth of the dent, to different surface speeds and thereby to slip in the contact zone of the rollers. The slip resulting in this way causes the appearance of a tangential force component due to friction and thereby reduces the print quality (ink smearing, double vision), disrupts the power transfer, and also reduces the service life of printing plates, respectively decals.

From German patent application DE 4315456 A1, a fabric web is known having in its composition one incompressible and one compressible elastomeric layer, the latter increasing the tolerances in the rolling of the mold by a cylinder. It follows from this document that with an optimized structure of the layers, there is practically no change in the surface, respectively, of the length within the known limits of the mutual position of the interacting cylinders, i.e. the difference in the angles of rotation of two cylinders rolling one over the other within these limits does not depend on the indentation. The difference in rotation angles can be determined on the basis of a laboratory model for various decks and various relative positions, with the first cylinder rotating from the drive and freely rotating, equipped with a deck, the second cylinder installed in the working position one relative to the other.

An article published by the applicant under the heading: "The effect of printing blankets on the condition of printing cylinders" (Proceedings of the Technical Association of the Printing Industry of the USA (TAGA), 2001, p. 211) proposes a parameter for determining the nature of the running-in of an elastic decal. This parameter will allow the designer to calculate the gear ratio between the gear cylinder and the plate cylinder. The device for determining the nature of the break-in incorporates one roller rotating from an external drive and one rotating under the action of friction, the angular velocities of which can be measured using optoelectronic angular decoders.

The objective of the invention is to provide a method of characterization, a method and apparatus for determining the parameter, as well as a method of selecting suitable decels on the rollers, respectively, the appropriate geometry of the rollers of the printing press.

This problem is solved according to the invention using the characteristics of claims 1, 4, 6, 8, 24, respectively 26 of the claims.

The advantages achieved by the present invention are, in particular, that it is possible to quantitatively describe the decals with respect to their transport properties, respectively the nature of the run-in, and that the characteristic thus obtained does not depend on the geometry of the measuring device, and also does not depend on the geometry printing section. The parameter used to characterize the dekel is independent with respect to the specific geometry of the measuring device and the printing section and can be applied to both the measuring device and the printing section. The description is no longer evaluated only qualitatively (for example, positively transporting, negatively transporting), it is evaluated quantitatively.

A method for characterizing a decel based on a parameter creates an unambiguously defined language between the manufacturer of the decels and the designer of the printing press, which allows, on the one hand, the design of the printing press for a specific predetermined print, and, on the other hand, the design of the print for a given configuration of the printing press can be developed. Both that and another can be found out already in advance thanks to what there is no need for carrying out a labor-intensive pilot program which usually has to be carried out on a printing machine for a special configuration and each type of decal.

Thus, the optimal solution is that for a given cylinder pair, a decal is selected which, when deformed with a dent, is lengthened due to its incompressible component to such an extent that the decrease in the distance to the rotation point is fully compensated. The proposed method allows you to calculate the required parameters and select the appropriate decle.

And vice versa, it is advisable to choose the geometry of the printing apparatus for this special dekel so that, at least in a certain interval of variable dents, the character of the run-in does not depend at all or depends only slightly on the dent.

The values of the measured value required to determine the parameter are found, for example, using a measuring device having two rollers. To determine the distance, respectively, to determine the magnitude of the change in distance (denting), the measuring device in the preferred embodiment of the invention is equipped with a lever transmitting a control movement. A higher gear can also be carried out through an eccentric moving the cylinder, and the lever is rigidly connected to the rotary bearing ring.

The parameter set for the dekel can be applied to a wide variety of printing apparatus configurations and does not depend on the geometry of the measuring device used. Only the algebraic relationship between geometry and parameter should be defined and known.

An advantage of the present invention is also the ability to configure a printing apparatus optimized with respect to the break-in nature. So, for example, if the transfer cylinder interacts with a counter-pressure cylinder, which has basically the same coverage as the transfer cylinder, then in this case the double-coverage transfer cylinder is performed with a dekel having a parameter α ranging from 0.989 to 0.999, and the simple-coverage transfer cylinder is performed with a dekel having a parameter α ranging from 0.980 to 0.995. The indicated parameters α must be observed, at least in the practice-relevant range of relative dents.

Of particular interest is the aforementioned embodiment of the printing apparatus for the case where the transfer cylinder and the counter-pressure cylinder operate independently of each other, each from its own drive. In this case, the load on the engine, calculation of electric motor power and the cost of regulation are minimal.

Below the present invention is explained in more detail with examples of its implementation with reference to the drawings, which show:

figure 1 - the passage of a compressible rubber sheet through the gap between the rollers;

figure 2 - the passage of an incompressible rubber sheet through the gap between the rollers;

figure 3 - measured gear ratios with variation of the dent;

figure 4 - qualitative representation of the gear ratios;

5 is an example of a printing section;

6 is an example of a printing section;

7 is an example of a printing section;

Fig - an example of the implementation of the printing section;

Fig.9 is an example of a measuring device;

figure 10 is a detailed side view according to figure 9.

A working machine, for example a printing machine, incorporates rollers 01, 02 rolling over each other, which in the area of their contact form a gap 03 between each other. In the case of a printing machine, these can be rollers 01, 02 of the ink machine, varnishing machine, or cylinders 01, 02 of the printing apparatus. In the examples shown in figures 1 and 2, the cylinders 01, 02 are a plate cylinder 01 with an effective diameter D _wPZ and a transfer cylinder 02 of the offset printing apparatus. One of the cylinders 01, 02, for example a transfer cylinder 02, has a soft elastomeric layer 06 of thickness t on the side surface of an practically incompressible, inelastic core 04 with a diameter D _wGZK . The core 04 and layer 06 together form the effective diameter D _{wGZ of the} transfer cylinder 02. The effective diameter D _wPZ is determined by the effective for _rolling in the side surface of the plate cylinder 01 and, if a printing form is applied to the side surface of the core, also includes this printing form (on not shown). The cylinder 01 with a solid surface can also be made in the form of a cylinder 01 backpressure, interacting with the transfer cylinder 02.

Depending on the relative position of both cylinders, i.e. from their center distance, the practically incompressible, inelastic lateral surface of the plate cylinder 01 “plunges” into the soft layer 06 and causes a dent S in it relative to the undisturbed line of the contour of the layer 06. This dent S is the cause of the above-mentioned problems when running both cylinders 01, 02, depending on the properties of the material (compressible and / or elastic behavior of the material) layer 06.

The underlying idea underlying the present invention is, therefore, to offer a description of the nature of the break-in of such a layer 06, independent of the specific applications, respectively of the measuring devices, on the basis of which a suitable layer 06 can be selected or the optimum size of the rollers 01 , 02. With the assumption of a perfectly compressible layer 06 (for example, a cork layer, etc.) and a perfectly incompressible layer 06 (for example, a solid rubber layer), limit cases can be established for the nature of the run-in ki. The real layer 06, which is a heterogeneous composite material, consisting, for example, of fabric, an air-porous layer, glue and a rubber cover sheet, i.e. of both compressible and incompressible components, is inside the above limiting cases.

Therefore, the solution is to determine, respectively, set the position of the measured or desired behavior relative to both theoretically calculated extreme cases - ideally compressible and ideally incompressible - behavior.

The following is an example of an analytical calculation of idealized limit cases. Moreover, for both ideal limiting cases, the velocity of the layer 06 in the gap 03 between the rollers is considered.

In the case of ideally compressible material, a dent S formed in the gap 03 between the rollers in the layer 06 causes a compaction of the layer 06. The velocity v ₀ on the undisturbed surface of the layer 06 decreases in the narrowing zone to the velocity v ₁ due to a decrease in the effective diameter D _wGZ (Fig. 1). The effective diameter D _wGZ decreases along the line connecting the centers of both cylinders by a double dent S:

For a gear ratio I of frequencies n _GZ ; n _PZ rotation, respectively, frequencies w _GZ ; w _PZ cylinders 01, 02, i.e. a relationship expressing lead and / or lag,

obtained for the case of compressible material at a surface speed v _{p of the} plate cylinder 01

In the case of "true rolling", i.e. the cylinders freely roll over each other, the surface speeds v _p and v _{1 of} both cylinders 01, 02 are equal. Slight slippage due to friction in the bearings of the cylinder driven into rotation through friction can be neglected. The gear ratio in the case of perfectly compressible material can thus be represented as

In the transport of incompressible media due to the narrowing of the cross section, the continuity equation is valid, which shows that the mass flow rate always remains constant. As applied to the dent S in the layer 06 formed in the gap 03 between the rollers, this means an increase in the speed of movement in the narrowing zone, respectively, in the contact zone of the rolling cylinders 01, 02 (FIG. 2).

The mass flow rate before the gap 03 between the rollers (through the cross-sectional area of AO) and in the narrowing of the gap (through the cross-sectional area A1) is constant.

The cross-sectional area A ₀ , A ₁ can be determined from the length L and the thickness t, respectively, of the thickness tS, reduced as a result of the formation of a dent S:

Assuming that in the narrowing zone the velocity profile between the velocity vGi inside and vGa outside the layer 06 is linear and that the edge velocities are determined by the surface velocities of the cylinders 01, 02, we obtain by integrating the average velocity for the displacement velocity. Thus, the continuity equation [6] can be written in the following form:

Using the expression [3] for the circular frequency ω, performing some transformations, we obtain the following expression as the ratio of rotation frequencies, respectively, of the gear ratio for the limiting case of incompressible material:

Figure 3 presents the gear ratios I for some measurements. For each layer 06, i.e. for various rubber canvases 06, the _nGZ / n _PZ ratios of rotation frequencies for four different dents S were determined and plotted, and the gear ratio I was calculated on their basis.

The connection of the measuring points with a good approximation is transmitted by lines, each of which begins at the intersection of the limiting cases, also plotted on the graph. So, partly, a noticeable shift to the intersection point is due to the different thickness t of the rubber bands 06 used.

Figure 4 schematically shows the ratio I of the rotational speeds, respectively, the gear ratio in the case of perfectly compressible, ideally incompressible and real materials.

To characterize layer 06, i.e. rubber web 06, a measurement is first carried out to determine the real gear ratio I _real on a suitable measuring device (see below) for at least one measuring point (dent S). The geometry of the measuring device is known, so that knowledge of the thickness t already gives the theoretical gear ratios I for a perfectly compressible and ideally incompressible case or, accordingly, allows them to be obtained. Then, the parameter α is calculated on the basis of the relationship between, for example, the gear ratios I actually measured using an appropriate measuring device and idealized limit cases for the same dent S. The parameter α determined in this way on the basis of idealized and linearized at least in some segments, for all dents S, or at least for the limits under consideration, is a constant that objectively describes the nature of the break-in (tension, respectively, with atie) layer 06.

The parameter α can be determined, for example, as follows:

moreover, A is the difference between real and theoretically incompressible, and B is the difference between theoretically compressible and theoretically incompressible gear ratio I, in each case for the same dent S. When determining the parameter α by the formula [9] in the case of a perfectly incompressible real layer 06 α = 0, and in the case of a perfectly compressible real layer 06 α = 1.

The parameter α can also be determined on the basis of a differently formulated algebraic prescription, which describes the relative position of the measured real gear ratios I to the position of extreme, theoretically calculated gear ratios I. Thus, another normalization can be chosen, for example, through factors, expanding the limit of values, or shifting by addition or subtraction. You can also reverse the differences in quotient, as well as swap the numerator and denominator. It is important, however, to know the algebraic rule underlying parameter α [9] in order to move from a suitable rubber sheet 06 to a suitable configuration of cylinders 01, 02 or from a configuration of cylinders 01, 02 to a suitable rubber sheet 06.

Instead of the relations I of the rotational speeds, one can also use advances, respectively, lags, ratios of angular velocities or other comparable quantities describing the advances, respectively, the lag, with the corresponding coordination of these requirements.

In the method of determining the parameter α characterizing the layer 06, constant, at least in some segments, and “cleaned” with respect to the geometry of the measuring device, the transport properties are first measured (for example, using the resulting gear ratio I _real ) depending on the dent S and determine the position of this measuring point (respectively, several measuring points) relative to the corresponding extreme points calculated theoretically for the measuring device. For this purpose, the measured and theoretically calculated gear ratios I _real , I _komp , I _{inkomp are} compared at least on some segments with each other, in particular, they are put in relation to each other according to the algebraic prescription [9]. In the simplest case, the parameter α can be determined using a single measuring point for the dent S.

And vice versa, for a rubber sheet 06 with a known parameter α, for example, already measured at the factory, with the corresponding algebraic prescription, as well as with a known cylinder geometry (diameters D _GZK , D _wPZ ) gear ratio I of cylinders 01, 02 or expected slippage for the corresponding dent S can be calculated in advance. In accordance with the expression [9] you can write:

The parameter α thereby allows to quantitatively determine the change in the effective diameter D _{wGZ of the} transfer cylinder 02 for a certain dent S and, therefore, in the case of rotation of the cylinders 01, 02 with angular synchronism, the resulting slippage can also be calculated.

When calculating cylinders 01, 02, for example, to prevent slippage or excessive forces for the drive, using the known constant, at least at some intervals, parameter α for the provided layer 06 of thickness t and with a given format (diameters D _GZK , D _wPZ ) one of the cylinders 01, 02 determines the diameter D _wPZ , D _{GZK of the} other cylinder 01, 02. In this way, the required diameter D _{GZK of the} core 03 can be calculated, respectively, the total diameter D _GZK + 2t of the transfer cylinder 02, for example, for a rubber sheet 06 s known parameter α, with the desired curve in the diagram (vertical height and elevation), reflecting the relationship between the gear ratio I and the dent S, as well as with a known diameter D _wPZ , for example, plate cylinder 01.

The character of the run-in, or deformation (tension, or compression) of layer 06 described by parameter α (rubber web 06, sleeve, metal plate, coating, décor, paint roller cover) can thus be taken into account when choosing the diameters D _GZK , D _wGZ , D _wPZ for perfect break-in. Using parameter α for a given rubber web 06, it is possible to calculate the diameters D _GZK , D _wGZ , D _wPZ so that an optimal run-in is achieved. In a preferred embodiment, the diameters D _GZK , D _wGZ , D _wPZ can also be optimized so that the deviation from the optimal break-in for the spectrum of various rubber bands 06 is minimized. For the use of various rubber sheets 06 or a special rubber sheet 06 in an existing printing apparatus, the number, respectively the thickness of the gaskets between the side surface and the rubber sheet 06 in order to _{adjust the} diameter D _GZK can be calculated before printing and taken into account during installation.

Conversely, the method allows you to select a suitable layer 06, for example a rubber sheet 06, based on a given geometry of the printing apparatus (diameters D _GZK , D _wPZ ) so that extreme cases are first algebraically calculated for the nature of the movement depending on the dent S, and then specify at least in some segments, the desired curve path (rise, vertical height on the diagram) for the nature of the movement of the real layer 06 and, finally, the parameter α for the required layer is “cleaned” with respect to the geometry of the measuring device 06, for example, of the rubber web 06, in that the position of the desired curve, respectively, of the desired value relative to the algebraically obtained curves, respectively, of the values is determined for at least one dent value S.

After that, a rubber web 06 with the corresponding parameter α can be selected if this parameter was obtained using the same algebraic prescription for describing the relative position. If different algebraic prescriptions were used to measure and determine the parameter (on the rubber sheet 06 and to determine the desired parameter α using the geometry of the cylinders 01, 02, then the knowledge of these prescriptions can be converted into one another.

With a change in the geometry of the cylinders, the straight lines of the theoretically determined gear ratios I _real , I _komp , I _inkomp “roll over” and the intersection point with the I-axis shifts in such a way that with a constant parameter α (rubber web 06 is the same) the absolute position of the lines for the real gear I _real relationship changes, while the relative position is maintained.

With a change in the parameter α (choice of rubber web 06 with a different characteristic), but with a constant geometry of the cylinders in the printing apparatus, the straight lines of theoretically determined gear ratios I _real , I _komp , I _inkomp remain, however the relative position of the straight lines for the real gear ratio I _real "caps over" and gets another lift.

Therefore, a dekel 06 with a suitable parameter α for a certain geometry of the printing apparatus is not suitable, in general, for a geometry different from it, in particular for a different ratio of diameters D _GZK , D _wGZ .

In an optimal embodiment, with a running-in of decal 06 practically independent of the relative position of the rollers, the geometry of the printing apparatus is coordinated with each other so that in at least one denting interval S of interest, respectively, relative dents S * rise in Fig. 4 between the gear ratio I _real and the dent S is basically zero, i.e. dI _real / dS = 0. The relative dent S * in this case is determined through the ratio S / t, i.e. through a dent S, referred to the initial, non-deformed thickness t of the layer 06. The corresponding interval for relative dents S * in the general case can be, for example, from 6% to 10%, in particular from 6.5% to 9%. However, for these intervals it may be appropriate to make a distinction depending on the “type” of contact zones. For the contact zone between the transfer cylinder 02, 11 and the plate cylinder 01, 12, the interval interesting for practice is, for example, from 6% to 7%, while for the contact zone between the transfer cylinder 02, 11 and the planetary cylinder 16, it is from 9% to 10%. The rise of dI _real / dS in these intervals in absolute terms should be no more than 0.01 1 / mm, in particular no more than 0.005 1 / mm. The considered thicknesses t for the preferred grade of decals 06 are, for example, from 1.6 to 2.5 mm, while for the second preferred grade with lower elasticity, respectively lower specific pressure and / or lower rise in the characteristic curve of elasticity (specific pressure, referred to the dent), the thicknesses t are, for example, from 3.5 to 5 mm.

All the printing apparatuses shown in FIGS. 5-8, respectively, printing sections are presented for simplicity in a linear form, i.e. the rotation axes of the participating cylinders are in the figures in the same plane. However, the cylinders of the printing apparatuses can also be located at an angle to each other, so that the options shown below are equally suitable for use in the case of linear and angular arrangements of cylinders, respectively cylinder groups.

Figures 5-6 show an optimally configured printing section 07, which is made in the form of a so-called double printing apparatus 07. The transfer cylinder 02 of the first cylinder pair 01, 02, coupled with the plate cylinder 01, interacts through the printing material 08, for example, web 08, with also in the form of a transfer cylinder 11 by a counter-pressure cylinder 11, to which a plate cylinder 12 is also attached. All four cylinders 01, 02, 11, 12 are driven mechanically independently from each other by means of various gears bottom engines 13 (figure 5). According to one variation of this embodiment, the plate and transfer cylinders 01, 02, 11, 12, respectively combined with each other, are driven in rotation from the drive motor 13 as a single pair of cylinders (via the plate cylinder 01, 12, through the transfer cylinder 02, 11, or in parallel ) (Fig.6).

The plate cylinders 01, 12 and the transfer cylinders 02, 11 are made in the first embodiment in the form of cylinders 01, 02, 11, 12 of double coverage, i.e. with coverage essentially equal to two vertical printed pages, in particular two newspaper pages. They have effective diameters D _wGZ , D _wPZ from 260 to 400 mm, in particular from 280 to 350 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with the parameter α ranging from 0.989 to 1,000, for example from 0.989 to 0.999, in particular from 0.993 to 0.997. Thanks to this configuration, running-in is guaranteed, respectively, the drive of cylinders 01, 02, 11, 12 is guaranteed with virtually no slippage and practically no transmission of torque. The ratio I _real of the rotational speeds is preferably chosen so that when varying dents S, or relative dents S *, at least in the above interval for relative dents S * of the corresponding cylinder pair, it differs by 0.002, in particular by 0.001, from 1,000 / n . The variable n in this regard is the ratio between the number of printed pages in the circumferential direction on the transfer cylinder 02, 11 and the number of printed pages of the same size in the circumferential direction of the plate cylinder 01, 12. Since in this embodiment both cylinders 01, 02 11, 12 have double coverage, then n = 1 and the deviation from 1,000 is at most 0.002, in particular 0.001.

In the second embodiment, plate cylinders 01, 12 and transfer cylinders 02, 11 are made in the form of cylinders 01, 02, 11, 12 of simple coverage, i.e. with coverage basically equal to one vertical printed page, in particular one newspaper page. They have effective diameters D _wGZ , D _wPZ from 150 to 190 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with the parameter α ranging from 0.980 to 1,000, for example from 0.980 to 0.995, in particular from 0.983 to 0.993. The ratio I _real of the rotational speeds in this case is also preferably chosen so that when varying dents S, or relative dents S *, at least in the above interval for relative dents S * of the corresponding cylinder pair, it differs by a maximum of 0.002, in particular by 0.001 , from 1,000 / n, i.e. differed by 0.002, in particular by 0.001, from 1,000.

In (not shown in the drawing) the third embodiment, the plate cylinders 01, 12 are made in the form of cylinders 01, 12 of simple coverage with effective diameters D _wPZ from 150 to 190 mm, and the transfer cylinders 02, 11 are made in the form of cylinders 02, 11 of double coverage with effective diameters D _wGZ from 260 to 400 mm, in particular from 280 to 350 mm. On the lateral surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with a parameter α ranging from 0.987 to 1,000, in particular from 0.997 to 1,000. The ratio I _real of the rotational speeds in this case is also preferably chosen so that when varying dents S, or relative dents S *, at least within the above interval for relative dents S * of the corresponding cylinder pair, it differs by a maximum of 0.002, in particular by 0.001, from 1,000 / n, i.e. in this case, when n = 2, so that it differs by 0.002, in particular by 0.001, from 0.500.

Figures 7 and 8 show a printing section 14, which can be operated either as part of a larger printing section, for example, a five-, nine- or ten-cylinder printing section, or as a three-cylinder printing section 14. The transfer cylinder 02 interacts with a non-printing ink cylinder 16, for example, a counter-pressure cylinder 16, in particular a planetary cylinder 16. In this case, the “soft” side surface of the transfer cylinder 02 interacts with the “hard” side surface of the plate cylinder 01 on one side and with a “gesture” th "satellite cylinder side surface 16 on the other side. Instead of the effective diameter D _wPZ , which was used in the previous discussion for plate cylinder 01, it is necessary to insert D _wSZ as the diameter of the planetary cylinder 16 in the equations describing the interaction between the transfer cylinder and planetary cylinder 16. In the embodiment according to FIG. 7 c, at least independently driven by gear 02 and planetary 16 cylinders, the planetary (planetary) cylinder 16 has (have) its own drive motor 13, while a pair consisting of mechanically knitted plate and transfer cylinders 01, 02, is rotated from a common drive motor 13 (Fig.7), or each cylinder of the pair is driven from its own drive motor 13 mechanically independently from each other (Fig.8).

Shaped cylinders 01, transfer cylinders 02 and planetary cylinders 16 are made in the first embodiment in accordance with FIG. 6 as double- _coated cylinders 01, 02, 16 with effective diameters D _wGZ , D _wPZ , D _wSZ from 260 to 400 mm, in particular from 280 to 350 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with a parameter α ranging from 0.990 to 0.999, in particular from 0.993 to 0.997. Thanks to this configuration, running-in is guaranteed, respectively, the drive of cylinders 01, 02, 16 is guaranteed with virtually no torque transmission.

In the second embodiment, in accordance with FIGS. 7 or 8, the plate cylinders 01, the transfer cylinders 02 and the planetary cylinders 16 are designed as simple-coverage cylinders 01, 02, 16, i.e. with coverage basically equal to one vertical printed page, in particular one newspaper page. They have effective diameters D _wGZ , D _wPZ from 120 to 180 mm, in particular from 130 to 170 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with the parameter α ranging from 0.980 to 0.995, in particular from 0.983 to 0.993.

In (not shown in the drawing) the third embodiment, in accordance with Figs. 7 or 8, plate cylinders 01, 12 are made in the form of simple-coverage cylinders 01 with effective diameters D _wPZ from 120 to 180 mm, in particular from 130 to 170 mm, and transfer cylinders 02, as well as planetary cylinders 16 are made in the form of double-coverage cylinders 02, 16 with effective diameters D _wGZ , D _wSZ from 260 to 350 mm, in particular from 280 to 320 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with a parameter α ranging from 0.985 to 0.995, in particular from 0.990 to 0.995.

In the fourth embodiment (not shown in the drawing) in accordance with FIGS. 7 or 8, the plate cylinders 01 and the transfer cylinders 02 are made in the form of simple-coverage cylinders 01, 02 with effective diameters D _wPZ , D _wGZ from 120 to 180 mm, in particular from 130 to 170 mm, and planetary cylinders 16 are made in the form of cylinders 02, 16 of double coverage with effective diameters D _wSZ from 260 to 350 mm, in particular from 280 to 320 mm. On the side surface of the core 04, the transfer cylinder 02, 11 has at least one dekel 06 with a parameter α ranging from 0.985 to 0.995, in particular from 0.990 to 0.995. If the plate and planetary cylinders 01, 16 are designed with different sizes, then, depending on the requirements, the ideal compromise for this case can be found in both contact zones.

As already noted above, the parameter α of dekel 06 is determined by measuring dekel 06 on a suitable measuring device, followed by processing the results using the appropriate algorithm. Fig. 9 shows an example of a measuring device (top view), and Fig. 10 shows the same measuring device in an enlarged side view, i.e. as it is especially suitable for calculating the parameter α.

The measuring device has at least two cylinders 17, 18, or a roller 17, 18, which are mounted on bearing bearings on the frame 19, in particular with their both sides, with the possibility of rotation. At least one of the cylinders 17, 18, in this case cylinder 17, has a practically incompressible and inelastic, solid side surface. At least one of the two cylinders 17, 18 is set so that the distance a between the axes of rotation of both cylinders 17, 18 can be changed. In the above example, the cylinder 17, made with a “solid” side surface and corresponding to the plate or planetary cylinder 01, 12, 16, is fixed with its ends in the eccentric sleeve 21 with pins on the frame 19. Another cylinder 18 in the example is fixed in the usual way stationary in frame 19. The fastening of the cylinders 17, 18 is made rigid and without gaps. To ensure the rigidity of the mounting, the supports are suitably massive. The absence of backlash is ensured either by a tapered bearing seating or by thermal pressing in. However, the soft cylinder 18 can also be mounted movably, and the solid cylinder 17 is stationary, or both cylinders 17, 18 can be fixedly mounted. Mobility can be realized under certain conditions also by turning the cylinder 17, 18, mounted in levers or in linear guides.

The eccentric sleeve 21, in a preferred embodiment, has an eccentricity e equal to the double, respectively quadruple thickness t, usually measured by the device layer 06 (from n2 · t to 4 · t); said eccentricity is, for example, from 3 to 8 mm, in particular from 4 to 6 mm for one grade of layers 06, and from 8 to 16 mm, in particular from 10 to 14 mm for a thicker layer. The position of the eccentricity e forms, with the plane E in the main position, an angle γ equal to from 75 to 120 °, in particular from 85 to 110 °. As the main position, here we consider the relative position of the cylinders 17, 18, in which there is a linear touch of both side surfaces, mainly without the formation of a dent S.

The rotation of the eccentric sleeve 21 in the preferred embodiment is carried out by means of a lever 22 rigidly connected to the eccentric sleeve 21, which, under the action of the actuator 23, can rotate around the swing axis of the eccentric sleeve 21. The actuator 23 may have a different design in principle, for example, it can be made form of a drive screw driven by the engine. In the considered embodiment, the actuator 23 is made in the form of a cylinder 23 loaded with a working fluid, pivotally mounted on the frame 19 and pivotally connected by its piston rod 24 to the lever 22 (or vice versa).

The actuator 23 rotates the lever 22 in the direction of the stop 26, restricting the pivoting movement of the eccentric sleeve 21 to the side of smaller distances a between the axes of the cylinders 17, 18. This stop 26 is made so that it can adjust the path limit for the lever 22, but it can be fixed in the desired position relative to the frame 19. In the example, the lead screw 27 rotated in a stationary thread relative to the frame, for example a pin or a screw with a thin thread, has a stop 26 at its end. By rotating the pin 27, by hand or by electric motor Atelier, you can move the emphasis 26 further in the direction of the lever 22 or in the opposite direction from it.

The movement, respectively the position of the eccentric sleeve 21, respectively, of the lever 22 in the preferred embodiment is determined using the device 28 for measuring the path. In this example, this measurement is carried out using a dial indicator 28 fixed on the frame, the free and movable pusher of which interacts with the lever 22. It is advisable to arrange the dial indicator 28 in which one turn of the arrow corresponds to a linear movement of the pusher by less than 0.05 mm, in particular less than 0.02 mm or this distance. Instead of mechanical execution, the device 28 for measuring the path can also be made in another way, for example, in the form of an electric and / or magnetic device, in which case the value of the measured value is either converted from a mechanical into an electrical signal, or in the form of a directly received electrical signal, may be routed to a (not shown) data processing device.

The measurement accuracy is ensured by a system in which the distance b taken between the swing axis A between the swing axis A and the point of movement measurement performed by the measuring device is large in comparison with the eccentricity e. The ratio of the distance b to the eccentricity e in the preferred embodiment is greater than or equal to 20, in particular greater than or is equal to 50. From the eccentricity e, the distance b, the resolution of the measuring device and the known line for turning the axis of rotation, the displacement of the cylinder 17 on its side surface is determined. A measurement device made in this way provides reproducible measurement accuracy when dents S is formed with a depth less than or equal to 0.005 mm.

In another embodiment of the invention, the emphasis is driven by an electric motor, wherein the position of the emphasis 26 serves as an electrical signal or is set as an electrical signal. At the same time, the path measuring device 28 outputs the measured value in the form of an electrical signal. In this embodiment, one or more positions for cylinder 17, respectively one or more distances a between the axes, can be automatically processed through a data processing device or control unit.

In another (not shown) embodiment, the installation of the stop 26 and the device 28 for measuring the path is carried out using only one means, for example, a threaded spindle driven by an electric motor with adjustment of the run-out angle of the rotor. The data processing device receives information about the position of the angle through the position, and vice versa.

To set the indentation zero point, i.e. position, in which between the two cylinders 17, 18 there is only a linear touch without the formation of a dent S, the measuring device is equipped, for example, with one or more (not shown) light sources on one side of the gap between the cylinders 17, 18. When the two cylinders 17 come closer together , 18 the zero point of indentation can be set with the help of a light gap, precisely when light is no longer incident through the gap. In manual mode, light can be detected on the other side of the slit by the human eye or in automatic mode, for example, by one or more detectors. In automatic mode, the signal is transmitted further to a (not shown) data processing device. The described application of light provides a zero point of indentation with an accuracy of less than or equal to 0.005 mm, in particular less than or equal to 0.002 mm.

To determine the nature of the running-in of both cylinders 17, 18, it is provided that one of the two cylinders 17, 18 is driven in rotation from an external drive 29, for example, from an electric motor 29. In Fig. 9, an electric motor 29, for example, through a drive wheel 36, for example a belt pulley 36 through transmission 37, for example a belt 37, in particular a timing belt 37, drives a driven wheel 38, for example a belt pulley 38, on a solid cylinder 17, while a soft cylinder 18 is driven only by friction. It is also possible to drive the soft cylinder 18 through the belt 37 from the electric motor 29, while the solid cylinder 17 will rotate only as a result of friction. In an optimal embodiment, the electric motor can be alternately connected with either a hard or soft cylinder 18, 17. According to another embodiment, one of the cylinders 17, 18 or even both has one electric motor 29 with an adjustable position or at least , with an adjustable speed of rotation. This electric motor drives the axis of the corresponding cylinder. The negative impact on the nature of the break-in provided by the drive of the cylinder 17, 18 through friction is reduced due to the use of bearings of extremely low friction. Due to this, the maximum deviation of the measured gear ratio I from the "true" gear ratio I does not exceed 0.01%.

The angular velocity or the angle of rotation of both cylinders 17, 18 is measured by means of a sync sensor 31, 32 located on the corresponding cylinder 17, 18 or on the corresponding axle, for example, an optoelectronic angle decoder.

In order to prevent interruption of contact between the two cylinders 17, 18 rolling over each other, the hard cylinder 17 is preferably provided with a continuous, non-discontinuous side surface in the area in which it rolls along the soft cylinder 18. However, this can also be achieved by arranging “spare printing forms” located on the side surface (in those cases when they are on this surface) with a displacement relative to each other in the circumferential direction (for example, by 180 °), or if the solid cylinder 17 carries only one final “spare printing form”, covering the formed joint, respectively, the channel is flush with the side surface of the corresponding tab 33 (see, for example, Fig. 9). The situation is also the case with the soft cylinder 18, and in Fig. 9, as an example, two decks 06 are shown, offset relative to each other by 180 ° in the circumferential direction, each with a tab 34 extending as much as half the length of the cylinder. This arrangement of decals 06 ensures constant contact of one of the decels with a solid cylinder 17.

For various dents S, the angular velocity of both cylinders 17, 18 and the possible advance, under certain circumstances, respectively, the lag, with great accuracy, are recorded by selsyn sensors 31, 32 and electronics connected in series with them. The drive is alternately through a hard or soft cylinder 17, 18. The adjustment of the axle distance a is made by moving the movable cylinder 17, 18 in its eccentric sleeve by turning it. The above regulation is made, in particular, more comfortable than the printing press. After that, the zero point of indentation is determined using a light gap between the side surfaces (for example, using a fluorescent lamp under the gap between the cylinders). And finally, by fine adjustment (emphasis 26), the dent S is accurately determined and measured (device 28 for measuring the path).

Based on the known geometry of the cylinders 17, 18, as well as the measuring points, respectively, the measuring points for determining the dent S (for S> 0) and using algebraic prescriptions, such as, for example, equations [5], [8] and [9], calculate the parameter α, as described above.

List of items

01 roller, cylinder, plate cylinder, backpressure cylinder

02 roller, cylinder, transmission cylinder

03 clearance between the rollers

04 rod

05 -

06 layer, rubber sheet, dekel

07 printing section, double printing apparatus

08 printed material, canvas

09 -

10 -

11 roller, cylinder, transfer cylinder, backpressure cylinder

12 roller, cylinder, plate cylinder

13 drive motor

14 printing section, three-cylinder printing section

fifteen -

16 roller, cylinder, counterpressure cylinder, planetary cylinder

17 roller, cylinder

18 roller, cylinder

19 frame

twenty -

21 eccentric bush

22 lever

23 actuator, cylinder

24 piston rod

25

26 emphasis

27 threaded finger

28 path measuring device, dial gauge

29 drive, electric motor

thirty

31 selsyn sensor

32 selsyn sensor

33 bookmark

34 bookmark

35

36 drive wheel, belt drive

37 gear, belt, timing belt

38 drive wheel, belt drive

D _wGZ diameter

D _wPZ diameter

D _wGZK diameter

D _wSZ diameter

ω circular frequency

W _gz frequency

W _PZ frequency

and distance

And the difference

A ₀ cross-sectional area

A ₁ cross-sectional area

b distance

In difference

eccentricity

E plane

α parameter

γ angle (e, E)

I ratio of rotational speeds, gear ratio

I _real speed ratio, gear ratio, measured, real

I _komp speed ratio, gear ratio, with compressible material

I _inkomp speed ratio, gear ratio, with incompressible material

L length

n variable

n _GZ speed

n _PZ speed

S dent

S * dent, relative

t thickness

v ₀ speed

v ₁ speed

v _p surface speed

V _gi speed

V _ga speed

Claims (49)

1. The method of selecting the layer (06) on the roller (01, 02, 11, 12; 16), in which first, at least in parts, depending on the indentation (S), theoretically obtained for purely compressible, are determined from the given geometry of the printing apparatus and in a purely incompressible case, the extreme values of the gear ratio (I _komp , I _inkomp ), establish, at least in parts, the desired relative position of the gear ratio (I _real ) of the real layer (06) with respect to the extreme values of the gear ratio (I _komp , I _inkomp ), and by matching at least in parts of the desired characteristic curve with theoretically determined characteristic curves of extreme values (I _komp , I _inkomp ) using the algebraic rule, the parameter (α) adjusted for the special geometry for the desired layer (06) is obtained. 2. The method according to claim 1, characterized in that the parameter (α) characterizing the layer (06) is first obtained by measuring on the measuring device, followed by adjusting the geometry of the measuring device using the same algebraic rule. 3. The method according to claim 1, characterized in that the algebraic rule expresses the relative position of the measured gear ratio (I _real ) to both extreme values of the gear ratio (I _komp , I _inkomp ) for the corresponding dent (S). 4. The printing section with at least two interacting rollers (01, 02, 11, 12, 16), and at least one of the rollers (02, 11) has on its side surface an elastic layer (06), and the other roller (01, 12, 16) has a practically undeformable lateral surface, characterized in that the layer (06) for at least one portion of the relative dent (S *) has a parameter (α) describing its elastic properties equal to 0.980 to 0.999, moreover, this parameter is obtained from the algebraic rule

where I _komp , I _inkomp are gear ratios for extreme cases of a purely compressible, respectively, purely incompressible layer (06), and I _real means the desired gear ratio. 5. The printing section according to claim 4, characterized in that the gear ratio I _real when varying in at least one portion of the relative dent (S *) of the layer (06) differs by no more than 0.002, in particular not more than 0.001 from 1,000 / n, and n is the ratio of the number of printed pages in the circumferential direction on the roller (02, 11) with a layer (06) to the number of printed pages on another roller (01, 12, 16). 6. The printing section with at least two interacting rollers (01, 02, 11, 12, 16), and at least one of the rollers (02, 11) has on its side surface an elastic layer (06), and the other roller (01, 12, 16) has a practically undeformable lateral surface, characterized in that the layer (06) and the geometry of both rollers (01, 02, 11, 12, 16) are mutually consistent with each other so that the gear ratio ( I _real) of rollers (01, 02, 11, 12, 16) for variation of at least one portion relative dents (S *) layer (06) differs by not more than 0,002 from 1,000 / n, wherein n represents the ratio of the number of printed pages in the circumferential direction on the roller (02, 11) with a layer (06) to the number of printed pages on the other roller (01, 12, 16). 7. The printing section according to claim 6, characterized in that the gear ratio (I _real ) of the rollers (01, 02, 11, 12, 16) when varying at least one section of the relative dent (S *) of the layer (06 ) differs by no more than 0.001 from 1,000 / n, and n represents the ratio of 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 another roller (01, 12, 16). 8. The printing section with at least two interacting rollers (01, 02, 11, 12, 16), and at least one of the rollers (02, 11) has on its side surface an elastic layer (06), and the other roller (01, 12, 16) has a practically non-deformable lateral surface, characterized in that the layer (06) and the geometry of both rollers (01, 02, 11, 12, 16) are matched to each other so that at least , for one section of the relative dent (S *), the derivative (dI _real / dS), i.e. the quotient of dividing the gear differential (I _real ) by the dent differential (S) differs from zero by no more than 0.01 1 / mm. 9. The printing section according to claim 6 or 8, characterized in that the layer (06), at least for the relative dent section (S *), has a parameter (α) describing its elastic properties equal to from 0.980 to 1.000, this parameter derived from an algebraic rule

where I _komp , I _inkomp are gear ratios for extreme cases of a purely compressible, respectively, purely incompressible layer (06), and I _real means the desired gear ratio. 10. The printing section according to claim 4 or 6, characterized in that at least for the relative dent portion (S *) is the derivative (dI _real / dS), i.e. the quotient of dividing the gear differential (I _real ) by the dent differential (S) differs from zero by no more than 0.01 1 / mm. 11. The printing section of claim 10, wherein the derivative (dI _real / dS) is substantially zero. 12. The printing section according to one of claims 4 to 8, characterized in that the relative dent area (S *) for the contact point is made in the form of a transfer cylinder (02, 11) and made in the form of a plate cylinder (01, 12) rollers (01, 02, 11, 12) is from 6 to 7%. 13. The printing section according to claim 9, characterized in that the relative dent area (S *) for the contact point is made between the transfer cylinder (02, 11) and the rollers (01, 12) made in the form of a plate cylinder (01, 12) , 11, 12) is from 6 to 7%. 14. The printing section according to claim 10, characterized in that the relative dent area (S *) for the contact point is made between the transfer cylinder (02, 11) and the rollers (01, 12) made in the form of a plate cylinder (01, 12) , 11, 12) is 6 - 7%. 15. The printing section according to one of claims 4 to 8, characterized in that the relative dent area (S *) for the contact point is made between the transfer cylinder (02, 11) and the rollers (01) made in the form of a planetary cylinder (16) , 02, 11, 12) is 9 - 10%. 16. The printing section according to claim 9, characterized in that the relative dent area (S *) for the point of contact between the rollers made in the form of a transfer cylinder (02, 11) and the rollers (01, 02, 11 made in the form of a planetary cylinder (16) , 12) is 9 - 10%. 17. The printing section according to claim 10, characterized in that the relative dent area (S *) for the contact point between the rollers made in the form of a transfer cylinder (02, 11) and the rollers (01, 02, 11 made in the form of a planetary cylinder (16) , 12) is 9 - 10%. 18. The printing section according to claim 4, characterized in that both rollers (01, 02, 11, 12, 16) have an effective diameter (D _wGZ , D _wPZ ) of each 260 - 350 mm, and the parameter (α) of the layer (06 ) is 0.989 - 1,000. 19. The printing section according to claim 9, characterized in that both rollers (01, 02, 11, 12, 16) have an effective diameter (D _wGZ , D _wPZ ) of each 260 - 350 mm, and the parameter (α) of the layer (06 ) is 0.989 - 1,000. 20. The printing section according to one of claims 4 to 8, characterized in that both rollers (01, 02, 11, 12, 16) have an effective diameter (D _wGZ , D _wPZ ) of each 120 - 180 mm, and the parameter (α ) of layer (06) is 0.980 - 0.990. 21. The printing section according to claim 9, characterized in that both rollers (01, 02, 11, 12, 16) have an effective diameter (D _wGZ , D _wPZ ) of each 120 - 180 mm, and the parameter (α) of the layer (06 ) is 0.980 - 0.990. 22. The printing section according to claim 4, characterized in that the roller (02, 11) bearing the elastic layer (06) has an effective diameter (D _wGZ , D _wP Z) 260 - 400 mm, and the other roller (01, 16 ) has an effective diameter (D _wGZ , D _wPZ ) of 150 - 190 mm and the parameter (α) of layer (06) is 0.987 - 1.000. 23. The printing section according to claim 9, characterized in that the roller (02, 11) bearing the elastic layer (06) has an effective diameter (D _wGZ , D _wPZ ) 260 - 400 mm, and the other roller (01, 16) has an effective diameter (D _wGZ , D _wPZ ) of 150 - 190 mm and the parameter (α) of the layer (06) is 0.987 - 1.000. 24. The printing section according to one of claims 4, 6 or 8, characterized in that the roller (02, 11) carrying the elastic layer (06) is made in the form of a transfer cylinder (02, 11), and the roller (01, 12 ), having a practically undeformable lateral surface, is made in the form of a plate cylinder (01, 12). 25. The printing section according to one of claims 4, 6 or 8, characterized in that the roller (02, 11) bearing the elastic layer (06) is made in the form of a transfer cylinder (02, 11), and the roller (16), having a practically undeformable lateral surface, made in the form of a planetary cylinder (16). 26. The printing section according to one of claims 4, 6 or 8, characterized in that both rollers (01, 02, 11, 12, 16) are made in the form of interacting rollers (01, 02, 11, 12, 16) of the ink apparatus . 27. The printing section according to claim 26, characterized in that one of the rollers (01, 02, 11, 12, 16) has a motor drive, and the other roller (01, 02, 11, 12, 16) has a friction drive. 28. The printing section according to paragraph 24, wherein the transfer cylinder (02, 11) interacts with a third roller (16) made in the form of a planetary cylinder (16), which is equipped with a mechanical drive from a drive motor (13) independently of both first rollers (01, 02, 11, 12). 29. The printing section according to one of claims 4, 6 or 8, characterized in that both rollers (01, 02, 11, 12) have a pairwise drive from a common drive motor (13). 30. The printing section according to paragraph 24, wherein both rollers (01, 02, 11, 12) have a pairwise drive from a common drive motor (13). 31. The printing section according to claim 26, characterized in that both rollers (01, 02, 11, 12) have a pairwise drive from a common drive motor (13). 32. The printing section according to one of claims 4, 6 or 8, characterized in that both rollers (01, 02, 11, 12, 16) are driven mechanically independently from two drive motors (13). 33. The printing section according to paragraph 24, wherein both rollers (01, 02, 11, 12, 16) are driven mechanically independently of two drive motors (13). 34. The printing section according A.25, characterized in that both rollers (01, 02, 11, 12, 16) are driven in rotation from two drive motors (13) mechanically independently from each other, 35. The printing section according to claim 26, characterized in that both rollers (01, 02, 11, 12, 16) are driven mechanically independently from two drive motors (13). 36. A device for determining the nature of the running-in of the elastic layer (06), at which the axle distance (a) between the roller (18) carrying the elastic layer (06) and the roller (17) having a substantially undeformable lateral surface changes, and the gear the ratio (I _real ) between both rollers (17, 18), characterized in that at least one of the two rollers (17, 18) is installed in the eccentric bushings (21) on the frame (19). 37. The device according to p. 36, characterized in that the lever (22) increasing the speed of the roller (17) is rigidly connected to the eccentric sleeve (21), the movement of which is determined by the device (28) for measuring the path. 38. A device for determining the nature of the running-in of the elastic layer (06), and the axle distance (a) between the roller (18) carrying the elastic layer (06) and the roller (17) having a substantially undeformable lateral surface is determined, and the gear ratio is measured (I _real ) between both rollers (17, 18), characterized in that the change in the axle distance (a) can be determined on the lever (22) increasing the speed of the roller (17) by the device (28) for measuring the path. 39. The device according to clause 37, characterized in that at least one of the two rollers (17, 18) is installed in the eccentric bushings (21), each of which is rigidly connected to one lever (22). 40. The device according to one of p. 36 or 39, characterized in that the ratio between the distance (b) of the swing axis (A) to the measuring point of the device (28) for measuring the path on the lever (22) and the eccentricity (e) is greater than or equal to twenty. 41. The device according to one of p. 36 or 39, characterized in that the eccentricity (e) and defined by the axis of rotation of the rollers (17, 18) is the plane (E) in the position of the rollers (17, 18), in which the linear contact of both side surfaces with each other, form between themselves an angle equal to 75 - 120 °. 42. The device according to one of p. 36 or 38, characterized in that the corresponding angular velocity and / or position of the angle of rotation is determined by a selsyn sensor (31, 32) provided for each roller (17, 18). 43. The device according to one of p. 36 or 38, characterized in that one of the rollers (17, 18) is rotated by an external drive (29), and the other roller (17, 18) is rotated only by friction with the first one. 44. The device according to item 43, wherein the drive (29) can alternately be connected to one or another roller (17, 18). 45. The device according to one of p. 37 or 38, characterized in that the device (28) for measuring the path is made in the form of an arrow indicator (28) with a resolution of less than or equal to 0.05 mm / 360 °. 46. The device according to one of claims 37 or 38, characterized in that a stop (26) with a variable position is provided for the lever (22). 47. The device according to one of p. 37 or 38, characterized in that the rotation of the lever (22) is carried out using the actuator (23). 48. The device according to one of p. 37 or 38, characterized in that the lever (22) can be installed against the stop (26) using an actuator (23), made in the form of a cylinder (23) filled with a working medium. 49. The device according to one of p. 36 or 38, characterized in that for determining the zero point of indentation, a light source is provided on one side of the gap between the rollers (17, 18).

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