Classifications

• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F13/00—Common details of rotary presses or machines
  • B41F13/08—Cylinders
  • B41F13/193—Transfer cylinders; Offset cylinders
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F30/00—Devices for attaching coverings or make-ready devices; Guiding devices for coverings
  • B41F30/04—Devices for attaching coverings or make-ready devices; Guiding devices for coverings attaching to transfer cylinders
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41N—PRINTING PLATES OR FOILS; MATERIALS FOR SURFACES USED IN PRINTING MACHINES FOR PRINTING, INKING, DAMPING, OR THE LIKE; PREPARING SUCH SURFACES FOR USE AND CONSERVING THEM
  • B41N10/00—Blankets or like coverings; Coverings for wipers for intaglio printing
  • B41N10/02—Blanket structure
  • B41N10/04—Blanket structure multi-layer
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41N—PRINTING PLATES OR FOILS; MATERIALS FOR SURFACES USED IN PRINTING MACHINES FOR PRINTING, INKING, DAMPING, OR THE LIKE; PREPARING SUCH SURFACES FOR USE AND CONSERVING THEM
  • B41N2210/00—Location or type of the layers in multi-layer blankets or like coverings
  • B41N2210/02—Top layers

Definitions

• 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
• 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.
• rollers e.g. B. paper web
• 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.
• 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.
• 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.
• 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.
• the measured values required to form the key figure are, for. B. determined by means of a measuring device having two rollers.
• 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.
• a transfer cylinder of double circumference with an elevator with a code number ⁇ from 0.989 to 0.999 a transfer cylinder with a single circumference with an elevator with code number ⁇ 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 ⁇ 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.
• Fig. 1 passage of a compressible rubber blanket through the nip
• Fig. 5 embodiment for a printing unit
• Fig. 7 embodiment for a printing unit
• FIG. 9 embodiment of a measuring device
• a work machine e.g. B. a printing press
• rollers 01; 02 of an inking unit, a coating unit, or cylinder 01; 02 of a printing unit rollers 01; 02 of an inking unit, a coating unit, or cylinder 01; 02 of a printing unit.
• 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 z ⁇ 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.
• 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.
• a suitable layer 06 e.g. cork or the like
• an ideally incompressible layer 06 e.g. solid rubber
• 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 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:
• 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.
• 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.
• 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. , , - ' - ""
• a measurement to determine the real transmission ratio l rea ⁇ 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.
• a measure ⁇ 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 ⁇ 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 ⁇ can be defined as follows, for example,
• A represents the difference between real and theoretical incompressible
• B represents the difference between theoretical compressible and theoretical incompressible gear ratio I for the same indentation S.
• ⁇ 0 for the case of a real layer 06 which behaves in an ideally incompressible manner
• ⁇ 1 for a real layer 06 which behaves in an ideally compressible manner.
• the characteristic number ⁇ 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 ⁇ 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.
• the delivery behavior (z. B. based on the resulting gear ratio l rea ⁇ ) 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 ⁇ ; 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].
• the characteristic number can be determined on the basis of a single measured value for an indentation S.
• the expected gear ratio I of the cylinders 01; can now be used for a rubber blanket 06 with the known index ⁇ , 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]:
• the characteristic number ⁇ 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.
• 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 ⁇ 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 ⁇ of the other cylinder 02; 01 determined.
• a rubber blanket 06 with a known characteristic number ⁇ , 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.
• the forme cylinder 01, the required diameter D GZK of the core 03, or the total diameter D wGZ ⁇ + 21 of the transfer cylinder 02 can be determined.
• 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 ⁇ can also be used to select the diameter D GZ ⁇ ' , D wG z ", D wPZ flow in for ideal processing.
• diameters D GZK ; D wGZ ; D wPZ can be designed in such a way that optimum processing is achieved.
• 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.
• 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.
• 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 ⁇ 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 ⁇ 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 ⁇ on the rubber blanket 06 and for the determination of the desired index ⁇ 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.
• An elevator 06 with a suitable characteristic number ⁇ 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 .
• the slope in Fig. 4 between ratio l rea ⁇ and indentation S is essentially zero, ie dl rea ⁇ / 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%.
• 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.
• / 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.
• 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.
• FIG. 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).
• 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.
• the transfer cylinder 02; 11 each have at least one elevator 06 with a characteristic number ⁇ 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 ⁇ 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.
• 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.
• the transfer cylinder 02; 11 each have at least one elevator 06 with a characteristic number ⁇ 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.
• the transfer cylinder 02; 11 each have at least one elevator 06 with a code number ⁇ from 0.987 to 1,000, in particular from 0.997 to 1,000.
• 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.
• 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.
• the transfer cylinder 02; 11 at least one elevator 06 with a characteristic number ⁇ 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.
• 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.
• the transfer cylinder 02 On the outer surface of the core 04, the transfer cylinder 02 has at least one elevator 06 with a characteristic number ⁇ from 0.980 to 0.995, in particular from 0.983 to 0.993.
• 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.
• 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.
• a fourth embodiment (not shown) for FIGS.
• 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.
• 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.
• 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.
• 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.
• the bearings are made correspondingly solid.
• the play is either due to a tapered seat of the bearing or due to thermal shrinking.
• 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.
• 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 ⁇ 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.
• 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
• 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.
• 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.
• 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).
• 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.
• 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.
• the stop is designed to be movable by a motor, the position of the stop 26 being present or predetermined as an electrical signal.
• the measured value of the path measurement 28 is in the form of an electronic signal.
• 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.
• 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.
• 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.
• 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.
• the signal is forwarded to the data processing (not shown).
• 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.
• the electric motor can be exchanged with the hard or the soft cylinder 18; 17 connectable.
• 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.
• the hard cylinder 17 advantageously has a continuous, uninterrupted lateral surface in the area rolling with the soft cylinder 18.
• 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 encoder 31; 32 and a downstream electronics 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.
• 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.
• 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).

Landscapes

• Engineering & Computer Science (AREA)
• Mechanical Engineering (AREA)
• Inking, Control Or Cleaning Of Printing Machines (AREA)
• Printing Plates And Materials Therefor (AREA)
• Printing Methods (AREA)
• Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
• Control Or Security For Electrophotography (AREA)
• Adjustment And Processing Of Grains (AREA)
• Dot-Matrix Printers And Others (AREA)
• Printers Or Recording Devices Using Electromagnetic And Radiation Means (AREA)

Applications Claiming Priority (3)

Publications (2)

Family

ID=23463881

Family Applications (1)

Country Status (8)

Families Citing this family (5)

Family Cites Families (2)

• 2002
  • 2002-08-28 JP JP2003583747A patent/JP2005519794A/ja active Pending
  • 2002-08-28 WO PCT/DE2002/003142 patent/WO2003086760A1/fr active Application Filing
  • 2002-08-28 DE DE10296772T patent/DE10296772D2/de not_active Withdrawn - After Issue
  • 2002-08-28 AT AT02762256T patent/ATE466729T1/de not_active IP Right Cessation
  • 2002-08-28 DE DE50214420T patent/DE50214420D1/de not_active Expired - Lifetime
  • 2002-08-28 CN CN02820928.1A patent/CN1575234A/zh active Pending
  • 2002-08-28 RU RU2004106149/12A patent/RU2291058C2/ru not_active IP Right Cessation
  • 2002-08-28 AU AU2002328265A patent/AU2002328265A1/en not_active Abandoned
  • 2002-08-28 EP EP02762256A patent/EP1492674B1/fr not_active Expired - Lifetime
  • 2002-08-28 DE DE20213169U patent/DE20213169U1/de not_active Expired - Lifetime

Non-Patent Citations (1)

Also Published As

Similar Documents

Legal Events