EP1637326A2 - Groupe d'impression offset comprenant un cylindre de transfert avec un recouvrement élastique - Google Patents

Groupe d'impression offset comprenant un cylindre de transfert avec un recouvrement élastique Download PDF

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Publication number
EP1637326A2
EP1637326A2 EP05108319A EP05108319A EP1637326A2 EP 1637326 A2 EP1637326 A2 EP 1637326A2 EP 05108319 A EP05108319 A EP 05108319A EP 05108319 A EP05108319 A EP 05108319A EP 1637326 A2 EP1637326 A2 EP 1637326A2
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EP
European Patent Office
Prior art keywords
printing unit
unit according
cylinder
transfer cylinder
transfer
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Withdrawn
Application number
EP05108319A
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German (de)
English (en)
Inventor
Oliver Hahn
Ralf Christel
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Koenig and Bauer AG
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Koenig and Bauer AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
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Publication date
Priority claimed from DE102004056389A external-priority patent/DE102004056389B4/de
Priority claimed from DE102004056388A external-priority patent/DE102004056388B3/de
Application filed by Koenig and Bauer AG filed Critical Koenig and Bauer AG
Publication of EP1637326A2 publication Critical patent/EP1637326A2/fr
Withdrawn legal-status Critical Current

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    • 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
    • B41F13/22—Means for cooling or heating forme or impression cylinders

Definitions

  • the invention relates to a printing unit of an offset printing machine with at least one forme cylinder and a transfer cylinder according to the preamble of claim 1.
  • the nip of the transfer cylinder paper can cause wave or even wrinkling of the paper. This is the case with small diameter / bale width ratios, in particular so with single-circumference transfer cylinders and double- or multi-width paper webs (i.e., 2 ... n printing plates wide).
  • the wave formation can lead to passer problems, z. B. to a distortion of the image.
  • the wrinkling leads to waste.
  • EP 1 428 658 A1 shows a convex forme cylinder.
  • DE 2 151 650 shows a transfer cylinder with a convex lateral surface.
  • Post-published WO 2005/005157 A1 describes a transfer cylinder a convex bale on which a single, trained as a sleeve elevator is arranged with different thicknesses.
  • the invention has for its object to provide a printing unit of an offset printing machine with at least one forme cylinder.
  • the printing cylinder is cambered, and thus has (also) a non-constant diameter in the printing area of the bale.
  • the local diameter is selected as a function of the location on the cylinder axis such that the settlement differences induced by the deflection (due to the compressive stress) are substantially compensated, but at least reduced to such an extent that no wrinkling or troublesome wave formation occurs ,
  • the transfer cylinder is convexly cambered.
  • the optimum profile of the crown depends on the effective diameter of the blanket cylinder change, .DELTA.D more, at a Eindschreibungs selectedung the blanket, .DELTA.s, within the typographically relevant Eindschreibungs Kunststoffes [S min S max ...] from. Since ⁇ D effective / ⁇ s depends on the rubber blanket, a selected crowning profile is generally only favorable for one type of blanket or blanket class (ie within a certain value range of ⁇ D / ⁇ s).
  • the size of the indentation changes over the bale width depend on the deflection, and thus on the line forces (and the cylinder arrangement).
  • the line forces in turn result from the surface pressure required in the respective nips and the spring characteristic of the rubber blanket.
  • An additional advantage of a (convex) crowning is also a smaller variation of the compressive stress across the bale width. Basically, however, can be achieved by bombing a rubber blanket over the bale width constant effective diameter at the same time constant compressive stress. Only a compromise is possible.
  • a surface profile of the transfer cylinder is designed so that the pressure differences that occur as a result of cylinder deflection due to the compressive stress on the bale width, balanced in one (or more) nip (s) or significantly reduced become.
  • the surface profile of the transfer or impression cylinder is designed so that wrinkling of the paper is prevented by the variation of the resultant of the local diameter and the local pressure effective diameter of the cylinder in one or more nips over the bale width is sufficiently low.
  • the surface profile is expediently designed so that the wave formation is eliminated or reduced to such an extent that as a result no more relevant register deviations arise and that sliding is prevented.
  • the surface profile for a particular type of rubber blanket or a optimized blanket class wherein the blanket a certain range of ⁇ D effective / ⁇ S, wherein ⁇ D wirk the Wirk thoroughly relevant Eindschreibdungs Kunststoffes [S min ... S max ], or
  • the surface profile is optimized for a specific line force range in the nip.
  • the surface profile is optimized for a certain line force range in the nips, with a specific nip arrangement around the cylinder.
  • the surface profile is optimized for a particular type of rubber blanket or blanket class by its spring characteristic field and the surface pressures necessary in the nips.
  • the surface profile is optimized for a rubber type or a blanket class, which generates a surface pressure of less than 60 N / cm 2 at a depression of 0.20 mm.
  • both cylinders are cambered so that in the mating results in a local pressure in the nip, which results in a sufficiently small variation of the resulting effective diameter over the bale width due to the local diameter to wrinkles or waves of the paper and Passer problems or pushing to avoid.
  • the impression cylinder can also be cambered.
  • the forme cylinder is cambered to pressure differences (and so that effective diameter differences) to compensate for the transfer cylinder, which can lead to sliding or Farbübertragungsparaen. If a crowning of the forme cylinder is required, this is usually concave.
  • the temperature in particular cooling at least one cylinder or at least one arranged in the axial direction of the cylinder zone, whereby the print quality can be significantly increased.
  • the tempered zones may in particular be a width of a lift, e.g. a blanket or a printing plate.
  • a printing blanket which consists of several layers and in extreme cases has a total thickness of 0.55 to 3.65 mm.
  • the Elastic modulus of cellular rubber sheets is between 0.2 to 50 MPa and from 0.1 to 25 MPa.
  • the special structure of the blanket and the properties of the layers a blanket is achieved, which, when pressed together, does not tend to lateral displacement or protuberance.
  • DE 19 40 852 A1 discloses a printing blanket for offset printing, which has a total thickness of approximately 1.9 mm.
  • a shear modulus as stress at 0.25 mm deformation is given at approximately 4.6, 1.9 and 8.23 kg / cm 2 in the case of a thickness of the printing blanket.
  • the goal here is to achieve a rapid recovery after a depression and a narrow thickness tolerance.
  • CH 426 903 discloses an offset printing blanket, with usual indentation depths of 0 to 0.1 mm being present.
  • An increase in the indentation from 0.05 to 0.1 mm requires or has a consequence in the surface pressure of about 20.6 N / cm 2 . That is, in this range for the indentation depth and surface pressures of up to about 40 N / cm 2 there would be a linearized "spring characteristic" with a slope of about 412 N / cm 2 / mm.
  • z. B. in the inking and / or dampening unit, and in particular in the offset process between printing cylinders, resorted to hard-soft regularly on the combination of materials.
  • the surface pressure required for the ink transfer is achieved by pressing a yielding, z. B. elastomeric layer (soft elastomeric cover / elevator, blanket, metal blanket, sleeve) on a cooperating roller with largely incompressible and non-elastic surface area achieved.
  • the contact force has changed permanently due to external conditions (long-wave interference)
  • long-wave interference there is a risk of a print product that is too pale or too color-intensive until the time of a correction (waste).
  • the contact force changes dynamically due to oscillations (short-wave interference), this manifests itself in the formation of visible stripes in the printed product.
  • the achievable with the present invention consist in particular that a lower sensitivity to changes or fluctuations in the contact force (surface pressure) is achieved, and thus a high quality of the printed product is easier to achieve and can be maintained.
  • Special elevators, an optimized design of the cylinders and their arrangement can reduce the influence of the cylinder movements on the ink transfer. In a particularly favorable embodiment with narrow points interrupted or reduced contact the vibration excitation itself is also reduced.
  • the transfer of the fluid is influenced considerably less by vibrations due to the design of the elevator and / or the arrangement of the rollers relative to one another.
  • a spring characteristic, ie a slope in the dependence of the surface pressure of the indentation is at least in an advantageous range for the indentation in pressure-on position highest 700 (N / cm 2 ) / mm.
  • Favorable are less than 400 (N / cm 2 ) / mm.
  • An advantageous range of relative indentation of the elevator in the operating state is z. B. between 10% and 25% between forming and transfer cylinders and 25% to 35% between transfer cylinder and paper.
  • z. B between 10% and 25% between forming and transfer cylinders and 25% to 35% between transfer cylinder and paper.
  • different areas for relative indentation may be preferred in order to achieve optimum results in terms of the required transition of the fluid with the smallest possible influence of fluctuations.
  • the surface pressure varies in pressure-on position in an advantageous embodiment highest in a range between 60 and 220 N / cm 2 , or different sub-ranges for fluids, eg. As printing inks, with greatly different rheological properties and / or different printing processes. Especially in these areas or partial areas, the curve should fulfill the condition on the slope.
  • the width of the contact zone in the nip resulting from the pressing of the rollers has hitherto been kept as small as possible.
  • a widened nip point brings a higher line force and thus a greater static deflection with it.
  • the disadvantage is overcompensated by the elevator according to the invention or the arrangement.
  • the press-in of the elevator is, for example, at least 0.18 mm, in an advantageous embodiment at least 0.25 mm.
  • the resulting width of the nip is z. B. in an advantageous embodiment at least 10 mm, in particular greater than or equal to 12 mm. This can be achieved a favorable surface pressure.
  • a vibration caused by a disturbance for. B. an interruption
  • the excitation of this vibration or its amplitude can be reduced.
  • a width of the interruption in the circumferential direction is at most in the ratio 1: 3 to the width of the nip (impression strip) resulting from the pressing.
  • the elevator or the layer allows the use of slimmer or even longer impression cylinders, d. H. a relation to the diameter large length of the cylinder.
  • Fig. 1 shows a three-cylinder printing unit or a printing unit 20 of an otherwise not shown offset printing machine, which may be part of a larger printing unit such as in particular a nine-cylinder satellite printing unit, as further explained below, but also as a three-cylinder printing unit is operable.
  • the printing unit 20 is in particular three times wide, d. H. for the printing of six axially juxtaposed newspaper pages executed. It comprises a forme cylinder 21, a transfer cylinder 22 abutting thereon and an impression cylinder 23 forming a printing nip 19 with the transfer cylinder 22, in particular a satellite cylinder 23. A web 24 to be printed is guided between transfer cylinder 22 and impression cylinder 23.
  • the form cylinder 21 is associated with a not shown inking unit and also not shown dampening unit.
  • the circumference of the forme cylinder 21 is preferably for receiving two stationary printed pages, z.
  • newspaper pages in broadsheet format by means of two in the circumferential direction on the forme cylinder 21 successively fixable elevators in the form of flexible printing plates, in particular printing plates, formed.
  • the folded at the ends of the printing plates are circumferentially on the forme cylinder 21 over there trained grooves 25 can be mounted and individually exchanged as each in the axial direction equipped with a pressure side single pressure plate.
  • the printing plates or printing plates are not shown in the figures.
  • the length of the usable bale of the forme cylinder 21 is in the axial direction for receiving z.
  • the transfer cylinder 22 is occupied in the longitudinal direction side by side with three elevators 26. They extend in the circumferential direction substantially to the full extent.
  • the elevators 26 are alternately offset from each other, whereby the vibration behavior is favorably influenced.
  • the elevators 26 provided on the transfer cylinder 22 are shown schematically in FIG.
  • the designed as a blanket lift 26 is designed as a so-called.
  • a backing plate 27 for a rubber blanket consists i. d. R. from a flexible, but otherwise dimensionally stable material, e.g. made of metal, z. B of an aluminum alloy, but in particular stainless steel, and has two opposite, to be fastened in or on the cylinder 22 ends 29; 30, these ends 29; 30 bent for training as suspension legs.
  • the leading end 29 is bent for example by 45 ° and the trailing end 30 by 90 °.
  • the folded ends 29; 30 of the elevators 26 are each inserted on the circumference of the cylinder 22 in the paraxial grooves 31 formed there, wherein the ends 29; 30 be held for example by their shape, friction or deformation. However, they can also be fixed by means of spring force, by pressure medium or an effective during operation centrifugal force operable means.
  • the grooves 25 for juxtaposed in the axial direction printing plates on the forme cylinder 21 are each arranged in alignment as a continuous groove, while the grooves 31 are not continuous for the arranged on the transfer cylinder 22 elevators 26, but alternately offset by 180 °.
  • FIGS. 2 to 8 show various embodiments of the transfer cylinder 22 with a lift 26 arranged thereon in a highly schematic representation, wherein the differences provided in the diameter of the lateral surface are realized in different ways.
  • outer surface of the cylinder is understood here the outside of the bale with a lift.
  • the diameter of the lateral surface of the cylinder 22 in the center of the cylinder 22 is greater than at the two ends. Furthermore, in all embodiments, the crowning of the cylinder 22 along the cylinder axis is preferably carried out symmetrically to the cylinder center.
  • the different diameter can be realized, on the one hand, that the bale of the transfer cylinder 22, seen in the axial direction, has the corresponding different shape and the elevator or the lifts have the same thickness, cf. z. 4, 5, 6 and 7.
  • An outer surface of the bale of the transfer cylinder or counter-pressure cylinder is arranged in the circumferential direction to an axis of rotation of the transfer cylinder 22 or impression cylinder 23 to a possibly present channel equidistant.
  • a profiling of a lateral surface of the transfer cylinder 22 or counter-pressure cylinder 23 is arranged rotationally symmetrical in the circumferential direction to a rotational axis of the transfer cylinder 22 or impression cylinder 23 except for an optionally present channel.
  • bale of the transfer cylinder 22 in axial direction in the region of the elevator or elevators same diameter and the elevator or elevators have different diameters, see. z. 2 and 3.
  • a third possibility is that both the bale of the transfer cylinder 22 and the elevator or the elevators in the axial direction have the same diameter or thickness and between bales of the transfer cylinder 22 and the elevator or the Elevators an underlay or intermediate layer is arranged, which generates the desired diameter differences in the axial direction (Fig. 8).
  • Fig. 2 shows an embodiment in which the bale of the transfer cylinder 22 in the axial direction has a constant diameter and the (single) elevator 32 has a convex lateral surface.
  • Fig. 3 shows an embodiment in which the bale of the transfer cylinder 22 in the axial direction also has constant diameter and three elevators 33, 34 and 35 are arranged side by side in the axial direction, the central elevator 34 has a larger diameter than the two arranged laterally Elevators 33 and 35, each with the same diameter.
  • the lateral surface of the transfer cylinder 22 is thus formed like a step or has two paragraphs.
  • Fig. 4 shows an embodiment in which the lateral surface of the bale of the transfer cylinder 22 seen in the axial direction is convex and the (single) elevator 36 in the axial direction has constant material thickness.
  • FIG. 5 shows an exemplary embodiment with three elevators 37, 38 and 39, each of equal thickness, lying next to one another in the axial direction.
  • the bale of the transfer cylinder 22 has the axial length of the elevators 37, 38, 39 respectively corresponding to a middle and two lateral cylindrical portions, wherein the diameter of the central portion is greater than the diameter of the two lateral sections.
  • the lateral surface of the transfer cylinder 22 is thus formed like a step or has two paragraphs.
  • Fig. 6 shows an embodiment in which the lateral surface of the bale of the transfer cylinder 22 seen in the axial direction has two rising towards the center straight sections, wherein the (single) elevator 40 seen in the axial direction has constant thickness; the straight sections are thus arranged in a triangular shape.
  • Fig. 7 shows an embodiment in which the lateral surface of the bale of the transfer cylinder 22 seen in the axial direction has three straight sections, namely a section with a positive slope, a central portion which is axis-parallel, and another portion with a negative slope.
  • three elevators 41, 42 and 43 are provided which, when viewed in the axial direction, each have the same thickness.
  • Fig. 8 shows an embodiment in which the lateral surface of the bale of the transfer cylinder 22 seen in the axial direction has the same diameter, that is cylindrical, and the (single) elevator 44 seen in the axial direction has the same strength.
  • the desired different diameter of the lateral surface of the transfer cylinder 22 is achieved here by the fact that between ball and elevator 44, a pad 45 is arranged, the lateral surface seen in the axial direction is convex.
  • This pad 45 has a calibrated thickness and may be formed as a self-adhesive film. In an alternative, not shown, two or more documents 45 may be provided, if necessary, different thickness.
  • the different diameter of the lateral surface of the transfer cylinder 22 is achieved by different thickness of the elevator or the lifts, such. B. in the case of Fig. 2, this is preferably realized in that the carrier plate 27 (FIG. 9) of the respective elevator receives the corresponding shape, that is to say it is especially convex in axial direction.
  • the carrier plate 27 FIG. 9
  • the differences in diameter of the lateral surface of the cylinder 22 and the differences in thickness of the lifts or documents are determined depending on the geometric properties of the transfer cylinder 22.
  • the diameters and thicknesses differ by at least 0.01 mm, preferably by at least 0.02 mm, possibly by at least 0.05 mm, but by less than 0.5 mm, preferably by less than 0.2 mm, if necessary by less than 0.1 mm.
  • the difference between the minimum and maximum diameters in the printing area is between 0.02 and 0.7 mm.
  • the transfer cylinder 22 seen in the axial direction has a curvature, such.
  • the surface profile of the forme cylinder 21 along the cylinder axis in the printing area can deviate parabolic or with a constant radius of curvature of the cylindrical ideal shape.
  • the transfer cylinder 22 As far as in the embodiments described above, only the transfer cylinder 22 reference is made, it should be noted that if necessary, the lateral surface of the impression cylinder 23 may have different diameters in the axial direction. In this case, the structures described in connection with the transfer cylinder 22 should be implemented accordingly, as far as applicable. The same applies to the forme cylinder 21, the i. d. R., however, will be crowned concave.
  • the present invention is particularly applicable to relates to such a printing unit having at least two pairs of two cylinders each, namely a transfer cylinder and an associated form cylinder, wherein the transfer and forme cylinders are designed with a width for the printing of six axially juxtaposed newspaper pages, and the transfer cylinder in one Pressure on position with a cylinder designed as a satellite cylinder pressure forming a pressure point cooperate.
  • a cylinder satellite unit which enables a simple, cost-effective and space-saving design with simultaneously high variability in the product or intermediate product, is disclosed in WO 03/031180 A2, to which reference is expressly made with regard to the details.
  • the printing unit is designed in particular as a nine-cylinder satellite printing unit, which has a high precision in the color register and on the other a low-vibration construction result.
  • the printing unit has in this case four star-shaped printing units with a common inner, designed as a satellite cylinder printing cylinder and in each case a subsequent transfer cylinder and in each case a voltage applied to the transfer cylinder form cylinder.
  • ink is applied from an inking unit to a web via a forme cylinder.
  • the printing unit which can be designed as offset printing unit for the wet offset, in addition to the inking unit on a dampening unit and the transfer cylinder.
  • the transfer cylinder forms a pressure point with the pressure cylinder forming an abutment.
  • Fig. 10 illustrates a six-plate wide printing unit 20 of an offset printing machine with a two-thirds width web 46 as an exemplary embodiment.
  • This three-cylinder pressure unit 20 may be arranged in particular in a nine-cylinder satellite pressure unit.
  • the forme cylinder 21 has in the axial direction of the forme cylinder 21 six (not shown) printing plates and thus has a length corresponding to six pages standing or lying newspaper pages.
  • the transfer cylinder 22 has a tempering or cooling device (not shown in more detail), which enables targeted temperature control or cooling of certain sections of the transfer cylinder 22.
  • the transfer cylinder 22 in three zones 47; 48; 49, wherein seen in the axial direction of the transfer cylinder 22, the positions and widths of these zones 47; 48; 49 those of the elevators 26a; 26b; 26c correspond.
  • Each tempered or temperature-controlled zone 47; 48; 49 thus corresponds to the width of the corresponding elevator 26a; 26b; 26c.
  • each zone 47 takes place; 48; 49 from the inside, by within the transfer cylinder 22 in the region of each zone 47; 48; 49 and from the adjacent zone 47; 48; 49 each separated or separable as the temperature control a suitable liquid is arranged.
  • Each zone 47; 48; 49 is basically independent of the other zone 47; 48; 49 tempered, where quite two zones 47; 48; 49 can be tempered together, ie in particular the zones 47; 48 in the region of the web 46 with one temperature and the zone 49 at a different temperature.
  • the temperature can be controlled by applying the respective zone or zones 47; 48; 49 are controlled with temperature control of different temperature and / or amount.
  • a common line is provided which supplies temperature control means from outside the cylinder 22.
  • a valve arrangement is provided, the temperature control either the respective zone 47; 48; 49 and the respective zones 47; 48; 49 feeds.
  • Such a valve device can be arranged inside or outside the cylinder 22.
  • a first and a second line is provided, which separated from outside of the transfer cylinder 22 tempering the respective zone 47; 48; 49 and the respective zones 47; 48; 49 feeds.
  • cooling can also take place via the existing spray dampening unit (see description of FIG. 1), in which case also the non-printing areas (in the region of the non-existing printing material) of the forme cylinder 21 provided with so-called dummy plates be applied with dampening solution, but not with color.
  • zones 47; 48; 49 are temperature controlled, but one or two zones 47; 48; 49 remain without targeted tempering.
  • the temperature control can also be designed such that within at least one tempered zone in the axial direction of the cylinder different amount of heat or by means of the dampening unit different amount of fountain solution is transferable.
  • the possibility of temperature control to the particular circumstances is adaptable and it is therefore provided that, in accordance with the occupancy of the printing unit and / or the substrate width, the temperature of the cylinder set and / or selectable.
  • a work machine, z. B. a printing machine such as the printing unit shown in Figure 1, has rolling rollers 22 rolling against each other; 23, which in the region of their touch a nip 19, z. B. a nip 19, form.
  • This can be in the case of the printing press rollers 21; 22 an inking unit, a coating unit, or cylinder 21; 22 be a printing unit.
  • the cylinder 21; 22 is a forme cylinder 21 having an effective diameter D wPZ and a transfer cylinder 22 of an offset printing unit.
  • a total thickness T of the elevator 26 is z. B. from the thickness t of the layer 28 and a thickness of an optionally associated with the layer 28 is substantially incompressible, inelastic support layer 27, in particular a support plate 27, for example, a metal plate 27, (shown by way of example in Fig. 18) together. If the elevator 26 has no additional carrier layer 27, then the thickness t corresponds to the total thickness T.
  • the layer 28 can be constructed as a heterogeneous layer 28 of multiple layers, which in total have the required property for the layer 28.
  • Core and elevator 26 or coating 26 together form an effective diameter D wGZ of the transfer cylinder 22.
  • the effective diameter D wPZ is determined by the effective for rolling lateral surface of the forme cylinder 21 and optionally includes an applied on the outer surface of a base body elevator, z , B. a printing form.
  • the hard surface cylinder 21 may also be designed as an impression cylinder 21 cooperating with the transfer cylinder 22.
  • the embodiment of the layer 26 set forth below is not dependent on the design of the rollers 21; 22 as a transfer and forme cylinder 21; 22 or bound to the execution with a printing forme.
  • a profile for a surface pressure P in Nipp 19 of the two rollers 21 and 22 is shown schematically.
  • the surface pressure P extends over the entire area of the contact zone, wherein it reaches a maximum surface pressure P max at standstill at the level of a connecting plane V of the axes of rotation. This shifts in production to the incoming gap side due to the viscous force component.
  • the contact zone and thus the profile has a width B.
  • the maximum surface pressure P max is ultimately responsible for the color transfer and adjust accordingly.
  • FIG. 12 schematically shows the profile of the surface pressure P in the case of a larger indentation S, which at the same time causes a broadening of the width B. If, however, the maximum surface pressure P max are nevertheless to be achieved, the integration of the surface pressure P over the entire width B leads to an increase in a force between the two rollers 21; 22nd
  • the absolute height of the surface pressure P in the nip 19 and its variation in the variation of the indentation S is largely determined by a spring characteristic of the layer 28 or the elevator 26 used with the layer 28.
  • the spring characteristic represents the surface pressure P as a function of the indentation S.
  • FIG. 13 shows, by way of example, some spring characteristics of conventional elevators 26, in particular blankets 26 with a corresponding layer 28. The values are determined on a quasi-static stamp test bench in the laboratory. They are to be transferred in a suitable way to otherwise determined values.
  • a slope ⁇ P / ⁇ S of the spring characteristic determines the fluctuation in the surface pressure P when the depression S (for example, vibration) changes.
  • the magnitude of a fluctuation ⁇ P of the required maximum surface pressure P max in the nip 19 about the average surface pressure P is approximately proportional to the slope ⁇ P / ⁇ S of the spring characteristics at the point S.
  • FIG an elevator a (FIG.
  • An elevator b has a lower pitch.
  • Lifts 26, which either as a whole or its layer 28 as such a large Slope .DELTA.P / .DELTA.S, in particular in the range of the required maximum surface pressure P max in the pressure-relevant area, are referred to hereinafter as "hard", those with a small pitch .DELTA.P / .DELTA.S as "soft".
  • the elevator 26 or the layer 28 is now executed as a "soft" elevator 26 or "soft” layer 28.
  • a "hard” elevator 26 or a hard layer 28 performs a same relative movements of the rollers 21; 22 (or change of the distance A) thus in a soft elevator 26 to a smaller change in the surface pressure P and thus to a reduction in the fluctuations in the color transfer.
  • the soft elevator 26 thus causes a lower sensitivity of the printing process to vibrations and / or deviations at intervals from a desired value. Due to smaller changes in the surface pressure P due to relative movements of the rollers 21; 22 are z.
  • the surface pressure varies in pressure-on position in an advantageous embodiment highest in a range between 60 and 220 N / cm 2 .
  • fluids e.g. As printing inks, with very different rheological properties, different areas within the above-mentioned area for the surface pressure may be preferred.
  • B. between 100 and 220 N / cm 2 , in particular 120 to 180 N / cm 2 varies, especially in these areas, the slope should meet the condition of the slope.
  • the pressure-relevant area for the maximum surface pressure P max is advantageously between 60 to 220 N / cm 2 .
  • different areas within the above-mentioned area for the surface pressure may be preferred. So varies the area for the Wet offset z. B. between 60 and 120 N / cm 2 , in particular from 80 to 100 N / cm 2 (shaded in Fig. 13 shown), while in the case of dry offset z. B. between 100 and 220 N / cm 2 , in particular from 120 to 180 N / cm 2 varies.
  • a soft elevator 26 at least in the range of 80 to 100 N / cm 2, a slope .DELTA.P / .DELTA.S of z. B. ⁇ P / ⁇ S ⁇ 700 (N / cm 2 ) / mm, especially ⁇ P / ⁇ S ⁇ 500 (N / cm 2 ) / mm, in particular less than 400 (N / cm 2 ) / mm.
  • the slope .DELTA.P / .DELTA.S should be smaller by a factor of at least two in the relevant area for the surface pressure P than is currently the case for elevators 26 in offset printing.
  • the layer 28 has a greater thickness t or the elevator 26 has a greater total thickness T than hitherto customary.
  • the thickness t of the layer 28 which is functional in terms of elasticity or compressibility amounts, for example, to 1.3 to 6.3 mm, in particular 1.7 to 5.0 mm, in particular more than 1.9 mm.
  • support layers eg, woven fabrics
  • the carrier layer 27 or support layers which are functionally not functional for the "softness" of the elevator 26 but rather for the dimensional stability, may also be arranged between the "soft" layers 26. It can, for example, be designed as a metal, in particular stainless steel sheet, about 0.1 to 0.3 mm thick. As a fabric, this may be from 0.1 to 0.6 mm, depending on the design of the elevator 26.
  • the stated thickness t of the layer 28 in the case of multiple layers of layers 28 refers to the sum of the "partial layers” functionally responsible for the above-described characteristic (dependence on surface pressure / indentation) and the elasticity or compressibility.
  • An elevator 26 then has, for example together with carrier layer (s) 27, the total thickness T of 2.0 to 6.5 mm, in particular 2.3 to 5.9 mm up.
  • the elastic layer 28 or its thickness t is understood as meaning the layer 28 or the sum of the layers 28 whose material has a modulus of elasticity in the radial direction of less than 50 N / mm 2 .
  • the layers possibly provided for support (fabric) or dimensional stability (support) have significantly greater modulus of elasticity, e.g. B. greater than 70 N / mm 2 , in particular greater than 100 N / mm 2 or even greater 300 N / mm 2 .
  • At least one partial layer of the layer 28, referred to here as an elastic layer, is made of porous material in an advantageous embodiment.
  • the elastic layer 28 may also include a covering layer 18 indicated by dashed lines in FIG. 18, the elastic modulus of which in the radial direction is less than 50 N / mm 2 .
  • a cover layer 18 is generally used to form a closed surface and contributes in this case to the formation of "softness". In other cases, cover layers 18 larger elastic modulus, z. B. greater than 70 N / mm 2 , in particular greater than 100 N / mm 2 or even greater than 300 N / mm 2 used, and then for this reason not the elastic and / or compressible layer 28 attributed.
  • the "soft" elevator 26 (or layer 28) is preferably operated with a higher indentation S in comparison to conventional indentations S (shown schematically in FIG. 12 in comparison to FIG. 11), ie the two rollers 21; 22 are related to their respective effective but undisturbed diameter D wGZ , D wPZ further hired.
  • an optimal maximum surface pressure P max is achieved despite a smaller pitch .DELTA.P / .DELTA.S.
  • a relative indentation S * ie related to the thickness t of the layer 28 Indentation S, lies z. B. without regard to the specific embodiment of the rollers 21; 22 z. B. between 10% and 35%, but especially between 13% and 30%.
  • a width B of the contact zone resulting from indentation S of the layer 28 in a projection perpendicular to a connecting plane V of its axes of rotation is advantageously at least 5% of the undisturbed effective diameter D wGZ of the roller 22 with layer 28.
  • the design and / or arrangement of the "soft" elevator 26 is particularly advantageous when one of the two cooperating rollers 21; 22 (or both) at least one interference affecting the unwinding 25; 31 has on its effective lateral surface.
  • This disorder 25; 31 can as interruption 25; 31, an axially extending butt 25; 31 of two ends 29; 30 of one or more elevators 26 be.
  • the disorder 25; 31 but by one or more axially extending channel 25; 31 for attachment of ends 29; 30 of one or more elevators 26 caused.
  • This channel 25; 31 has an opening towards the lateral surface, through which the ends 29; 30 are guided.
  • a device for clamping and / or tensioning of the elevator 26 and the elevators 26 have.
  • width B25; B31 of the channel 25; 31 smaller than the width B of the contact zone.
  • at least always based areas of co-operating lateral surfaces in the contact zone from each other it also results in a reduction in the height and a flatter course (broadening of the pulse) for the force of the impact excitation.
  • Softer lifts 26 or softer layers 28 result in narrow channels 25; 31 thus to a weakening and a temporal extension of the channel impact.
  • ends of a metal blanket may be disposed in the channel 31.
  • the layer 28 is in this case on a dimensionally stable support 27, for.
  • a thin metal plate (a plate), applied, the folded ends are arranged in the channel 31.
  • the channel 31 can then extremely narrow in the circumferential direction, z. B. less than or equal to 5 mm, in particular less than or equal to 3 mm.
  • the channel 25 in an advantageous embodiment with a width in the circumferential direction is less than or equal to 5 mm, in particular less than or equal to 3 mm executed.
  • the permissible ratio B25: B or B31: B is reduced.
  • a version in which the width B25; B31 of the channel 25; 31 in the region of its opening or mouth to the lateral surface of the core or main body in the circumferential direction at most in the ratio 1: 3 to the resultant by the pressing width B of the contact zone (impression strip) is.
  • the soft layer 28 preferably has a reduced damping constant compared to commonly used materials, so that no higher flexing heat is generated despite the higher loading and unloading speeds due to the higher indentation S when unrolling.
  • the must Layer 28 be designed such that a sufficiently fast recovery or springing takes place after passing through the nip 19 in the starting position, so that, for example, when in contact with a paint roller or another cylinder already present the output strength.
  • FIGS. 14 and 15 show a printing unit 20 configured in an advantageous manner with the layer 28, designed as a so-called double printing unit 20.
  • the forme cylinder 21 associated transfer cylinder 02 of a first cylinder pair 21; 22 acts via a printing material 24; 46, z. B. a web 24; 46 with a likewise designed as a transfer cylinder 22 impression cylinder 22 together, which is also associated with a forme cylinder 21.
  • All four cylinders 21; 22 are mechanically driven independently of one another by means of different drive motors 17 (FIG. 14).
  • forming and transfer cylinders 21; 22 in pairs coupled by a paired drive motor 17 (on the forme cylinder 21 on the transfer cylinder 22 or parallel) driven (FIG. 15).
  • the forme cylinder 21 and the transfer cylinder 22 are in a first embodiment as a cylinder 21; 22 double circumference, ie with a circumference of substantially two stationary printed pages, in particular of two newspaper pages executed. They are with effective diameters D wGZ ; D wPZ made between 260 to 400 mm, in particular 280 to 350 mm.
  • the transfer cylinder 22 On the lateral surface of the core, the transfer cylinder 22 in each case has at least one elevator 26 with a total thickness T of 2.0 to 6.5 mm, in particular of 2.3 to 5.9 mm.
  • the slope .DELTA.P / .DELTA.S of the spring characteristic is at least in the pressure-relevant area (see above) below 700 (N / cm 2 ) / mm, in particular below 500 (N / cm 2 ) / mm.
  • Forming and transfer cylinder 21; 22 are set in pairs in such a way that the width B of the contact zone between the forming and transfer cylinders 21; 22 in Anstelllage 10 to 25 mm, in particular 12 to 21 mm. This configuration largely minimizes sensitivity to vibration and inaccuracy.
  • the individual drives by the drive motors 17 support this by the mechanical decoupling.
  • the forme cylinder 21 and the transfer cylinder 22 as a cylinder 21; 22 simple circumference, ie with a circumference of substantially a standing pressure side, especially from a newspaper page executed. They are with effective diameters D wGZ ; D wPZ running between 150 to 190 mm.
  • the transfer cylinder 22 On the lateral surface of the core, the transfer cylinder 22 in each case has at least one elevator 26 with a total thickness T of 2.0 to 6.5 mm, in particular of 2.3 to 5.9 mm.
  • the slope ⁇ P / ⁇ S of the spring characteristic is again below 700 (N / cm 2 ) / mm, in particular below 500 (N / cm 2 ) / mm, at least in the pressure-relevant area (see above).
  • Forming and transfer cylinder 21; 22 are set in pairs in such a way that the width B of the contact zone between the forming and transfer cylinders 21; 22 in Anstelllage 7 to 18 mm, in particular 9 to 15 mm.
  • the transfer cylinder 22 On the lateral surface of the core, the transfer cylinder 22 has at least one elevator 26 of total thickness T from 2.0 to 6.5 mm, in particular from 2.3 to 5.9 mm.
  • the slope ⁇ P / ⁇ S of the spring characteristic is again below 700 (N / cm 2 ) / mm, in particular below 500 (N / cm 2 ) / mm, at least in the pressure-relevant area (see above).
  • Forming and transfer cylinder 21; 22 are set in pairs in such a way that the width B of the contact zone between the forming and transfer cylinders 21; 22 in Anstelllage 8 to 20 mm, in particular 9 to 17 mm.
  • a printing unit 20 is shown, which is either part of a larger printing unit, such.
  • B. a five-cylinder, nine-cylinder or ten-cylinder printing unit, is, or is operable as a three-cylinder printing unit 20.
  • the transfer cylinder 22 acts here with a cylinder leading to no ink 23, z. B. a counter-pressure cylinder 23, in particular a satellite cylinder 23, together.
  • the "soft" lateral surface of the transfer cylinder 22 now interacts with the "hard” lateral surface of the forme cylinder 21 on one side, and with the "hard” lateral surface of the satellite cylinder 23 on the other side.
  • the one or more satellite cylinders 23 have their own drive motor 17, while the pair of forming and transfer cylinders 21; 22 mechanically coupled by a common drive motor 17 (FIG. 16), or are driven mechanically independent of each other by a separate drive motor 17 (FIG. 17).
  • Form cylinder 21, transfer cylinder 22 and satellite cylinder 23 are in a first embodiment for Fig. 16 or 17 as a cylinder 21; 22; 23 double circumference with effective diameters D wGZ ; D wPZ ; D wSZ made between 260 to 400 mm, especially 280 to 350 mm.
  • the transfer cylinder 22 On the lateral surface of the core, the transfer cylinder 22 in each case has at least one elevator 26 with a total thickness T of 2.0 to 6.5 mm, in particular of 2.3 to 5.9 mm.
  • the slope .DELTA.P / .DELTA.S of the spring characteristic is at least in the pressure-relevant area (see above) below 700 (N / cm 2 ) / mm, in particular below 500 (N / cm 2 ) / mm.
  • Forming and transfer cylinder 21; 22 and transfer cylinder 22 and satellite cylinder 23 are each paired in such a manner employed that the width B of the contact zone in Anstelllage each 10 to 25 mm, in particular 12 to 21 mm.
  • forme cylinder 21, transfer cylinder 22 and satellite cylinder 23 are cylinders 21; 22; 23 simple circumference, ie with a circumference of substantially a standing pressure side, in particular from a newspaper page executed. They are with effective diameters D wGZ ; D wPZ ; D wSZ performed between 120 to 180 mm, in particular 130 to 170 mm.
  • the transfer cylinder 22 in each case has at least one elevator 26 of a total thickness T of 2.0 to 6.5 mm, in particular of 2.3 to 5.9 mm.
  • the slope ⁇ P / ⁇ S of the spring characteristic is again below 700 (N / cm 2 ) / mm, in particular below 500 (N / cm 2 ) / mm, at least in the pressure-relevant area (see above).
  • Forming and transfer cylinder 21; 22 and transfer cylinder 22 and satellite cylinder 23 are each paired in such a manner employed that the width B of the contact zone in Anstelllage each 7 to 18 mm, in particular 9 to 15 mm.
  • the aforementioned elevator 26 or the layer 28 is z. B. in a printing unit with one or more long but slim cylinders 21; 22 arranged.
  • the forme cylinder 21 and the transfer cylinder 22 z. B. in the region of their bales each have a length which four or more widths of a printed page, z. B. a newspaper page, z. B. 1100 to 1,800 mm, in particular 1,500 to 1,700 mm corresponds.
  • the diameter D wGz ; D wPZ at least of the forme cylinder 01; 16 is z. B. 150 to 190 mm, in particular 145 to 185 mm, which corresponds in scope substantially a length of a newspaper page ("single circumference").
  • the device is advantageous in which the ratio between the diameter and length of the cylinder 21, 22; 23 is less than or equal to 0.16, in particular less than 0.12 or even less than or equal to 0.08.
  • the diameter of at least the forme cylinder 21 is z. B. at 260 to 340 mm, in particular 280 to 300 mm, which corresponds in scope substantially two lengths of a newspaper page ("double circumference").
  • a ratio of the diameter D wGZ ; D wPZ at least of the forme cylinder 21 to its length is here at 0.11 to 0.17, in particular at 0.13 to 0.16.
EP05108319A 2004-09-16 2005-09-12 Groupe d'impression offset comprenant un cylindre de transfert avec un recouvrement élastique Withdrawn EP1637326A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102004045285 2004-09-16
DE102004045607 2004-09-17
DE102004056389A DE102004056389B4 (de) 2004-09-16 2004-11-23 Druckwerk einer Offsetdruckmaschine mit mindestens einem Formzylinder und einem Übertragungszylinder
DE102004056388A DE102004056388B3 (de) 2004-09-17 2004-11-23 Druckwerk einer Offsetdruckmaschine mit mindestens einem Formzylinder, einem Übertragungszylinder und einem Gegendruckzylinder

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EP1637326A2 true EP1637326A2 (fr) 2006-03-22

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Family Applications (2)

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EP05108318A Withdrawn EP1637327A3 (fr) 2004-09-16 2005-09-12 Groupe d'impression offset comportant au moins un cylindre conditionné thermiquement
EP05108319A Withdrawn EP1637326A2 (fr) 2004-09-16 2005-09-12 Groupe d'impression offset comprenant un cylindre de transfert avec un recouvrement élastique

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EP05108318A Withdrawn EP1637327A3 (fr) 2004-09-16 2005-09-12 Groupe d'impression offset comportant au moins un cylindre conditionné thermiquement

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1908589A2 (fr) 2006-09-29 2008-04-09 MAN Roland Druckmaschinen AG Unité d'impression d'une machine d'impression
DE102007047781A1 (de) * 2007-05-08 2008-11-13 Manroland Ag Rollendruckmaschine

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3242066A1 (de) * 1982-11-13 1984-05-17 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Kuehlwalze mit vorgewaehlten unterschiedlichen kuehlzonen
ATE254536T1 (de) * 1999-10-08 2003-12-15 Koenig & Bauer Ag Zylinder einer rotationsdruckmaschine
DE19957943B4 (de) * 1999-12-02 2006-07-13 Koenig & Bauer Ag Druckformzylinder
DE10250686A1 (de) * 2002-10-31 2004-05-19 Koenig & Bauer Ag Verfahren zum Temperieren eines Ballens eines Rotationskörpers einer Druckmaschine und Rotationskörper einer Druckmaschine mit einem Ballen
DE10250684B3 (de) * 2002-10-31 2004-04-01 Koenig & Bauer Ag Verfahren zur Herstellung eines Rotationskörpers und Rotationskörper einer Druckmaschine

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP1908589A2 (fr) 2006-09-29 2008-04-09 MAN Roland Druckmaschinen AG Unité d'impression d'une machine d'impression
EP1908589A3 (fr) * 2006-09-29 2009-07-29 manroland AG Unité d'impression d'une machine d'impression
DE102007047781A1 (de) * 2007-05-08 2008-11-13 Manroland Ag Rollendruckmaschine

Also Published As

Publication number Publication date
EP1637327A2 (fr) 2006-03-22
EP1637327A3 (fr) 2011-07-20

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