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
• • 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
  • B41F13/10—Forme cylinders
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F13/00—Common details of rotary presses or machines
  • B41F13/004—Electric or hydraulic features of drives
  • B41F13/0045—Electric driving devices
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F13/00—Common details of rotary presses or machines
  • B41F13/008—Mechanical features of drives, e.g. gears, clutches
• • 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
  • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
  • B41F13/26—Arrangement of cylinder bearings
  • B41F13/28—Bearings mounted eccentrically of the cylinder axis
• • 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
  • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
  • B41F13/26—Arrangement of cylinder bearings
  • B41F13/30—Bearings mounted on sliding supports
• • 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
  • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
  • B41F13/26—Arrangement of cylinder bearings
  • B41F13/32—Bearings mounted on swinging supports
• • 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
  • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
  • B41F13/34—Cylinder lifting or adjusting devices
  • B41F13/36—Cams, eccentrics, wedges, or the like
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F27/00—Devices for attaching printing elements or formes to supports
  • B41F27/10—Devices for attaching printing elements or formes to supports for attaching non-deformable curved printing formes to forme cylinders
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F27/00—Devices for attaching printing elements or formes to supports
  • B41F27/12—Devices for attaching printing elements or formes to supports for attaching flexible printing formes
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41F—PRINTING MACHINES OR PRESSES
  • B41F7/00—Rotary lithographic machines
  • B41F7/02—Rotary lithographic machines for offset printing
  • B41F7/12—Rotary lithographic machines for offset printing using two cylinders one of which serves two functions, e.g. as a transfer and impression cylinder in perfecting machines
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
  • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
  • B41P2213/10—Constitutive elements of driving devices
  • B41P2213/20—Gearings
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
  • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
  • B41P2213/10—Constitutive elements of driving devices
  • B41P2213/20—Gearings
  • B41P2213/206—Planetary gears
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
  • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
  • B41P2213/70—Driving devices associated with particular installations or situations
  • B41P2213/73—Driving devices for multicolour presses
  • B41P2213/734—Driving devices for multicolour presses each printing unit being driven by its own electric motor, i.e. electric shaft
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
  • B41P2227/00—Mounting or handling printing plates; Forming printing surfaces in situ
  • B41P2227/10—Attaching several printing plates on one cylinder
• • B—PERFORMING OPERATIONS; TRANSPORTING
  • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
  • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
  • B41P2227/00—Mounting or handling printing plates; Forming printing surfaces in situ
  • B41P2227/10—Attaching several printing plates on one cylinder
  • B41P2227/11—Attaching several printing plates on one cylinder in axial direction

Definitions

• Printing unit of a printing press method for turning a cylinder on and off, and method for producing a printed product
• the invention relates to a printing unit of a printing press, a method for turning a cylinder on and off, and a method for producing a printed product according to the preamble of claims 1, 5, 16, 27, 29, 31 and 32.
• a printing unit is known from DE 198 03 809 A1, the forme cylinder of which has one circumferential circumference and a plurality of printing plates in the longitudinal direction.
• a transfer cylinder cooperating with the forme cylinder has a double circumference and is designed in the circumferential direction with a printing blanket and in the longitudinal direction with two printing blankets which are arranged offset to one another in the circumferential direction.
• JP 100 71 694 discloses printing group cylinders with four channels arranged next to one another and offset in the circumferential direction from one another.
• the printing unit cylinders have a so-called double circumference.
• CH 3 45 906 discloses a device for bumpless printing, wherein bumps from four lifts arranged next to one another on transfer cylinders of double circumference and bumps from four lifts arranged next to one another on a forme cylinder of double circumference are offset from one another.
• a double printing unit is known from DE 198 15 294 A1, the axes of rotation of the printing unit cylinders being arranged in one plane.
• the cylinders have four times the width of a newspaper page (double width) and a circumference of one height of a newspaper page.
• the transfer cylinders have endless sleeves, which are on the side are interchangeable through openings in the side wall.
• a double printing unit is known from DE 44 15 711 A1, in order to improve the print quality, a plane perpendicular to the paper web is inclined by approximately 0 ° to 10 ° to the plane connecting the two axes of rotation of the transfer cylinders.
• JP 57-131 561 discloses a double printing unit with axes of the printing unit cylinders arranged in one plane.
• the printing unit cylinders are arranged in phase to one another in such a way that channels for fastening the lifts to one another and in the two printing units acting together roll simultaneously.
• DE 34 12 812 C1 also discloses a double printing unit, the cylinder axes being arranged in a common plane which is inclined to the plane of the web to be printed.
• the transfer cylinders are turned on and off along an almost rectilinear direction of movement by means of double eccentrics.
• EP 08 62 999 A2 discloses a double printing unit with two transfer cylinders acting together, which are mounted in eccentric or double eccentric bushings for the purpose of attaching and detaching. In another version, they are mounted in levers which are pivotally mounted eccentrically to the forme cylinder axis. From EP 10 75 945 A1, a double printing unit with axes of the printing unit cylinders arranged in one plane is known, several printing unit cylinders being mounted in slides, and for the purpose of turning on and off by means of guide elements arranged on a supporting wall, the distance between them being variable.
• Printing unit cylinders are known from DE 199 37 796 A1, which can be moved along a linear adjustment path in order to place them on or against one another.
• a drive motor is assigned to each cylinder and is moved together with the cylinder. The movement takes place in a direction which is parallel to a common plane of the printing couple cylinders.
• the invention has for its object to provide a compact, low-vibration printing unit of a printing press, which is easy to manufacture and a method for turning on and off a cylinder and a method for producing a printed product.
• the advantages that can be achieved with the invention consist in particular in that the measures create a printing press that is compact, low-vibration and robust, has a high production diversity, and requires a relatively low production and maintenance effort.
• the cylinders support each other. This reduces relative cylinder deflection. It is even possible to compensate the bending line (static) of the forme cylinder and the transfer cylinder with respect to one another.
• the elevators on the cylinders are not held in channels that are continuous over the length of the cylinders, but in channels that are offset in the circumferential direction, channel blow during passage of the channel during the rolling of two interacting cylinders is considerably reduced.
• the channels are arranged offset by 180 ° to one another in the case of two channels arranged side by side in the longitudinal direction.
• the arrangement of the printing unit cylinders and the channels is particularly advantageous in such a way that the channels of each cylinder offset from one another roll in the region of the opposite, offset channel of the cooperating cylinder. This allows the dynamic forces to be balanced. With a fixed offset angle of 180 ° and a linear arrangement of the cylinders for all production rates, i. H. Angular velocities, destructive interference, without having to vary an offset angle of the channels depending on the speed or frequency.
• the arrangement of printing unit cylinders of a simple scope is particularly advantageous for printed products of smaller and / or variable page size and / or for printing shops with limited space. Compared to producing the same product on a double-size press (without collecting), no "double" plate change is required. In contrast to a double-size press in the collecting company it is possible to create a page jump from two sides, and thereby to create increased flexibility in the printed product.
• the transfer cylinders can be moved to turn the printing unit on and off.
• the forme cylinders can be mounted for the purpose of adjustment at a distance from the assigned transfer cylinder and, if necessary, the inking and, if present, dampening unit, the transfer cylinders can be turned on and off from one another and from the assigned forme cylinders advantageously only by moving the transfer cylinders.
• a linear movement of the cylinders is made possible by a movement specially selected in the area of the pressure point and at the same time avoiding devices and movements of the forme cylinders are avoided. This also contributes to the robust and simple design.
• the transfer cylinders are mounted, for example, in slides in linear guides in or on the side frame, which enables movement essentially perpendicular to the plane of the cylinder axes. If the guides are arranged on specially designed inserts on the side frame, then they are shortened Tenon and enable the simple formation of an encapsulated lubricant chamber. A special arrangement of the direction of movement enables the forme and impression cylinder and the web to be parked quickly and safely.
• the transfer cylinders are arranged for this purpose in levers which are pivotally mounted eccentrically to the forme cylinder axis. Due to the special position of the pivot points and the size of the eccentric (to the axis of rotation of the forme cylinder) in connection with the selected inclination to the plane of the cylinders forming the pressure point or between the web and the plane of the cylinders, the assigned cylinders or the web can be quickly switched off possible.
• the operational starting and stopping takes place only by means of the transfer cylinder, and in a preferred embodiment by means of only one actuating movement.
• the transfer cylinders are mounted in double eccentric bushings, which, at least in the area close to the pressure point, enables an almost linear movement largely perpendicular to the plane of the cylinder axes.
• the effective channel width is reduced by the lifts on the transfer cylinders, which are designed as so-called metal printing blankets, whereby the excitation of vibrations is advantageously further reduced and the non-printing area on the cylinders, i. H. the "white border" on the product or paper waste is reduced.
• cylinders or rollers must be used in printing units with the operating state "pressure on”, ie a pressure on position against and against each other.
• the necessary radial movement of the rollers also contains a movement component in the tangential direction, the size of which depends on the design (eccentric, lever, linear guide If the adjustment in relation to the operating state results in a speed difference on the effective lateral surfaces in the nip, this implies, due to the surface friction of the roller materials used, a tangential frictional force component which is opposite to the adjustment movement is thus inhibited or its speed is limited. This is particularly important in the case of printing unit cylinders in the case of so-called “winders”, since the high pressures that occur also result in large frictional forces.
• Figure 1 is a schematic representation of a double printing unit.
• FIG. 2 shows a schematic illustration of a three-cylinder offset printing unit
• Fig. 3 is a schematic representation of a double-wide double printing unit
• Fig. 4 is a schematic representation of a double-wide double printing unit, highly symmetrical
• FIG. 5 shows a schematic illustration of a double printing unit in section BB according to FIG. 1 with linear travel
• Fig. 6 is a schematic representation of a non-linear double printing unit with linear travel ranges
• Fig. 7 is a schematic representation of an H-pressure unit with linear travel
• FIG. 8 shows a side view of a first exemplary embodiment of a linear guide for transfer cylinders
• FIG. 9 shows a section through the linear guide according to FIG. 8
• FIG. 10 shows a side view of a second exemplary embodiment of a linear guide for transfer cylinders
• FIG. 11 shows a section through the linear guide according to FIG. 10;
• FIG. 12 shows a schematic illustration of a linear double printing unit in section BB according to FIG. 1 with a curved adjustment path;
• FIG. 13 shows a schematic illustration of an angular double printing unit in section BB according to FIG. 1 with a curved adjustment path
• FIG. Fig. 14 is a schematic representation of an H-printing unit with a curved adjustment path
• 15 is a side view for the storage of the cylinders
• FIG. 16 shows a section of the mounting according to FIG. 15;
• FIG. 18 shows a schematic front view according to FIG. 10
• 19 is a schematic front view of a double printing unit with cylinders of different circumference
• a first printing unit 01 of a printing press in particular a rotary printing press, has a first cylinder 02, e.g. B. a forme cylinder 02, and an associated second cylinder 03, z. B. a transfer cylinder 03, (Fig. 1).
• first cylinder 02 e.g. B. a forme cylinder 02
• second cylinder 03 e.g. B. a transfer cylinder 03
• Fig. 1 their axes of rotation define R02; R03 a level E.
• the forme cylinder 02 and the transfer cylinder 03 have at least one malfunction, z. B. an interruption 04; 06 in the lateral surface effective when unrolling.
• This interruption 04; 06 can be a joint of a leading and a trailing end of one or more elevators, which are arranged on the circumference, for example by means of magnetic force or cohesively.
• channels 04; 06 or slots 04; 06 act which pick up the ends of elevators.
• the channels 04; Faults designated 06 are synonymous with other interruptions 04; 06 on the effective lateral surface, ie the outward-facing surface of the cylinders 02; 03.
• the forme cylinder 02 and transfer cylinder 03 each have at least two channels 04; 06 (or interruptions 03; 04 etc.). These two channels 04; 06 are each in the longitudinal direction of the cylinder 02; 03 one behind the other, and staggered in the circumferential direction.
• Channels 04; 06 are so on the two cylinders 02; 03 arranged that when the two cylinders 02; 03 each on one of the channels 06; 04 of the other cylinder 03; 04 unroll.
• the offset of the channels is preferably 04; 06 each cylinder 02; 03 approx. 180 ° in the circumferential direction.
• the transfer cylinder 01 of the first printing unit 01 forms with a third cylinder 07; via a train 08; z. B. a printing material web 08, a printing point 09.
• This third cylinder 07 can be used as a second transfer cylinder 07 (FIG. 1) or as an impression cylinder 07 (FIG. 2), e.g. B. steel cylinders, or satellite cylinders 07.
• the axes of rotation R03 and R07 of the cylinder 03; 07 span a plane D in the ON position (see e.g. Fig. 6 or 13).
• the axes of rotation R02; R03; R07 of the three interacting cylinders 02; 03; 07 during a print-on position AN essentially in a common plane E, which in this case coincides with plane D, and run parallel to one another (see FIGS. 5, 12).
• a second printing unit not shown, is preferably also arranged in the common plane E. However, it can also define its own level E, which is also different from the level D assigned to it.
• the third cylinder 07 designed as a second transfer cylinder 07 interacts with a fourth cylinder 11, in particular a second forme cylinder 11 with an axis of rotation R11, and forms a second printing unit 12.
• the two printing units 01; 12 form a printing unit 13 printing on both sides simultaneously on the web 08, a so-called double printing unit 13.
• FIG. 5 shows a corresponding one Printing unit 13, wherein a pair of form and transfer cylinders 02, 03; 11, 07 a plane E, and the transfer cylinders 03; 07 which form level D different from levels E.
• the cylinders 07; 11 of the second printing unit 12 channels 04; 06 with the properties described above for the first printing group 01 with regard to the number and that of the offset to one another.
• Channels 04; 06 of the four cylinders 02; 03; 07; 11 are now preferably arranged so that two channels 04; 06 two interacting cylinders 02; 03; 07; 11 roll on top of each other.
• the forme cylinder 02 and the transfer cylinder 03 each have a length L02; L03, which are four or more widths of a printed page, e.g. B. a newspaper page, e.g. B. 1,100 to 1,800 mm, in particular 1,500 to 1,700 mm and a diameter D02; D03, e.g. B. 130 to 200 mm, in particular. 145 to 185 mm, the circumference U of which essentially corresponds to the length of a newspaper page, hereinafter referred to as "simple circumference" (FIGS. 3 and 4).
• the device is also advantageous for other dimensions in which the ratio between diameter D02; D03 and Length L02; L03 of the cylinder 02; 03 is less than or equal to 0.16, in particular less than 0.12, or even less than or equal to 0.08.
• each of the two cylinders 02; 03 two channels 04; 06 which each extend continuously at least over a length which corresponds to two widths of a newspaper page (FIG. 3).
• Each cylinder 02; 03 but also more than two channels 04; 06 may be arranged.
• two channels 04; 06 in alignment, or alternately.
• four channels 04; 06 the two the end faces of the cylinders 02; 03 adjacent channels 04; 06 in a common escape, and the two "inside" lying channels 04; 06 in a common flight, but offset in the circumferential direction from the former (FIG. 4).
• channels 04; 06 on the respective cylinder 02; 03; 07; 11 are offset from each other by 180 °.
• the elevator on the transfer cylinder 03; 07 is preferably designed as a so-called metal printing blanket, which has an ink-carrying coating on a metallic base plate.
• the bent ends are in the case of transfer cylinders 03; 07 for example by clamping and / or tensioning devices and in the case of forme cylinders 02; 11 by clamping devices in the channels 04; 06 held.
• each of the channels 06 of the transfer cylinder 03 a single, continuous clamping and / or tensioning device or - in the case of channels passing through several newspaper page widths - a plurality of clamping and / or tensioning devices can be arranged one behind the other in the longitudinal direction.
• the channels 04 of the forme cylinder 02 each also have, for example, one or more clamping devices.
• the forme cylinder 02; 11 as well as in the channels 06 of the transfer cylinders 03; 07 a "minigap technology" is used, in which a leading end is inserted into a narrow channel 04; 06 with an inclined leading hooking edge, the elevator is wound onto the cylinder 02; 03; 07; 11, the trailing end also in channel 04; 06 is inserted, and the ends are clamped against slipping out, for example by means of a rotating spindle or a pneumatic device.
• the transfer cylinder 03; 07 have z. B. in an advantageous embodiment (Fig. 3) only two, circumferentially offset by 180 ° to each other, each having at least one width which corresponds to two widths of a newspaper page.
• the elevators or channels 04 of the forme cylinders 02; 11 complementary to this and must either have, as shown, two continuous channels 04 each having a length of two newspaper page widths, or alternatively pairs of adjacent channels 04 arranged in alignment, each with a length of a newspaper page width.
• each interruption 04 of the forme cylinder 02; 11 in an advantageous embodiment, two clamping devices each of a length which essentially corresponds to a width of a newspaper page.
• the forme cylinder 02; 11 are in an advantageous embodiment with four in the longitudinal direction of the forme cylinder 02; 11 bendable lifts arranged side by side occupy, which have a length in the circumferential direction of a little over the length of the printed image of a newspaper page, and in the longitudinal direction a width of about a newspaper page.
• an arrangement can also be advantageous, wherein the "outer" elevators adjacent to side I and the side II and II are aligned and the “inner” elevators are aligned and closed the former around Are arranged offset by 180 ° (Fig. 4).
• This highly symmetrical arrangement additionally reduces or prevents the risk of vibration excitation in plane E, which is caused by the non-simultaneous passage of channels 04; 06 on page I and page II.
• This also alternately tensioning and relaxing the web 08 alternately on side I and side II, and the resulting vibration of the web 08 can thereby be avoided.
• the forme cylinders 02; 11 in an advantageous embodiment with respect to their axes of rotation R02; R11 fixed.
• the transfer cylinders 03; 07 with respect to their axes of rotation R03; R07 are designed to be movable and are at the same time from the associated forme cylinder 02; 11 and of the cooperating transfer cylinder 03; 07 can be switched off or adjusted to this.
• only the transfer cylinders 03; 07 moves while the forme cylinder 02; 11 remain in their fixed, possibly previously adjusted position.
• the forme cylinders 02; 11 however in appropriate devices, e.g. B. in eccentric or double eccentric bushings, in linear guides or in levers.
• the transfer cylinder 03; 07 can, as schematically in FIGS. 5 to 7, as well as in 8 to 11 are shown in more detail, along a linear adjustment path 16, or, as shown schematically in FIGS. 12 and 13 and in more detail in FIGS. 14 and 15, can be movable along a curved adjustment path 17. Travel 16 and 17 and the transfer cylinder 03; 07 in a print-down position AB are shown in dashed lines in FIGS. 5, 6 and 12.
• the adjustment path 16; 17 by the storage of the transfer cylinder 03; 07 generated in eccentric bushings, not shown, especially in double eccentric bushings.
• an essentially linear actuation path 16 can be generated in the area of the pressure-on position AN, but in the area further away from the pressure point 09, if necessary, a curved actuation path 17 can be generated, which means that the transfer cylinder 03; 07 from the cooperating transfer cylinder 07; 03 as from the associated forme cylinder 02; 11 or vice versa allowed.
• the storage on side I and on side II of the double printing unit 13 is also advantageous for the use of eccentrics.
• FIGS. 5 to 11 are exemplary embodiments for the printing group 01; 12, wherein at least one of the transfer cylinders 03; 07 can be moved along a linear adjustment path 16 (FIG. 5):
• the linear travel 16 takes place by means of linear guides, not shown in FIG. 5, which are arranged in or on the side frame, also not shown in FIG. 5.
• storage in a linear guide is preferably carried out on side I and on side II of the double printing unit 13.
• FIG. 5 shows the course of the web 08 through the printing point 09 located in the print-on position ON.
• the plane E of the double printing unit 13 (FIG. 5) or the respective printing unit 01; 12 (Fig. 6) and the plane of the web 08 intersect in an advantageous embodiment at an angle ⁇ of 70 ° to 85 °.
• This choice of the angle ⁇ contributes to the safe and quick release of the web 08 and / or the parking cylinders 03; 07 from each other with minimized travel 16, and minimizes on the other hand negative influences on the printing result, which are caused by the degree of partial wrapping of the transfer cylinder 03; 07 is significantly influenced (duplication, lubrication, etc.).
• the required linear travel 16 of each transfer cylinder 03; 07 less than or equal to 20 mm for the on / off of the transfer cylinders 03; 07 to / from each other, for an exemption of web 08 in an imprintbetheb up to 35 mm.
• the direction of the linear adjustment path 16 with the plane E forms an angle ⁇ which is essentially 90 °.
• the direction of the linear adjustment path 16 forms an angle ⁇ with a plane of the incoming or outgoing web 08 in the region of an obtuse angle ⁇ between the web 08 and plane E.
• ß 180 ° - ⁇ , where ⁇ z. B. is 5 to 20 °, in particular 7 to 13 °.
• the obtuse angle ⁇ is then preferably 95 ° to 110 ° with linear printing unit 01 and web 08 running straight ahead.
• the angle ⁇ between the travel path 16 and the plane of the path 08 is preferably greater than or equal to 5 °, eg. B. between 5 ° and 30 °, in particular between 5 ° and 20 °.
• the angle ⁇ is in particular for forme cylinder 02; 03; 07; 11 simple circumference greater than or equal to 10 °.
• the angle ⁇ has an upper limit such that the angle ⁇ between the in the direction of the forme cylinder 02; 11 facing part of the plane E and the direction of the parking path 16 is at least 90 °. So is a quick and safe parking of the transfer cylinder 03; 07 simultaneously from the web 08 and the associated forme cylinder 02; 11 guaranteed.
• the direction of the actuating path 16 (in the direction of the shutdown) is selected such that an angle ⁇ between the plane D and the actuating path 16 in the direction of the shutdown is at least 90 ° and at most 120 °, in particular from 90 ° to 115 ° lies.
• the angle ⁇ is again limited upwards in such a way that the angle ⁇ is at least 90 °.
• the double printing unit 13 is multiple, as shown in FIG. 7, for example twice, in a printing unit 19, for. B. a so-called. H-printing unit 19, can be used in a common side frame 20.
• FIG. 7 the separate designation of the parts which are the same as the upper double printing unit 13 for the double printing unit 13 located below is omitted. If all cylinders 02; 03; 07; 11 with a circumference which essentially corresponds to the length of a newspaper page can be saved in terms of installation space, ie at a height h of the printing unit 19.
• this also applies to individual printing units 01; 12, for double printing units 13 and for printing units configured differently, which several printing units 01; 12 have.
• Fig. 7 indicates the transfer cylinder 03; 07 in a second possible position along the linear travel path 16, with here, for example, the upper double printing unit 13, e.g. B. for the printing form change, in the print-down position AB (solid), and the lower double printing unit 13, z. B. for continued printing, is operated in the print-on position ON (solid).
• each of the printing units 01; 12 at least one of its own drive motors 14, which are only indicated by dashed lines in FIG. 7, for the rotary drive of the cylinders 02; 03; 07; 11 on.
• this can be a single drive motor 14 for the respective printing group 01; 12, which in this case, in an advantageous embodiment, is initially placed on the forme cylinder 02; 11 drives, and from there via a mechanical drive connection, for. B. spur gears, timing belts, etc., on the transfer cylinder 03; 07 is driven.
• a mechanical drive connection for. B. spur gears, timing belts, etc.
• it can also be advantageous to move the drive motor 14 to the transfer cylinder 03; 07 and from there to the forme cylinder 02; 11 to drive.
• the type of drive from FIG. 7 (top and bottom) are each shown as examples and can therefore be transferred to the other example.
• the drive by the drive motor 14 is in each case coaxial between axis of rotation R02; R03; R07; R11 and motor shaft, possibly with an angle and / or offset compensating coupling, explained in more detail below. If a "co-movement" of the drive motor 14 or a flexible coupling between the drive motor and the cylinder 02; 03; 07; 11 which may have to be moved is to be avoided, it can also take place via a pinion.
• FIGS. 8 and 9 show a first exemplary embodiment for realizing the linear adjustment path 16 by means of a linear guide.
• the pin 23 of at least one of the transfer cylinders 03; 07 are rotatably mounted, for example, in bearing housings 24 designed as slides 24 in radial bearings 27 (in FIGS. 8 and 9 only the arrangement in the region of one end face of the cylinders 02; 03; 07; 11 is shown).
• the bearing housing 24 or slide 24 can be moved in linear guides 26 which are connected to a side frame 27.
• two linear guides 26 are provided for guiding each bearing housing 24 or slide 24, which run parallel to one another.
• the linear guides 26 of two adjacent transfer cylinders 03; 07 preferably run parallel to one another.
• the linear guides 26 can be arranged directly on walls of the side frame 27, in particular on walls of openings in the side frame 27, which are almost perpendicular to the end face of the cylinders 02; 03; 07; 11 run.
• the side frame 27 has an insert 28, z. B. a so-called. Bell 28 on.
• the linear guides 26 are on or in this bell 28 arranged.
• the bell 28 has an area which extends in the direction of the cylinder 02; 03; 07; 11 emerges from the alignment of the side frame 27.
• the linear guides 26 are arranged in or on this area of the bell 28.
• the distance between the two opposite side frames 20 (only one shown) is oriented i. d.
• the broadest aggregate e.g. B. on the wider inking unit 21, and usually causes a correspondingly longer pin on the cylinders 02; 03; 07; 11.
• the pins of the cylinders 02; 03; 07; 11 can be kept as short as possible.
• the bell 28 has a cavity 29, which is arranged at least partially at the level of the side frame 20.
• the cylinders 02; 03; 07; 11 can also drive connections, such as. B. cooperating drive wheels 30, are housed in this cavity 29.
• On the transfer cylinder 03; 07 can, in an advantageous embodiment (FIG. 9) with drive motor 14 fixed to the frame, between transfer cylinder 03; 07 and drive motor 14 an angular and offset compensating coupling 61 can be arranged to the on and off movement of the transfer cylinder 03; 07 to compensate.
• This can be designed as a double joint 61 or, in an advantageous embodiment, as an all-metal coupling 61 with two torsionally rigid but axially deformable plate packs.
• the all-metal coupling 61 can simultaneously compensate for the offset and the change in length caused therefrom.
• the rotary motion is transmitted without play.
• the clutch 62 is designed as an at least slight angle and offset compensating clutch 62. This is also carried out in an advantageous embodiment as an all-metal clutch 62 with two torsionally rigid but axially deformable plate packs. The linear movement is absorbed by the plate packs which are positively connected in the axial direction to the pin 51 or to a shaft of the drive motor 14.
• the cavity 29 can be limited in a simple manner by means of a cover 31 (dashed lines) without this increasing the width of the machine or protruding from the side frame 20.
• the cavity 29 can then be encapsulated.
• the arrangement of the bell 28 thus shortens the length of the pins, which results in a reduction in the vibration, and enables a simple and variable construction, which is suitable for a wide variety of drive concepts, and with largely identical construction, the change between the concepts - with or without drive connections, with or without lubricant, with or without additional couplings - allowed.
• the drive of the respective bearing housing 24 or slide 24 in the linear guides 26 takes place in the embodiment shown schematically in FIG. B. by means of linear drives 32, for. B. each a screw 32, z. B. a threaded spindle, which is driven by an electric motor, not shown.
• the electric motor can be regulated with respect to a rotational position. To limit the travel in the ON position can be provided for the bearing housing 24, a fixed but adjustable stop.
• the bearing housing 24 can also be driven by means of a lever mechanism. This can also be driven by means of an electric motor or by means of at least one cylinder to which pressure medium can be applied. If the lever mechanism is driven by means of one or more cylinders to which pressure medium can be applied, the arrangement of a synchronizing spindle which synchronizes the actuating movement on the two sides I and II is advantageous.
• connection of the transfer cylinder 03; 07 on the side frame 20 or the bell 28 is carried out in the exemplary embodiment according to FIG. 9 as follows: on both sides of the slide 24 to be guided, the bell 28 has supporting walls 33 which receive one of the two corresponding parts of the linear guide 26. This part can possibly already be part of the support wall 33, or be incorporated into it. The other corresponding part of the linear guide 26 is arranged on the slide 24 or incorporated into it or having it. In an advantageous embodiment, the slide 24 is guided through two such linear guides 26 arranged on two opposite sides of the slide 24.
• the parts of the guides 26 arranged on the supporting walls 33 thus comprise the slide 24 arranged between them.
• the active surfaces of the parts of the linear guide 26 connected to the side frame 20 or the bell 28 point in the same direction Pin 23 facing half space.
• linear bearing 34 in particular a linear movement enabling roller bearing cages 34 are arranged.
• the two parts of the two guides 26 in the ideal state allow movement of the slide 24 only with a degree of freedom as a linear movement.
• the entire arrangement is in a direction perpendicular to the axis of rotation R03; R07 and the direction lying perpendicular to the direction of movement of the carriage 24 are braced against one another essentially without play.
• the part of the guide close to the forme cylinder (with larger dimensions in FIG. 9) has a clamping device (not shown).
• the carriage 24 mounted in the manner described has, for. B. on a radially inward side of the transfer cylinder 03; 07 facing recess, the radial bearing 27 receiving the pin 23.
• the active surfaces of the parts of the linear guide 26 connected to the side frame 20 or the bell 28 point into the half space facing away from the pin 23.
• these parts of the linear guide are arranged on a support 36 connected to the bell 28 (or the side frame 20).
• the carriage 24 has the parts of the linear guide 26 assigned to it in a recess facing the side frame 20 or the bell 28. These parts can be arranged in the recess as components, or can already be incorporated in the slide 24 in an inwardly facing surface of the recess.
• these parts of the linear guide are arranged on a support 36 connected to the bell 28 (or the side frame 20).
• the carriage 24 has the parts of the linear guide 26 assigned to it in a recess facing the side frame 20 or the bell 28. These parts can be arranged in the recess as components, or can already be incorporated in the slide
• the carriage 24 has a connection to the transfer cylinder 03; 07 facing recess in which the radial bearing 27 for receiving the pin 23 is arranged.
• a running surface for rolling elements of the radial bearing 27 designed as a rolling bearing 27 is already incorporated in an inwardly directed surface of the recess.
• the parts of the guides 26 arranged on the slide 24 thus comprise the carrier 36, or the parts of the guides 26 arranged on the carrier 36, on the side frame 20 or on the bell 28.
• the carrier 36 assigned to 07 has an elongated hole oriented in the direction of movement of the slide 24 and not visible in the figures for carrying out the pin 23 to be moved linearly. This elongated hole is at least partially aligned with an elongated hole, likewise not visible, arranged in the bell 28 (or in the associated side frame 20).
• These elongated holes are penetrated by the pin 23 or by a shaft connected to the pin 23, which shaft is used for the rotary drive of the transfer cylinder 03; 07 is connected to a drive wheel 30 (see FIG. 9) or the drive motor 14.
• the carriage 24 can be driven in one of the ways already mentioned in the first exemplary embodiment.
• Fig. 11 shows the implementation of an actuating means designed as a lever mechanism.
• the carriage 24 is connected in an articulated manner via a coupling 37 to a lever 38, which extends essentially parallel to the axis of rotation R03; R07 of the transfer cylinder 03; 07 extending axis is pivotable.
• the coupling 37 of the two adjacent carriages 24 for the transfer cylinders 03; 07 in an articulated manner with the lever 38 embodied here as a three-armed lever 39.
• the lever 38 is driven by at least one actuator 39, e.g. B.
• stops 41 against which the respective carriage 24 is placed in the pressure-on position AN is advantageous.
• These stops are designed to be adjustable in order to set the end position for the transfer cylinders 03; 07 to allow in which their axes of rotation R03; R07 come to lie in level E.
• the system becomes very rigid when the slide 24 is pressed with great force against the stop 41 or the stops 41 (two in each case in FIG. 10).
• each coupling 37 in the manner of a spring strut has a spring assembly 42, e.g. B. a plate spring assembly 42. While the spring assembly 42 of the one transfer cylinder 03; 07 is compressed, the other transfer cylinder 07; 03 associated spring assembly 42 under tensile stress.
• a shaft 43, z. B. a synchronous shaft 43 with the two sides of the transfer cylinder 03; 07 arranged adjusting means in connection.
• the shaft 43 is rotatably connected to the two levers 38, each associated with a side frame 20 on side I and II. This also represents the pivot axis for the lever 38 here.
• an adjustment device can be provided which, in particular during assembly and / or when configurations and / or conditions have changed, a basic setting for the distances of the axis of rotation R02; R03; R07; R11 enables.
• individual cylinders 02; 03; 07; 11, e.g. B. the forme cylinder 02; 11, possibly in an eccentric bushing be stored.
• At least one of the transfer cylinders 03; 07 can be adjustable for adjustment in a radial direction.
• the parts of the linear guides 26 or the carrier 36 assigned to the side frame 20 or the bell 28 can be connected to the side frame 20 or the bell 28 in elongated holes sufficient for adjustment purposes.
• An eccentric and lockable mounting of the radial bearing 27 in the slide 24 is also possible.
• FIGS. 12 to 18 are exemplary embodiments for the printing group 01; 12, wherein at least one of the transfer cylinders 03; 07 can be moved along a curved adjusting path 17 (FIG. 12):
• one of the transfer cylinders 03 is pivotally mounted about a pivot axis S.
• the pivot axis S is here z. B. in the plane E.
• the lever 18 has a length between the mounting of the axis of rotation R03; R07 of the transfer cylinder 03; 07 and the pivot axis S, which is larger than the distance of the axis of rotation R03; R07 of the transfer cylinder 03; 07 from the axis of rotation R02; R11 of the associated forme cylinder 02; 11 in print-on position ON. This means that the transfer cylinder 03; 07 and the associated forme cylinder 02; 11, and vice versa for queuing.
• pivot axis S can in particular, as described in more detail below, eccentrically to the axis of rotation R02; R11 of the associated forme cylinder 02; 11, e.g. B. at a distance from the plane E.
• the storage in a lever 18 is preferably carried out on side I and on side II of the double printing unit 13.
• FIGS. 12 and 13 the course of the web 08 is shown by the printing point 09 in the print-on position ON.
• the plane E of the double printing unit 13 (FIG. 12) or the respective printing group 01; 12 (FIG. 13) and the plane of the web 08 also intersect in an advantageous embodiment at an angle ⁇ of 70 ° to 85 °.
• this choice of the angle ⁇ contributes to the safe and quick release of the web 08 and / or the parking cylinders 03; 07 from each other with minimized travel 16.
• it minimizes negative influences on the printing result which are caused by the extent of partial wrapping of the transfer cylinder or cylinders 03; 07 is significantly influenced (duplication, lubrication, etc.)
• the double printing unit 13 (here in a linear version) is multiple, as shown in FIG. 14, for example twice, in a printing unit 19, for. B. the so-called. H-printing unit 19, can be used in the common side frame 20.
• FIG. 14 the separate designation of the parts that are the same as the upper double printing unit 13 for the double printing unit 13 located below is omitted. For the advantages of this arrangement, reference is made to the comments on FIG. 7.
• FIG. 13 indicates the transfer cylinders 03 with dashed lines (but exaggerated for clarity); 07 in a second possible position along the travel path 17, with here, for example, the upper double printing unit 13, e.g. B. for printing form change, in the print-down position AB, and the lower double printing unit 13, z. B. for continued production, is operated in the print-on position ON.
• each of the printing units 01; 12 at least one separate drive motor 14 for the rotary drive of the cylinders 02; 03; 07; 11 on.
• this can be a single drive motor 14 for the respective printing group 01; 12, which in this case, in an advantageous embodiment, is initially placed on the forme cylinder 02; 11 drives, and from there via a mechanical drive connection, for. B. spur gears, timing belts, etc., on the transfer cylinder 03; 07 is driven.
• the printing group 01; 12 in an embodiment with its own drive motor 14, which is mechanically independent of the other drives, per cylinder 02; 03; 07; 11 about a high degree of flexibility (Fig. 14 shown in dashed lines for the upper double printing unit 13).
• the type of drive from FIG. 14 (top and bottom) are each shown as examples and thus to the other printing units 01; 12 or to transmit the other double printing unit 13.
• the drive motor 14 drives coaxially between the axis of rotation R02; R03; R07; R11 and motor shaft, if necessary via the couplings 61; 62.
• the drive can, if a "co-movement" of the drive motor 14 or a flexible coupling between the drive motor and the cylinder 02; 03; 07; 11 which may be to be moved should be avoided, can also take place via a pinion.
• 15 and 16 show an exemplary embodiment for the implementation of the curved adjustment path 17 by means of the lever 18.
• FIG. 15 shows a side view, two of the end faces of the transfer cylinder 03; 07 (dashed) arranged pin 23 only one is visible.
• the lever 18 is pivotally mounted about the pivot axis S, which is preferably stationary (but possibly adjustable) with respect to the side frame 20.
• the axes of rotation R02; R03; R07; R11 of the cylinder 02; 03; 07; 11 are in the illustrated embodiment in the print-on position again in a plane E, which here with plane D between the cylinders 03; 07 coincides.
• the pivot axis S of the lever 18 is eccentric to the axis of rotation R02; R11 of the forme cylinder 02; 11 is arranged and lies outside the plane E or D.
• the toggle mechanism 46 is articulated to the lever 18 and to a pivot point fixed to the frame.
• the advantageously double-acting pressure cylinder acts z. B.
• the adjusting means 44 can connect the two adjusting means 44 to a shaft 47, e.g. B. have a synchronous shaft 47, or be connected to such.
• a stop 48 is provided for each lever 18, which is preferably designed to be adjustable.
• the drive and actuating means 44; 46 are designed and arranged in such a way that the transfer cylinders 03; 07 in the direction of the obtuse angle ⁇ (for straight web run 180 ° - ⁇ ) between web 08 and level D or E.
• the eccentricity eS of the pivot axis S to the axis of rotation R02; R11 des Forme cylinder 02; 11 is between 7 and 15 mm, in particular approximately 9 to 12 mm.
• the eccentricity eS is in the position of the transfer cylinder 02; 03; 07; 11, ie the axes of rotation R03; R07 lie in the above-mentioned plane D, oriented so that an angle ⁇ -S between the plane D of the cylinders 03; 07 and the connecting plane V of the pivot axis S and the axis of rotation R02; R11 is between 25 ° and 65 °, advantageously between 32 ° and 55 °, in particular between 38 ° and 52 °, the pivot axis S preferably in the range of an obtuse angle ⁇ between the plane D and the incoming or outgoing web 08, and is further apart from the printing point 09 than the axis of rotation R02; R1 1 of the associated forme cylinder 02; 11.
• the eccentric eS z. B an angle of 12 to 52 °, advantageously 19 to 42 °, in particular 25 to 39 ° to the horizontal H.
• the arrangement as described so far satisfies the requirement for switching the printing units 01 on and off without further adjustment mechanisms; 12 or the double printing unit 13.
• the axis of rotation R02; R11 of the forme cylinder 02; 11 is adjustable, e.g. B. also eccentrically for its attachment to the side frame 20, here to a bore 49, stored.
• a pin 51 of the forme cylinder 02; 11 arranged in an eccentric bearing 52 or an eccentric bearing bush 52 which is pivotally mounted in the bore 49.
• a pivot axis S51 of the forme cylinder 02; 11 is eccentric to the axis of rotation R02 by an eccentricity of 5 to 15 mm, in particular approximately 7 to 12 mm; R11 of the forme cylinder 02; 11 and is located outside of level E.
• the eccentricity e-S51 is in the position of the form and associated transfer cylinder 02, 03; 11, 07, d. H.
• the axes of rotation R02, R03 and R11, R07 lie in the plane E, oriented so that an angle ⁇ -S51 between the plane E of the pair of cylinders 02, 03 or 11, 07 and a connecting plane of the pivot axis S51 and the axis of rotation R02; R11 of the forme cylinder 02; 11 between 25 ° and 65 °, advantageously between 32 ° and 55 °, in particular between 38 ° and 52 °.
• the pivot axis S5 is preferably in a half-plane, which is more distant from the axis of rotation R03; R07 of the assigned transfer cylinder 03; 07 as the axis of rotation R02; R11 of the associated forme cylinder 02; 11 lies.
• the swivel axis S51 for the eccentric mounting of the forme cylinder 02; 11 coincides with the pivot axis S of the lever 18 in the exemplary embodiment.
• the coincidence of the pivot axis S and S51 is not mandatory, but it is useful.
• the pivot axis S which is stationary with respect to the side frame 20 and which is caused by pivoting the forme cylinder 02; 11 is not influenced, allows simple and exact adjustment.
• the lever 18 could also be arranged on an eccentric flange of the bearing bush 52 receiving the pins 51, which, however, when twisting a simultaneous adjustment of the distances between the form 02; 11 and transfer cylinder 03; 07 and between the transfer cylinders 03; 07 would have resulted.
• An eccentricity e-S23 of a pivot axis S-23 to the axis of rotation R03; R07 of the transfer cylinder 03; 07 is between 1 and 4 mm, especially around 2 mm.
• the eccentricity e-S23 is in the position of contact of the cylinders 03; 07, d. H.
• the axes of rotation R03; R07 lie in the plane D, oriented so that an angle ⁇ -S23 between the plane D and the connecting plane of the swivel axis S-23 and the axis of rotation R07 (R03) is between 70 ° and 110 °, advantageously between 80 ° and 100 °, is in particular between 85 ° and 95 °.
• the angle ⁇ -S23 should be approx. 90 °.
• FIG. 16 shows an embodiment according to FIG. 15 in a representation of a section along the plane E.
• the pin 51 of the forme cylinder 02; 07 are each in bearings 54, z. B. rolling bearings 54, rotatably mounted.
• this bearing 54 or an additional axial bearing (not shown) enables the movement of the forme cylinder 02; 11 or its pin 51 in the axial direction.
• the bearings 54 are arranged in the eccentric bearing 52 or eccentric bearing bush 52, which in turn is arranged pivotably in the bore 49 in the side frame 20.
• further bearing rings and plain or roller bearings can be arranged between the bore 49 and the pin 51 his.
• the lever 18 is on a to the forme cylinder 02; 07 out of the side frame 20 projecting part of the bearing bush 52, and pivotally mounted relative to this.
• the lever 18 takes in its end remote from the pivot axis S the pin 23 of the transfer cylinder 03; 07, which is rotatable in a bearing 56, and this is arranged in the case of the transfer cylinder 07, pivotable about the pivot axis S-23 in an eccentric bearing 57 or in an eccentric bearing bush 57.
• Such a pivotable bearing bush 57 can, if necessary, also for both transfer cylinders 03; 07 be arranged.
• the side frame 20 has recesses 58 in which the pins 23 of the transfer cylinder 03; 07 are pivotable.
• the actuating means 46; 53 or drive means 44 are not shown in FIG. 8.
• the rotary drive of the cylinders 02; 03; 07; 11 takes place by means of their own, mechanically driven by the respective other cylinders 02; 03; 07; 11 independent drive motors 14, which are preferably arranged fixed to the frame.
• the latter has the advantage that the drive motors 10 do not have to be moved.
• the angle and offset compensating coupling 61 is arranged between the transfer cylinder and the drive motor 10, which coupling is designed as a double joint 61 or, in an advantageous embodiment, as an all-metal coupling 61.
• the all-metal coupling 61 simultaneously compensates for the offset and the change in length caused therefrom, the rotational movement being transmitted without play.
• the drive of the forme cylinder 02; 11 has between the pin 51 and the drive motor 14 the at least one axial relative movement between the cylinder 02; 11 and drive motor 14 receiving clutch 62, which, in order to manufacturing tolerances and any necessary adjustment movements of the forme cylinder 02; 11 to be able to accommodate adjustment purposes, at least slight angles and offsets can be compensated for.
• This is also designed in an advantageous embodiment as an all-metal clutch 62, which absorbs the axial movement by means of the plate packs which are positively connected in the axial direction to the pin 51 or a shaft of the drive motor 14.
• a paired drive can also be driven from the drive motor (possibly via further gear parts, not shown) through a pinion 59 to a drive wheel 61 of the transfer cylinder 03; 07 if, for example, a special torque flow is to be achieved.
• An axis of rotation R59 of the pinion 59 is then preferably fixed to the frame such that a straight line G1 defined by the axis of rotation R59 of the pinion 59 and the pivot axis S of the lever 18 has a straight line defined by the pivot axis S of the lever 18 and the axis of rotation R03; R07 of the transfer cylinder 03; 07 defined level E18 includes an opening angle ⁇ in the range of + 20 ° to - 20 °.
• the aforementioned statements on the drive and for moving the transfer cylinder 03; 07 and the design of the lever 18 or the linear guide 26 are equally applicable to printing units in which the cylinders 02; 03; 07; 11 do not all have the same circumference or diameter (FIG. 19). So can the forme cylinder or cylinders 02; 11 have a circumference U, which in the circumferential direction a pressure side, for.
• the cooperating transfer cylinder 03; 07 has, for example, a circumference or diameter which corresponds to an integer multiple (greater than 1) of that of the forme cylinder 02; 11 , ie it has, for example, a length of two or even three printed pages in newspaper format (or adapted accordingly to other formats).
• the printing point is 03; 07 and a z. B. as a satellite cylinder 07; 03 executed impression cylinder 07; 03 formed, forme and transfer cylinders 02; 11; 03; 07 have a simple circumference and the associated impression cylinder 07; 03 be made many times larger.
• the aforementioned designs also advantageously achieve increased rigidity of the printing unit. This is particularly advantageous in connection with cylinders 02; 03; 07; 11, which have a length that corresponds to at least four or even six standing printed pages, in particular newspaper pages.
• At least one of the transfer cylinders 03; 07 adjustable so far that the retracted web 08 during of the printing operation by means of other printing units can be guided through the printing point 09 without contact.
• the cylinders 02; 03; 07; 11 can, as described, be driven either in pairs or individually by a separate drive motor 14 for all of the exemplary embodiments.
• a drive is also possible, one of the forme cylinders 02; 11 of a printing group 01; 12 its own drive motor 14, and the remaining cylinders 02; 03; 07; 11 of the printing group 01; 12 have a common drive motor 14.
• a configuration of four or five cylinders 02; 03; 07; 11 with three drive motors 14 can be advantageous: In the case of a double printing unit 13 z. B.
• the four cylinders 02; 03; 07; 11 each in pairs by a drive motor 14 depending on the requirement of the forme cylinder 02; 11 or from the transfer cylinder 03; 07 ago driven by rotation.
• the drive wheels 30, each forming a transmission, between the forme cylinder 02; 11 and the respectively assigned transfer cylinder 03; 07 each form a drive connection with the associated drive motor 14.
• the two pairs of drive wheels 30 are preferably arranged with respect to one another in such a way that they are disengaged. H. in two drive levels.
• the design of the cooperating drive wheels (30) between the form and transfer cylinders 02, 03; 11, 07 each with one Straight toothing to prevent relative axial movement of one of the two cylinders 02; 03; 07; 11 enable, but without changing the relative position in the circumferential direction.
• the latter also applies to a possibly arranged pinion between the drive motor 14 and the drive wheel of the forme cylinder 02; 11 when the pair on the forme cylinder 02; 11 is not driven coaxially.
• a cooperating pair of links in the drive connection between drive motor 14 and forme cylinder 02; 11 straight teeth and axially movable against each other to the axial movement of the forme cylinder 02; 11 without ensuring twisting at the same time.
• the drive situations shown in FIGS. 9 and 11 can be mutually transferred to the two versions shown for realizing the linear movement.
• the drive motors 14 are arranged in an advantageous embodiment fixed to the frame. Should the cylinder 02; 03; 07; 11 driving drive motor 14 deviating from this, however, be arranged in a cylinder-fixed manner, so it can be during the actuating movement and / or adjustment of the cylinder 02; 03; 07; 11 in a variant also on a corresponding (or the same) guide or lever, z. B. carried on an outside of the side frame 20.
• the drive motor 14 is advantageously designed as an electric motor, in particular as an asynchronous motor, synchronous motor or as a DC motor.
• a gear 63 is arranged between each of the drive motors 14 and the cylinder 02; 03; 07; 11 .
• This gear 63 can be connected to the drive motor 14 attachment gear 63, e.g. B. be a planetary gear 63.
• it can also be designed as a differently designed reduction gear 63, e.g. B. from pinion or belt and drive wheel.
• each gear 63, z. B. as individually encapsulated attachment gear 63.
• the lubricant spaces thus generated are spatially limited and prevent contamination of neighboring machine parts and contribute to an increase in the quality of the product. If the bell 28 (FIG. 11) is used, the gears between the form and transfer cylinders 02, 03; 07, 11 arranged in the cavity 29, and encapsulated as a lubricant chamber to the outside.
• the drive units each encapsulated, d. H. each with its own lubricant chamber.
• One of the above single encapsulation extends, for example, around the paired drive of two cylinders 02, 03; 11, 07 or - especially in the case of the bell 28 described above - around both pairs.
• a bell 28 can also be used for a pair of two cylinders 02; 03; 07; 11 be executed. The latter is advantageous in the sense of modularization, for example.
• the respective forme cylinder 02; 11 assigned inking unit 21 and, if present, the assigned dampening unit 22 is rotatably driven by a drive motor which is independent of the drive of the printing unit cylinders.
• the inking unit 21 and any dampening unit 22 which may be present can each have their own drive motor.
• the anilox roller can, and in the case of a roller inking unit 21, the one or more distribution cylinders can do so individually or be driven in groups by rotation.
• the one or more distribution cylinders of a dampening unit 22 can also be driven in rotation individually or in groups.
• the execution of the cylinder 02; 03; 07; 11 double width and - at least the forme cylinder 02; 11 - with "single scope” enables, in contrast to printing presses with double scope and single width, a significantly higher product variability.
• the maximum number of possible print pages is the same, but in the case of the single-width printing units 01; 12 double scope in the collecting operation in two different " In the present case of the double-wide printing units 01; 12 of simple circumference, the (double-wide) webs 08 are cut lengthways after printing.
• the double-width printing press of a simple scope has a high degree of variability, particularly in the grading of the possible number of pages in the product, in the so-called "page jump". While the thickness per booklet (position) for the printing press with double the circumference and single width in the collecting operation (ie maximum product thickness) ) can only be varied in steps of four printed pages, the double-width printing press of simple scope described allows a "page jump" from two pages (e.g. in Newspaper printing). The product strength and in particular the "distribution" of the printed pages on different issues of the overall product or products is considerably more flexible.
• the partial web is thus either guided onto a folding former and / or folder which is different from the corresponding partial web, or else it is turned to escape the latter. That is, in the second case, the partial web is brought into the correct longitudinal or cutting register before, during or after turning, but before merging with the "straight webs". This is done depending on the channels 04; 06 of a cylinder 02; 03; 07; 11 are taken into account in an advantageous embodiment by corresponding design of the turning deck (eg preset distances of the bars or of the path sections).
• the fine adjustment or control is carried out with the adjustment paths of the cut register control for the relevant partial web and / or partial web strand, in order to bring partial webs of two different running levels into register with one another if necessary.
• the forme cylinder 02; 11 can now be loaded in the circumferential direction with one and in the longitudinal direction with at least four standing printed pages in broadsheet format (FIG. 20).
• this forme cylinder 02; 11 also optionally in the circumferential direction with two and in the longitudinal direction with at least four lying printed pages in tabloid format (Fig. 21) or in the circumferential direction with two and in the longitudinal direction with at least eight standing printed pages in book format (Fig. 22) or in the circumferential direction with four and in the longitudinal direction with at least four lying printed pages in book format (FIG. 23) by means of one in the circumferential direction of the forme cylinder 03 and its longitudinal direction at least one flexible printing plate which can be arranged thereon.
• the double printing unit has a web width corresponding to four standing printed pages in broadsheet format for the production of two single-layer products in broadsheet format with four printed pages in one product and four printed pages in the other product or with two printed pages in one product and six Print pages can be used in the other product.
• a web width corresponding to three standing printed pages it can be used for the production of two single-layer products in broadsheet format with four printed pages in one product and two printed pages in the other product.
• the double printing unit 13 has a web width corresponding to four standing printed pages in broadsheet format for the production of a two-layer product in broadsheet format with four printed pages in one layer and four printed pages in the other layer or two printed pages in one layer and six printed pages usable in the other layer.
• a web width corresponding to three standing printed pages it can be used for the production of a two-layer product in broadsheet format with four printed pages in one layer and two printed pages in the other layer.
• the double printing unit for the production is in a gradation of four lying on the forme cylinder 02; 11 arranged printed pages of changeable products (kidney page jump ”) can be used in tabloid format.
• the double printing unit 13 with a web width corresponding to four or three or two lying printed pages or a lying printed page is suitable for the production of one from one layer in the above sequence with sixteen or 12 or 8 or 4 printed pages of existing product in tabloid format can be used.
• the double printing unit is with a web width corresponding to four lying print pages in tabloid format for the production of two products in tabloid format each consisting of one layer with eight printed pages in one product and eight printed pages in the other product or with four printed pages in one product and twelve Print pages can be used in the other product.
• a web width corresponding to three lying printed pages it can be used for the production of two tabloid-sized products each with four printed pages in one product and eight printed pages in the other product.
• the double printing unit 13 is standing on the forme cylinder 02; 11 arranged printed pages of changeable ("eight page jump") products can be used.
• Double printing unit 13 can be used for the production of two one-layer products in book format with sixteen printed pages in one product and sixteen printed pages in the other product or twenty-four printed pages in one product and eight printed pages in the other product.
• a web width corresponding to six standing printed pages in book format it can be used for the production of two single-layer products in book format with sixteen printed pages in one product and eight printed pages in the other product.
• the double printing unit 13 can be used for products in book format for the production in a gradation of eight printable pages arranged on the forme cylinder 03 and changeable products (“eight-page jump”) (double transverse fold).
• the double printing unit 13 is suitable for producing a product consisting of one layer in the above sequence with thirty-two or twenty-four or twenty or sixteen or eight printing pages Book format usable.
• the double printing unit is with a web width corresponding to four lying printed pages in book format for the production of two one-layer products in book format with sixteen printed pages in one product and sixteen printed pages in the other product or twenty-four printed pages in one product and eight printed pages usable in the other product.
• a web width corresponding to three lying printed pages in book format it can be used for the production of two single-layer products in book format with sixteen printed pages in one product and eight printed pages in the other product. If the two partial web strands are folded lengthways on different hoppers and then fed into a common folder, the above is to be used for the distribution of the product on different, combined booklets or layers with the variable number of pages described.

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• Mechanical Engineering (AREA)
• Engineering & Computer Science (AREA)
• Rotary Presses (AREA)
• Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
• Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
• Printing Methods (AREA)
• Manufacturing Of Printed Wiring (AREA)
• Printers Or Recording Devices Using Electromagnetic And Radiation Means (AREA)
• Electrostatic Charge, Transfer And Separation In Electrography (AREA)
• Handling Of Sheets (AREA)
• Character Spaces And Line Spaces In Printers (AREA)
• Inking, Control Or Cleaning Of Printing Machines (AREA)
• Perforating, Stamping-Out Or Severing By Means Other Than Cutting (AREA)
• Application Of Or Painting With Fluid Materials (AREA)
• Sewing Machines And Sewing (AREA)
• Bearings For Parts Moving Linearly (AREA)
• General Factory Administration (AREA)
• Screen Printers (AREA)

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• 2002
  • 2002-04-06 AT AT07101541T patent/ATE434520T1/de not_active IP Right Cessation
  • 2002-04-06 EP EP03103416A patent/EP1378350A3/fr not_active Withdrawn
  • 2002-04-06 WO PCT/DE2002/001264 patent/WO2002081216A2/fr not_active Ceased
  • 2002-04-06 DE DE50213618T patent/DE50213618D1/de not_active Expired - Fee Related
  • 2002-04-06 DE DE50201368T patent/DE50201368D1/de not_active Expired - Lifetime
  • 2002-04-06 RU RU2003132536/12A patent/RU2263029C2/ru not_active IP Right Cessation
  • 2002-04-06 WO PCT/DE2002/001265 patent/WO2002081217A2/fr not_active Ceased
  • 2002-04-06 EP EP03103411A patent/EP1371485A3/fr not_active Withdrawn
  • 2002-04-06 AT AT03103401T patent/ATE358018T1/de not_active IP Right Cessation
  • 2002-04-06 AT AT02740232T patent/ATE270613T1/de not_active IP Right Cessation
  • 2002-04-06 WO PCT/DE2002/001267 patent/WO2002081213A2/fr not_active Ceased
  • 2002-04-06 EP EP02742673A patent/EP1377456B1/fr not_active Expired - Lifetime
  • 2002-04-06 DE DE10215261A patent/DE10215261A1/de not_active Withdrawn
  • 2002-04-06 RU RU2005120377/21A patent/RU2415016C2/ru not_active IP Right Cessation
  • 2002-04-06 CN CNB02811583XA patent/CN1317125C/zh not_active Expired - Fee Related
  • 2002-04-06 JP JP2002579229A patent/JP2004527399A/ja active Pending
  • 2002-04-06 AT AT05101366T patent/ATE433862T1/de not_active IP Right Cessation
  • 2002-04-06 AT AT03103427T patent/ATE433859T1/de not_active IP Right Cessation
  • 2002-04-06 DE DE50200604T patent/DE50200604D1/de not_active Expired - Fee Related
  • 2002-04-06 EP EP03103427A patent/EP1378351B1/fr not_active Expired - Lifetime
  • 2002-04-06 US US10/473,141 patent/US7140295B2/en not_active Expired - Fee Related
  • 2002-04-06 EP EP03104076.9A patent/EP1393900B1/fr not_active Expired - Lifetime
  • 2002-04-06 AT AT07101553T patent/ATE435120T1/de not_active IP Right Cessation
  • 2002-04-06 ES ES03103401T patent/ES2281603T3/es not_active Expired - Lifetime
  • 2002-04-06 ES ES07101541T patent/ES2325639T3/es not_active Expired - Lifetime
  • 2002-04-06 ES ES02740232T patent/ES2220895T3/es not_active Expired - Lifetime
  • 2002-04-06 EP EP03103407A patent/EP1375139B1/fr not_active Expired - Lifetime
  • 2002-04-06 DE DE50209830T patent/DE50209830D1/de not_active Expired - Lifetime
  • 2002-04-06 AT AT02742672T patent/ATE271973T1/de not_active IP Right Cessation
  • 2002-04-06 ES ES02742671T patent/ES2224070T3/es not_active Expired - Lifetime
  • 2002-04-06 AT AT02740233T patent/ATE280042T1/de active
  • 2002-04-06 EP EP07101553A patent/EP1775123B1/fr not_active Expired - Lifetime
  • 2002-04-06 DE DE50200714T patent/DE50200714D1/de not_active Expired - Fee Related
  • 2002-04-06 EP EP05101366A patent/EP1543964B1/fr not_active Expired - Lifetime
  • 2002-04-06 EP EP07101541A patent/EP1775125B1/fr not_active Expired - Lifetime
  • 2002-04-06 EP EP02740232A patent/EP1377452B1/fr not_active Expired - Lifetime
  • 2002-04-06 EP EP03103432A patent/EP1378352A3/fr not_active Withdrawn
  • 2002-04-06 WO PCT/DE2002/001263 patent/WO2002081215A2/fr not_active Ceased
  • 2002-04-06 EP EP03103443A patent/EP1384579A3/fr not_active Withdrawn
  • 2002-04-06 ES ES02742673T patent/ES2220896T3/es not_active Expired - Lifetime
  • 2002-04-06 AT AT02742673T patent/ATE270614T1/de not_active IP Right Cessation
  • 2002-04-06 DE DE50213624T patent/DE50213624D1/de not_active Expired - Lifetime
  • 2002-04-06 EP EP03103401A patent/EP1375137B1/fr not_active Expired - Lifetime
  • 2002-04-06 DE DE50200670T patent/DE50200670D1/de not_active Expired - Fee Related
  • 2002-04-06 AU AU2002338305A patent/AU2002338305A1/en not_active Abandoned
  • 2002-04-06 ES ES02742672T patent/ES2224071T3/es not_active Expired - Lifetime
  • 2002-04-06 EP EP03103402A patent/EP1375138A3/fr not_active Withdrawn
  • 2002-04-06 ES ES05101366T patent/ES2325623T3/es not_active Expired - Lifetime
  • 2002-04-06 CN CNB028115848A patent/CN1297402C/zh not_active Expired - Fee Related
  • 2002-04-06 EP EP02742671A patent/EP1377454B1/fr not_active Expired - Lifetime
  • 2002-04-06 AU AU2002315636A patent/AU2002315636A1/en not_active Abandoned
  • 2002-04-06 US US10/473,148 patent/US7156018B2/en not_active Expired - Fee Related
  • 2002-04-06 DE DE50208204T patent/DE50208204D1/de not_active Expired - Lifetime
  • 2002-04-06 EP EP05100307A patent/EP1541347A3/fr not_active Withdrawn
  • 2002-04-06 KR KR1020037013215A patent/KR100564781B1/ko not_active Expired - Fee Related
  • 2002-04-06 EP EP07101568A patent/EP1782950A3/fr not_active Withdrawn
  • 2002-04-06 AU AU2002338304A patent/AU2002338304A1/en not_active Abandoned
  • 2002-04-06 DE DE50200602T patent/DE50200602D1/de not_active Expired - Fee Related
  • 2002-04-06 WO PCT/DE2002/001266 patent/WO2002081218A2/fr not_active Ceased
  • 2002-04-06 EP EP03103442A patent/EP1378353A3/fr not_active Withdrawn
  • 2002-04-06 US US10/473,147 patent/US7213513B2/en not_active Expired - Fee Related
  • 2002-04-06 DE DE50213640T patent/DE50213640D1/de not_active Expired - Lifetime
  • 2002-04-06 EP EP02742672A patent/EP1377455B1/fr not_active Expired - Lifetime
  • 2002-04-06 JP JP2002579234A patent/JP4146240B2/ja not_active Expired - Fee Related
  • 2002-04-06 DE DE50213659T patent/DE50213659D1/de not_active Expired - Lifetime
  • 2002-04-06 AT AT03103407T patent/ATE340076T1/de not_active IP Right Cessation
  • 2002-04-06 ES ES02740233T patent/ES2229152T5/es not_active Expired - Lifetime
  • 2002-04-06 EP EP02740233A patent/EP1377453B2/fr not_active Expired - Lifetime
  • 2002-04-06 AT AT02742671T patent/ATE271465T1/de not_active IP Right Cessation
• 2006
  • 2006-04-27 JP JP2006124068A patent/JP2006199046A/ja active Pending
  • 2006-06-30 US US11/477,523 patent/US7469637B2/en not_active Expired - Fee Related
  • 2006-08-29 US US11/511,403 patent/US20060288890A1/en not_active Abandoned
• 2007
  • 2007-04-06 US US11/783,144 patent/US20070181021A1/en not_active Abandoned
• 2008
  • 2008-07-15 US US12/219,036 patent/US7707935B2/en not_active Expired - Fee Related

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