EP1733876A2 - Méthode et procédé pour le réglage d'un cylindre ou d'un rouleau - Google Patents

Méthode et procédé pour le réglage d'un cylindre ou d'un rouleau Download PDF

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Publication number
EP1733876A2
EP1733876A2 EP20060115151 EP06115151A EP1733876A2 EP 1733876 A2 EP1733876 A2 EP 1733876A2 EP 20060115151 EP20060115151 EP 20060115151 EP 06115151 A EP06115151 A EP 06115151A EP 1733876 A2 EP1733876 A2 EP 1733876A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
roller
bearing
stop
linear bearing
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Withdrawn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
EP20060115151
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German (de)
English (en)
Inventor
Ewald RÖTHLEIN
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.)
Filing date
Publication date
Application filed by Koenig and Bauer AG filed Critical Koenig and Bauer AG
Publication of EP1733876A2 publication Critical patent/EP1733876A2/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Withdrawn legal-status Critical Current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
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/26—Arrangement of cylinder bearings
    • B41F13/30—Bearings mounted on sliding supports

Definitions

  • the invention relates to a method and a device for adjusting a cylinder or a roller according to the features of claim 1 or 9.
  • a device for inking a roller of the printing unit In connection with an inking unit for a printing unit of a double wide printing machine, a device for inking a roller of the printing unit is known in which either two in the axial direction of the roller juxtaposed doctor blade independently of each other, or arranged a doctor blade with a length of at least four side by side Newspaper pages can be switched on or off at the roller.
  • the WO 01/49491 A2 discloses an apparatus for adjusting a roll of a printing press.
  • the WO 02/081213 A2 describes a printing unit of a printing press, wherein the cylinders are displaceable in linear bearings.
  • the invention has for its object to provide a method and apparatus for adjusting a cylinder or a roller.
  • the advantages that can be achieved with the invention are, in particular, that a machine that is easy to manufacture or operate and / or spatially comparatively compact and / or that enables a high print quality is created.
  • the intended coupling of the chambered doctor blade with the linear support of the anilox roller additionally affords the following advantage: It is advantageous in the case of a hydraulic adjustment of the doctoring system to a pneumatic adjustment that the hydraulic pressure column is not compressible. A disadvantage, however, in this embodiment, that a quick shutdown of the doctor chamber of the anilox roller in a necessary change in position of the anilox roller, z. B. due to a paper tear, is not possible. By provided according to the invention coupling with the linear slide of the anilox roll this disadvantage is avoided.
  • An otherwise not shown flexographic printing machine comprises several, for example, two juxtaposed printing towers 01, each of which several, especially two superimposed printing unit 03, in particular satellite printing units 03, through which printed material webs 02, in particular paper webs 02 for two-sided, multicolor printing are.
  • the printing towers 01 can be arranged on a machine platform, not shown, and underneath the pedestal can be arranged roll changers, not shown, which feed the printing towers 01 with the paper webs 02.
  • the printing towers 01 are traversed by the paper webs 02 in the transport direction from bottom to top.
  • Printed, led out of the towers 01 paper webs 02 can be merged in a superstructure of the printing machine, not shown, and one or more processing stations such as a cutting station and one or more post-processing stations such as a folding unit supplied.
  • Each satellite printing unit 03 comprises a central cylinder 05 serving as a counterpressure cylinder 05, namely the satellite cylinder 05, and a plurality of, preferably at least four, in the case of the exemplary embodiment exactly four printing units 04 arranged on the satellite cylinder 05.
  • Each printing unit 04 is designed for high pressure, in particular for the flexographic printing.
  • the general structure and operation of flexographic printing units 04 is generally state of the art, so that it need not be discussed in detail. In the highly schematic representation according to FIGS.
  • the embodiment according to FIG. 2 differs from the embodiment according to FIG. 1 essentially only by the respectively somewhat different arrangement of the printing units 04 on the satellite cylinder 05.
  • the flexographic printing machine is designed, for example, for newspaper printing.
  • the width of the machine is, in the axial direction of the cylinder 05; 06; 07, such that the forme cylinder 06 in the axial direction as a printed image 29 have at least two, preferably four newspaper pages.
  • the diameter of the forme cylinder 06 is preferably selected such that the forme cylinders 06 have four newspaper pages in the circumferential direction as print image 29.
  • the bale of the forme cylinder 06 can have a circumference of 1,100 mm to 1,300 mm and a length of 1,400 mm to 1,800 mm.
  • the forme cylinders 06 bear four flexographic printing plates side by side in the axial direction (not shown here) and two flexographic printing plates in succession in the circumferential direction.
  • the diameter of the satellite cylinder 05 is preferably an integer multiple, in particular a triple of the diameter of the associated forme cylinder 06; However, it may also be advantageous to dimension the satellite cylinder 05 so that its diameter is in particular a 2.5 times the diameter of the associated forme cylinder 06. According to a further aspect, it is advantageous to dimension the circumference of the satellite cylinder 05 so that it corresponds to an integer multiple of the section length of a printed product manufactured with the flexographic printing press.
  • the forme cylinder 06, the anilox roller 07 and the chamber doctor blade 08 of each printing unit 04 are each guided so that they can be adjusted to the satellite cylinder 05 and are offset by this.
  • the forme cylinder 06, the anilox rollers 07 and the chamber doctor blades 08 are each mounted in bearing units 14, cf. Fig. 2, in addition to a rotary bearing, each also comprise a linear bearing 15, as will be explained in detail below.
  • each forme cylinder 06, each anilox roller 07 and each chambered doctor blade 08 each have its own linear bearing 15 assigned.
  • the bearing units 14 or linear bearings 15 of the forme cylinder 06 and the anilox rollers 07 on the one hand and the chambered doctor blades 08 on the other hand can be structurally designed in each case differently.
  • drive motors 121 which in particular each angular position-controlled electric motors 121, preferably a synchronous motor 121 and / or a drive motor 121 may act with permanent magnet excitation.
  • drive motors 121 preferably used herein follows below.
  • FIGS. 3 and 4 show a bearing unit 14, preferably based on linear travel paths, in schematic longitudinal and cross-section.
  • the on / off mechanism integrating bearing unit 14 has in addition to a bearing 71, z. B. radial bearing 71, for example, a cylindrical roller bearing 71, for rotatably supporting the cylinder 06; 07 storage means 72; 73 or bearing elements 72; 73 for a radial movement of the cylinder 06; 07 for pressure on or pressure off.
  • the bearing unit 14 (after mounting the bearing unit 14 frame-fixed) carrier-resistant bearing elements 72 as well as against them movable bearing elements 73.
  • the carrier-fixed and movable bearing elements 72; 73 are as co-operating linear elements 72; 73 and together with corresponding sliding surfaces or intermediate rolling elements total as a linear guide 70, z. B. linear bearing 70 is formed.
  • the linear elements 72; 73 take in pairs a radial bearing 71 receiving bearing block 74, z. B. carriage 74 between them.
  • Bearing block 74 and the movable bearing elements 73 may also be made in one piece.
  • the carrier-fixed bearing elements 72 are arranged on a carrier 76, which in total with the side frame 11; 12 of a printing tower 01 is connected or is.
  • the carrier 76 is designed for example as a support plate 76, which, for example, at least on a drive side, a recess 77 for the passage of a shaft 78, z. B. drive shaft 78 of a pin 63; 64 of a cylinder 06; 07 has.
  • the side frame 11; 12 on the drive side preferably has a recess or an opening for a drive shaft 78.
  • On the opposite side of the drive side does not necessarily have a recess 77 or a recess in the side frame 12; 11 may be provided.
  • a length of the linear bearing 70 is smaller than a diameter of the associated cylinder 06 in the direction of adjustment S; 07th
  • the clamping device 66 is here for example as z. T. slotted hollow shaft end formed, which comprises the journal end (pin 63, 64) and is to be pulled together by means of a screw in such a way that a frictional rotationally fixed connection between the journal end (pin 63, 64) and hollow shaft inner surface can be produced.
  • the coupling can also be used in other ways, eg.
  • the shaft 78 is formed by a recess in the side frame 11; 12 out, which is sufficiently large for the movement of the shaft 78 is dimensioned together with the bearing block 74 and which z. B. is formed in the manner of a slot.
  • a cover 69 may be provided with a slot covering the collar, which z. B. with the bearing block 74, but not connected to the shaft 78.
  • one of possibly a plurality of serially arranged coupling 148 is connected to the cylinder-distal end of the shaft 78 by a rotationally fixed connection 75, eg, a piston.
  • a rotationally fixed connection 75 eg, a piston.
  • B. a clamping element 75 coupled.
  • a transmission with drive motor 121 without angle and / or offset compensating coupling 148 can be coupled directly to the shaft 78.
  • the drive motor 121 is not fixed to the frame, but arranged cylinder-tight and is connected to the cylinder 06; 07 moved.
  • the pin 64 is preferably provided with a device for axially moving the cylinder 06, d. H. coupled with a side register drive, not shown.
  • a device for axially moving the cylinder 06 d. H. coupled with a side register drive, not shown.
  • the example in the manner of Figure 3 with the pin 63; 64 connected shaft 78 is this about a camp, z. B. thrust bearing connected to an axial drive.
  • linear bearings 70 in such a way that the cooperating bearing elements 72; 73 both on the assembly storage unit 14 - and not a part of the side frame 11; 12 of the printing tower 01 or the printing unit 03 - are provided, allows pre-assembly and pre-adjustment or adjustment of the bearing voltage.
  • the advantageous arrangement of the two bearing block 74 encompassing linear bearing 70 allows a backlash-free setting, since the two linear bearings 70 in the manner opposed to, that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 06; 07 learn or record.
  • the linear bearings 70 are thus adjustable in the direction to which it is at play-free positions of the cylinder 06; 07 also arrives.
  • non-penetration and the above definition with respect to the clear width is to be understood in a broader sense as meaning that, at least in the region of the intended end position, the cylinder 06; 07 and at least on a continuous path from a frame edge to the location of the end position such a "non-penetration" is present, so that the cylinder unit 80 of an open, between the two end-side side frames 11; 12 lying side without tilting, d. H.
  • the bearing units 14 are in the manner on the inner walls of the side frame 11; 12 arranged that the cylinder 06; 07, in particular their bearing units 14 on the cylinder side by the side frame 11; 12 are supported, which has static and mounting advantages.
  • the linear bearings 70 (72, 73) which can be seen in FIGS. 3 and 4 thus each have pairings of corresponding cooperating bearing means 72 and 73 or their guide or active surfaces, designed as sliding surfaces (not shown) or with rolling elements 65 arranged therebetween.
  • Fig. 5 is in preferred Execution of at least one of the two, advantageous both linear bearings 70 of a bearing unit 14 carried out such that the two corresponding bearing means 72 and 73 each have at least two guide surfaces 72.1; 72.2; 73.1; 73.2, which in two mutually inclined planes E1; E2 are lying.
  • the two guide surfaces 72.1; 72.2; 73.1; 73.2 (or their planes E1, E2) of the same bearing means 72; 73 are z. B.
  • the two guide surfaces 73.1; 73.2; 72.1; 72.2 of the cooperating bearing means 73; 72 are complementary in shape.
  • At least one of the two pairings of cooperating guide surfaces 72.1; 73.1 or 72.2; 73.2 is parallel to a plane E1 or E2, which has a component not equal to zero in the radial direction of the cylinder axis and thereby the degree of freedom of movement in a purely axial direction of the cylinder 06; 07 stops.
  • both pairings lie to planes E1; E2, which both have a component not equal to zero in the radial direction of the cylinder axis, but in reverse tilt against the cylinder axis and thereby the degree of freedom of movement in both axial directions of the cylinder 06; 07 stop.
  • a section line of the two planes E1; E2 is parallel to the direction S
  • the inclined active or guide surfaces 72.1; 72.2; 73.1; 73.2 are arranged so that they a relative movement of the bearing parts of the linear bearing 70 in the axial direction of the cylinder 06; 07, ie the bearing is "tied off” in the axial direction.
  • the linear bearings 70 both a cylinder 06; 07 frontally associated bearing units 14 two mutually arranged pairs of cooperating active or guide surfaces 72.1; 72.2; 73.1; 73.2.
  • at least one of the two radial bearings 71 of the two bearing units 14 a slight bearing clearance .DELTA.71 in the axial direction.
  • the frame-fixed bearing means 72 encompass here the bearing block 74 arranged between them.
  • the frame-fixed guide surfaces 72.1; 72.2 of the two linear bearings 70 thus partially surround the guide surfaces 73.1; 73.2 of the bearing block 74 with respect to an axial direction of the cylinder 06; 07th
  • assembly aids 89, z. B. dowel pins 89 in the side frame 11; 12 can be provided, to which the bearing unit 14 of the fully assembled cylinder unit 80 is aligned, before they by releasable retaining means 91, z. B. screws 91, or even cohesively by welding to the side frame 11; 12 are connected.
  • corresponding means 92 e.g. B. clamping screws 92 may be provided (Fig. 3).
  • the bearing unit 14 - at least to the cylinder side - by a cover 94 largely protected against contamination or even encapsulated executed as a unit.
  • Fig. 3 is schematically the cylinder 06; 07 with pin 63; 64 and a preassembled storage unit 14.
  • This module can thus be preassembled between the side frames 11; 12 of the printing unit 03 and the printing tower 01 are used in an easy to install and attached to designated locations.
  • the bearing units 14 for forme cylinder 06 and anilox roller 07 - possibly up to the permitted operational size of the travel - executed identical.
  • the effective inner surface of the radial bearing 71 and the outer effective lateral surface of the pin 63; 64 be cylindrical instead of tapered, since both the assembly of the bearing unit 14 on the pin 63; 64 as well as the setting of the bearing clearance outside of the printing unit 03 can be done.
  • the storage unit 14 can be shrunk, for example.
  • the mountable as a whole unit is advantageous in the manner of an optionally partially open housing of z. B. the carrier 76, and / or z. B. a frame (in Fig. 4 without reference numeral, for example, the four the bearing unit 14 to all four sides outwardly bounding plates) and / or z. B. the cover 94 (Fig. 3).
  • the frame-fixed bearing elements 72 are arranged substantially parallel to one another and define the adjustment direction S (FIG. 4).
  • Pressing is effected by moving the bearing block 74 in the direction of the pressure point by means of a force F applied to the bearing block 74 by at least one actuator 82, in particular by a force-controlled or force-defined actuator 82, by means of which a defined resp . definable force F in print-on direction on the bearing block 74 can be brought (Fig. 4).
  • the decisive for the color transfer and thus the print quality, among other line force in the Nippstellen is therefore not by a travel, but by the balance of power between the force F and between the cylinders 06; 07 resulting line force F L and the resulting equilibrium defined.
  • cylinders 06; 07 in pairs together by the Storage block 74 is acted upon by the actuator (s) 82 with the corresponding adjusted force F.
  • the storage unit 14 has a positionable means 79, z. B. a stop 79, which limits the travel to the pressure point.
  • the stop 79 can be moved in such a way that the stop surface 83, which acts as a stop, can be varied along the direction of adjustment S at least in one region. It is thus an adjustment device (adjustable stop 79) provided in an advantageous embodiment, by means of which the position of a pressure near the end position of the bearing block 74 is adjustable.
  • the placement of the stop 79 can basically be done manually or via an actuator 84 (see below).
  • At least one resilient element 81, z. B. spring element 81 which applies to the bearing block 74 a force F R from the stop 79 in a direction away from the stop surface 83 away.
  • the spring member 81 causes pressure-off in the event that the bearing block 74 is not prevented from moving in any other way.
  • the applied force F, the restoring force F R and the position of the stop 79 is selected such that between stop 79 and the stop surface of the Bearing block 74 in Anstelllage no significant force .DELTA.F is transferred, for example, that
  • the contact force between the cylinders 06; 07 substantially determined by the voltage applied by the actuator 82 force F.
  • the decisive for the color transfer and thus the print quality, among other decisive line force in the Nippstellen is therefore not primarily by a travel, but at quasi-free stop 79 defined by the force F and the resulting balance. Basically, after finding the basic setting with the appropriate forces F, a removal of the stop 79 or a corresponding fixation, which is effective only during the basic adjustment, would be conceivable.
  • the actuator 82 can be embodied as any desired actuator 82 applying a defined force F.
  • the actuator 82 is designed as actuatable by pressure medium actuating means 82, in particular as a piston 82 movable by a fluid.
  • Advantageous in terms of possible tilting is the arrangement of several, here two, such actuators 82.
  • a liquid eg. As oil or water, used.
  • the mountable as a whole bearing unit 14 has two simultaneously operable, acting in the same direction and with their force application points on the bearing block 74 in a direction perpendicular to the cylinder axis spaced actuators 82 for pressure-on position.
  • a controllable valve 93 is provided in the bearing unit 14. This is performed, for example, electronically controlled and provides a hydraulic piston in a position without pressure or at least to a lower pressure level, while in another position of the force F conditional pressure P is applied.
  • a non-designated leakage line is provided here for safety.
  • a travel limit by a mobile, force-limited stop 88 as overload protection 88, z. B. spring element 88 may be provided, which in the operational pressure-Ab, d. H. the pistons 82 are unloaded and / or retracted, although serve as a stop 88 for the bearing block 74 in pressure-off position, in the case of a web winder or other excessive forces from the pressure point ago, however, gives way and releases a larger path.
  • a spring force of this overload protection 88 is therefore selected to be greater than the sum of the forces from the spring elements 81.
  • the stop 79 in the illustrated embodiment is designed as a wedge 79 movable transversely to the direction of adjustment S, the position of the respectively effective stop face 83 varying along the direction of adjustment S when the latter is moved.
  • the wedge 79 is supported for example on a carrier-fixed stop 96.
  • an actuator 84 for example, a druckstoffbetätigbares adjusting means 84 such as a pressure medium actuated piston 84 in a working cylinder with (double-acting) piston via a z. B. designed as a piston rod 85 transmission member 85 or by an electric motor via a designed as a threaded spindle transmission member 85, movable.
  • This actuator 84 can either be effective in both directions or, as shown here, be designed as a one-way reactor, which operates against a return spring 86 when activated.
  • the force of the return spring 86 is from o.g. Reasons (largely force-free stop 79) chosen so weak that the wedge 79 is held only against gravity or vibration forces in its correct position.
  • the stop 79 can also be provided in other ways (eg, as the direction of adjustment S adjustable and fixable plunger, etc.) be executed in such a way that it forms a variable in the adjustment direction S, and - at least during the adjustment process - fixable stop surface 83 for the movement of the bearing block 74 in the direction of pressure point.
  • a setting of the stopper 79 for example, directly parallel to the direction of adjustment S by a drive means, for example, a pressure medium actuated cylinder with (double-acting) piston or an electric motor.
  • the particular for driving a rotary body 05; 06; 07 in particular a cylinder 05; 06; 07, ie the satellite cylinder 05, the forme cylinder 06 and the anilox rollers 07 of the flexographic printing machine used 121, which may in particular each be a angular position-controlled electric motor 121, preferably a synchronous motor 121 and / or a drive motor 121 with permanent magnet excitation.
  • Fig. 6 shows an embodiment of a drive by means of a synchronous motor 121 and / or as a permanent magnet excited motor 121 formed drive motor 121 with a rotor (rotor) 266.
  • the synchronous motor 121 is z. B. formed as field weakenable synchronous motor 121.
  • the field weakening of the synchronous motor 121 is provided, for example, up to a ratio of 1:10. He points z. B. six poles and has an electrical stimulation.
  • the motor 121 which is embodied as a synchronous motor 121 and / or permanently excited motor 121, preferably has a permanent excitation, ie it is designed to be excited by a permanent magnet.
  • the rotor 266 or rotor 266 of the synchronous motor 121 has poles of permanent magnets 267. He points z.
  • a steady state torque in the range of 100 Nm to 200 Nm.
  • the synchronous motor 121 has a maximum torque in the range of 600 to 800 Nm, especially about 700 Nm, on.
  • the permanent magnets 267 preferably have rare earth materials.
  • the trained as a synchronous motor 121 and / or permanent-magnet motor 121 engine 121 has z.
  • the motor 121 formed as a synchronous motor 121 and / or permanent-magnet motor 121 is z.
  • a rotational angle sensor 274 is provided on the motor 121 formed as a synchronous motor 121 and / or a permanent-magnet motor 121.
  • a cooling device in particular a fan wheel or a liquid coolant circuit, is provided on the motor 121 designed as a synchronous motor 121 and / or permanent-magnet motor 121.
  • a braking device may be provided on the motor 121 formed as a synchronous motor 121 and / or permanent-magnet motor 121.
  • the motor 121 is also used in generator mode as a braking device.
  • a rotation axis of a rotation angle sensor 274 may be disposed coaxially with the rotation axis of the rotor 266 of the motor 121.
  • the stator 269 has windings 268 for generating magnetic fields by electric energy.
  • Fig. 7 shows an embodiment of the drive of a roller or a cylinder 06; 07, in particular a forme cylinder 06 or an anilox roller 07, with bearing unit 14 with a drive motor 121 designed as a synchronous motor 121 and / or permanent-magnet motor 121, ie with a section of permanent magnets formed on the rotor 266.
  • the stator 269 is in this case, for example, directly on the movable part of the storage unit 14, z. B. attached to the movable bearing block 74 and movable together with this.
  • a guide 271 may be provided, on which the motor 121 slides.
  • the drive motor 121 is to the rotary drive as an external rotor motor, in particular also with permanent magnets 267 on now outer rotor 266, formed (Fig. 8).
  • the rotor 266 is now z. B. with the jacket body of the cylinder 06; 07 connected or formed by this.
  • the windings 268 of the stator 269 are powered by electrical leads 272, for example.
  • the rotation angle sensor 274 can in principle at different points rotationally fixed to the cylinder 06; 07 and / or the rotor 266, z. B. also on the other end face of the cylinder 06; 07, and has z. B. a signal line 276 for drive control. In the example it is connected to the rotor 266.
  • Stator 269 and rotor 266 are supported on bearings 277, here radial bearings 277, each other.
  • bearings 277 here radial bearings 277, each other.
  • the stator 269 is rotatably connected to the bearing block 74 and linearly movable together with this.
  • FIG. 9 shows an advantageous variant, wherein, in particular in the case of a cylinder 06 designed as a forme cylinder 06, an axial movement by the drive motor 121 should also take place.
  • the rotor 266 has a section otherwise occupied by permanent magnets 278.
  • the poles of the permanent magnets 278 alternate here, for example, in the axial direction.
  • z. B the poles in the provided for the rotary drive portion of permanent magnets 267 z. B. in the circumferential direction (also in Fig. 8).
  • the section of permanent magnets 278 provided for the axial movement is arranged opposite to the windings 268 different windings 279 which are connected via their own signal lines 281 of FIG a machine control forth for the purpose of page register setting are controlled.
  • the bearings 277 are formed here, for example, as an axial relative movement enabling roller bearing 277.
  • Fig. 10 shows an advantageous variant, wherein the cylinder 06; 07 in the region of its lateral surface or slightly below the permanent magnets 267 in the circumferential direction.
  • the windings 268 having stator 269 is fixed to the frame outside the cylinder 06; 07 (or a roller), but within the two side frames 12; 11 arranged.
  • the stator 269 carrying the windings 268 can in this case be around the entire circumference of the cylinder 06; 07 range or only over an angular segment (Fig. 10, bottom).
  • the permanent magnets 267 can also on a pin 63; 64 or a frontal taper of the cylinder 06; 07 be arranged.
  • FIG 11 shows a schematic side view of a forme cylinder 06 with a linear bearing 15, as has already been described with regard to its basic structure in connection with FIGS. 3 to 5.
  • the stop 79 designed here as a stop wedge 79 is here drivingly connected to a servomotor 33 and the position of the stop wedge 79 can by means of a co-operating with the actuator 33 sensor 32, z. B. a potentiometer 32 can be monitored or controlled.
  • each of the forme cylinders 06, each anilox roller 07 and each chambered doctor blade 08 is assigned its own linear bearing 15 of the type explained above and at least the satellite cylinders 05, the forme cylinders 06 and the anilox rollers 07 each have a drive motor 121 of the type explained above.
  • each forme cylinder 06 to the associated satellite cylinder 05 is fine adjustable adjustable
  • each anilox roller 07 is about their Linear bearing 15 to the associated forme cylinder 06 finely adjustable adjustable
  • each chamber doctor blade 08 is preferably adjustable in pressure via its linear bearing 15 to its associated anilox roller 07.
  • the arrangement of the forme cylinder 06 on the circumference of the respective satellite cylinder 05 is such that between each contact line which forms the forme cylinder 06 with the satellite cylinder 05, the same distance, or, in other words, the forme cylinder 06 are equidistant on the circumference of the satellite cylinder 05th distributed.
  • the form cylinder 06 are, as in the case of the embodiment of Figure 1, with respect to the respective satellite cylinder 05 arranged so that in each case two forme cylinder 06 are diametrically opposed; in other words, the axes of rotation of satellite cylinder 05 and two associated therewith form cylinders 06 lie on a common line.
  • the anilox rollers 07 are each arranged relative to the forme cylinders 06 such that the axis of rotation of an anilox roller 07, the axis of rotation of the associated forme cylinder 06 and the axis of rotation of the associated satellite cylinder 05 lie on a common straight line. This ensures that at a delivery of the forme cylinder 06 to the satellite cylinder 05 due to the selected position of the cylinder 05; 06 to each other, the anilox roller 07 can now be moved synchronously with the same feed value as the forme cylinder 06, so that the set between the anilox roller 07 and forme cylinder 06 pressure bias does not change.
  • Fig. 12 shows a plan view of a mechanical coupling of the linear bearing 15 of the chambered doctor blade 08 with the linear bearing 15 of the anilox roller 07 in the salaried state of the chambered doctor blade 08 to the anilox roller 07, while Fig. 13 shows the parked state.
  • the anilox roller 07 is with its pin 64 in the linear bearing 15, d. H. mounted in the carriage 74 of the linear bearing 15, which in turn is longitudinally displaceably guided on the linear guide 16 of the linear bearing 15 of the anilox roller 07.
  • the chambered doctor blade 08 is connected via a cross member 17 attached to it and a holder 18 in a linear bearing 15, d. H.
  • the carriage 74 of the linear bearing 15 of the chambered doctor blade 08 is connected to the carriage 74 of the linear bearing 15 of the anilox roller 07 variable in distance, which can be designed as follows:
  • An actuator 19 which may in particular be pressure-medium-actuated and in the case of the embodiment may comprise a force-controlled cylinder-piston device 19 is between chambered blade 08 and between the carriage 74 of the linear bearing 15 of the chambered doctor blade 08 and the carriage 74 of the linear bearing 15 of the anilox roller 07 effective.
  • a cylinder 21, to which a working fluid can be supplied is connected to the chambered doctor blade 08 or its carriage 74, and a piston 22 displaceably guided in the cylinder 21 is connected via its piston rod 23 to the carriage 74 of the anilox roller 07.
  • the chambered doctor blade 08 is biased in its parked position, see.
  • the chamber doctor blade 08 By supplying working fluid into the cylinder 21, the chamber doctor blade 08 is set at the desired pressure against the anilox roller 07 against the pressure of the return spring 24, cf. Fig. 12. Due to the combination of anilox roller 07 and chamber doctor blade 08 by means of the actuator 19, the chamber doctor blade 08 follows every movement of the anilox roller 07 inevitably, namely without the contact pressure between chamber doctor blade 08 and anilox roller 07 would change. Due to the coupling thus the pressure-controlled pressure-on position of the chambered doctor blade 08 is maintained.
  • FIG. 14 and 15 show in a representation corresponding to that of FIG. 11, the coupling between anilox roller 07 and chamber doctor blade 08 in a view perpendicular to that shown in FIG. 12 or FIG. 13.
  • Anilox roller 07 parked chambered scraper 08 pivoted from its functional position to prepare a knife change.
  • a linear bearing 15 is preferably the forme cylinder 06 without pressure plates 27 or with pressure plates 27, z. B flexographic printing plates 27 occupied with a defined thickness.
  • the stop wedge 79 of the linear bearing 70 is retracted and the linear bearing 70 is against suitable attacks such. B. lateral surface of the impression cylinder 05 or measuring rings or frame-fixed stops z. B. hydraulically employed.
  • this zero position of the stop wedge 79 is retracted and it is preferably a feedback of the position of the stop wedge 79 and / or his associated drive (electric motor 121) to a control device. From this zero position of the stop wedge 79 and thus of the forme cylinder 06 and / or anilox roller 07, the stop wedge 79 is retracted again a predetermined path, whereby the contact pressure when setting the cylinder 06 and the anilox roller 07 is set.
  • FIG. 16 shows a schematic view of a cylinder group consisting of satellite cylinder 05, forme cylinder 06 and anilox roller 07.
  • the forme cylinder 06 has on its circumference a pressure plate 27, which comprises a carrier material 28 and the print image 29. At the end faces of the forme cylinder 06 measuring rings 31 are attached.
  • both the forme cylinder 06 and the anilox roller 07 are each mounted in a linear bearing 15 of the type described above.
  • the stop wedge 79 of the respective linear bearing 15 is adjustable by means of a servomotor 33 and the position of the stop wedge 79 can be monitored by means of a servomotor 33 associated potentiometer 32.
  • the stop wedge 79 of the linear bearing 15 of the forme cylinder 06 is initially extended until the potentiometer 32 on the servomotor 33 has reached the maximum value. Subsequently, the forme cylinder 06 is displaced toward the satellite cylinder 05 via the hydraulic pistons 82 (see FIG. 4) until the measuring rings 31, which are arranged on the end faces of the forme cylinder 06, bear against the lateral surface of the satellite cylinder 05 (FIGS ).
  • the outer diameter of the measuring rings 31 are designed so that they slightly surmount the carrier material 28 of the printing plate 27, but still the actual diameter, which is formed by the surface of the printed image 29, fall below.
  • the form cylinder channel 34 is intended here to point to the center of the satellite cylinder 05.
  • the adjustment is possible with or without applied pressure plates 27.
  • FIG. 17 This state is shown in FIG. 17.
  • the measuring rings 31 of the forme cylinder 06 are set against the lateral surface of the satellite cylinder 05 and the forme cylinder channel 34 is aligned with the center of the satellite cylinder 05.
  • the structure of the measuring rings 31 to the carrier material 28 and the print image 29 of the pressure plate 27 can be seen.
  • the hydraulic piston 82 is acted upon by a maximum pressure p max and then the stop wedge 79 is driven via the servomotor 33 into the gap.
  • the end position of the stop wedge 79 is indicated by the increased to maximum current consumption of the servomotor 33.
  • the servomotor 33 is switched off, the pressure on the hydraulic piston 82 is set to a lower pressure p 1 .
  • the pressure p max must produce a higher setting force than the force F n generated by the entering stop wedge 79, which is dependent on the torque of the servomotor 33.
  • the pressure p 1 generates a lower contact force than the motor torque can generate on the stop wedge 79, but is also so large that a secure fixation of the forme cylinder 06 is ensured during the printing process.
  • the stop wedge 79 is moved by the servo motor 33 by a predetermined distance x in the gap to turn off the forme cylinder 06 from the satellite cylinder 05 so far that the gap required for printing is reached. As a rule, then the printed image 29 is on the paper with a slight bias.
  • the position of the stop wedge 79 is always indexed via the potentiometer 32 on the servo motor 33. Process-related changes in the gap can be realized by adjusting the stop wedge 79, wherein the pressurized hydraulic piston 82 always clamp the carriage 74 of the linear bearing 70 against the stop key 79.
  • the anilox roller 07 is moved with fully extended stop key 79 to the forme cylinder 06 until the measuring rings 31, which are arranged on the end faces of the forme cylinder 06, abut against the lateral surface of the anilox roller 07.
  • the form cylinder channel 34 must point to the anilox center.
  • the hydraulic piston 82 of the linear bearing 70 of the anilox roller 07 are acted upon by a maximum pressure p max and then driven the stop key 79 via the servo motor 33 in the gap.
  • the end position of the stop wedge 79 is indicated by the maximum current consumption of the servomotor 33.
  • the servomotor 33 is switched off, the pressure on the hydraulic piston 82 is set to a lower pressure p 1 .
  • the stop key 79 is moved by the servo motor 33 by a predetermined distance y in the gap to the form cylinder 06 of the anilox roller 07 so far off that the necessary gap for printing is achieved.
  • FIG. 18 shows the forme cylinder 06 set relative to the satellite cylinder 05 after setting the gap required for printing, while the lower detail view shows the delivery of the anilox roller 07 to the measuring rings 31 of the forme cylinder 06, the forme cylinder channel 34 facing the axis of FIG Anilox roller 07 is aligned.
  • the first guide roller 26, with which the printed paper web 02 comes into contact after printing is arranged so that the freshly printed paper side does not come into contact with the surface of the guide roller 26.
  • one or more drying devices 25.1; 25.2 or dryer 25.1; 25.2 provided for drying the freshly printed paper web 02.
  • At least one of these dryers 25.1; 25.2, in Fig. 2, at least the dryer 25.2, is arranged so that the waste heat of the dryer 25.2 the overlying paper web 02 dries again.
  • the paper web 02 is guided so that it just above a dryer 25.2, the one running below the dryer 25.2 Paper web 02 dries, runs. In this way, the time required for drying path or the time required for drying is shortened or the energy of the dryer 25.2 used particularly well.
  • FIG. 19 shows a modification of the satellite printing unit 03 shown in FIG. 2.
  • the linear guides 16 of the linear bearings 15 of chamber doctor blade 08, anilox roller 07 and forme cylinder 06 of each printing unit 04 are parallel, in the case of the embodiment in particular on a horizontal, so that the channel beats between form cylinder 06 and anilox roller 07 can not act on the linear guides 16.
  • all the carriage 74 of the linear bearings 15 of a printing unit 04 can lie in common linear guides 16.
  • the anilox roller 07 can be moved synchronously with the same feed value as the forme cylinder 06, so that the pressure bias between the anilox roller 07 and forme cylinder 06 does not change.
  • Fig. 20 shows a modification of the satellite printing unit 03 shown in Fig. 19, wherein the linear guides 16 of the two lower forme cylinder 06 and anilox rollers 07 are arranged vertically to improve the operability of the printing unit 03 for disk laying.
  • the anilox roller 07 With a delivery of the forme cylinder 06 to the satellite cylinder 05 can due to the selected position of the cylinder 05; 06; 07 to each other, the anilox roller 07 are moved synchronously with the same feed value as the forme cylinder 06, so that the pressure bias between the anilox roller 07 and forme cylinder 06 does not change.
  • the linear bearing 15 of the chambered doctor blade 08 and its linear guide 16 is not fixed here in the side frame 11 and 12 of the printing unit 03, but on a separate support member 36 which may be formed as an angled plate 36 and non-positively the carriage 74 of the anilox roller 07 is connected, so that the pressure-on position of the chambered doctor blade 08 to the anilox roller 07 is independent of the movement of the anilox roller 07, cf. Fig. 21.
  • a satellite printing unit 03 provided with at least eight cylinders 06, wherein the forme cylinder 06 pairs may have different diameters and / or each two form cylinders 06 each associated with only one common anilox roller 07.
  • a satellite printing unit 03 with eight forme cylinders 06 is shown, wherein in each case two forme cylinders 06 are assigned in pairs only one anilox roller 07 and both forme cylinders 06 of a cylinder pair can have different diameters or can have the same diameter for the purpose of imprinter operation the anilox roller 07 can optionally be assigned to the larger or the smaller forme cylinder 06.
  • FIG. 23 shows, in the illustration corresponding to FIG. 11, a linear bearing 15 of a cylinder 07 or an anilox roller 07, which has two stop wedges 79.
  • a linear bearing 15 is also applicable in the case of the above-described embodiment of FIG. 22, in which the anilox roller 07 is movable between two forme cylinders 06.
  • anilox roller 07 is accordingly either alternatively or alternately between the one and the other stop 79.
  • a middle position of the anilox roller 07, in which it is in contact with neither of the two forme cylinder 06, z. B. achieved in that a stop wedge 79 is retracted completely into its associated gap, while at the same time the or the opposite hydraulic piston 82 (see, eg., Fig. 4) is pressurized or be.
  • the arrangement may in particular be such that the hydraulic pistons 82 are mechanically connected on both sides to the carriage 74 of the linear bearing 70 of the anilox roller 07.
  • the back of the hydraulic elements is formed as an inclined plane and forms with the associated stop wedge 79 an inclined plane.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)
EP20060115151 2005-06-17 2006-06-08 Méthode et procédé pour le réglage d'un cylindre ou d'un rouleau Withdrawn EP1733876A2 (fr)

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
DE102005028424 2005-06-17
DE102005032120 2005-07-07
DE102005039074 2005-08-18
DE102006003006.0A DE102006003006B4 (de) 2005-06-17 2006-01-23 Verfahren zum Einstellen einer Druck-An-Stellung

Publications (1)

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EP1733876A2 true EP1733876A2 (fr) 2006-12-20

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EP20060115151 Withdrawn EP1733876A2 (fr) 2005-06-17 2006-06-08 Méthode et procédé pour le réglage d'un cylindre ou d'un rouleau

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DE (1) DE102006003006B4 (fr)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009074295A1 (fr) * 2007-12-11 2009-06-18 Fischer & Krecke Gmbh Presse à imprimer équipée d'un capteur de cylindre

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE202007005402U1 (de) * 2007-04-13 2008-08-14 Aradex Ag Flexodruckmaschine

Citations (3)

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Publication number Priority date Publication date Assignee Title
WO2001049491A2 (fr) 1999-12-31 2001-07-12 Koenig & Bauer Aktiengesellschaft Procede et dispositifs pour regler un rouleau d'une machine a imprimer
WO2002081213A2 (fr) 2001-04-09 2002-10-17 Koenig & Bauer Aktiengesellschaft Groupe d'impression d'une machine d'imprimerie, procede pour abaisser et relever un cylindre, et procede de realisation d'un produit imprime
WO2003047864A2 (fr) 2001-11-28 2003-06-12 Koenig & Bauer Aktiengesellschaft Dispositif d'encrage d'un rouleau

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2001049491A2 (fr) 1999-12-31 2001-07-12 Koenig & Bauer Aktiengesellschaft Procede et dispositifs pour regler un rouleau d'une machine a imprimer
WO2002081213A2 (fr) 2001-04-09 2002-10-17 Koenig & Bauer Aktiengesellschaft Groupe d'impression d'une machine d'imprimerie, procede pour abaisser et relever un cylindre, et procede de realisation d'un produit imprime
WO2003047864A2 (fr) 2001-11-28 2003-06-12 Koenig & Bauer Aktiengesellschaft Dispositif d'encrage d'un rouleau

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009074295A1 (fr) * 2007-12-11 2009-06-18 Fischer & Krecke Gmbh Presse à imprimer équipée d'un capteur de cylindre
CN101888930B (zh) * 2007-12-11 2012-01-25 菲舍尔&克雷克有限公司 具有筒传感器的印刷机
US8464638B2 (en) 2007-12-11 2013-06-18 Bobst Bielefeld Gmbh Printing press with cylinder sensor

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DE102006003006B4 (de) 2014-01-23

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