EP1820643A2 - Procédé destiné à la réduction de vibrations - Google Patents

Procédé destiné à la réduction de vibrations Download PDF

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Publication number
EP1820643A2
EP1820643A2 EP07100903A EP07100903A EP1820643A2 EP 1820643 A2 EP1820643 A2 EP 1820643A2 EP 07100903 A EP07100903 A EP 07100903A EP 07100903 A EP07100903 A EP 07100903A EP 1820643 A2 EP1820643 A2 EP 1820643A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
bearing
actuator
pressure
force
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Withdrawn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
EP07100903A
Other languages
German (de)
English (en)
Other versions
EP1820643A3 (fr
Inventor
Fred Büttner
Bernd Masuch
Karl Schäfer
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
Original Assignee
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 EP1820643A2 publication Critical patent/EP1820643A2/fr
Publication of EP1820643A3 publication Critical patent/EP1820643A3/fr
Withdrawn legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/085—Cylinders with means for preventing or damping vibrations or shocks
    • 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

Definitions

  • the invention relates to a method for vibration reduction according to the preamble of claim 1.
  • the WO 03/064763 A1 discloses a method and apparatus for reducing vibration, acting on pins and / or bearings by means of actuators.
  • DE 196 52 769 A1 discloses a method for damping of contact vibrations, wherein acting on the bearing or the pin actuators are provided, which are operated for vibration damping via a control loop.
  • the EP 03 31 870 A2 discloses a device for supporting cylinders, wherein pins of a cylinder are mounted in two bearings arranged in the axial direction of the cylinder side by side. By means of pressure cylinders, the bearings can be moved individually perpendicular to the axis of rotation to compensate for example, a deflection.
  • a method for vibration damping of a cylinder of a printing machine wherein by means of an actuator of the vibration counteracting forces are applied, which are controlled in size and direction depending on the actually measured vibrations.
  • an adaptive counter-control can be used, wherein the repetitive deviation per revolution of the cylinder is measured and evaluated by a stationary, on the angular position of the cylinder associated algorithm, the respective remaining deviation and compensated for by the control of the actuator.
  • the WO 2004/085154 A1 discloses a cylinder with means for generating an internal voltage and a control unit, which controls the means in response to a measured vibration.
  • the invention has for its object to provide a method for vibration reduction.
  • the achievable with the present invention consist in particular that the required fast by the pilot control with a predefined force curve Reaction times and high dynamics is achievable.
  • a signal curve of the force impulse to be generated by the actuator which is adapted to the channel impact profile, only an adjustment of the signal level is necessary.
  • an actuator which is directed against the vibration is different from the actuator effecting an actuating movement
  • a printing machine, z. B. web-fed rotary printing press, in particular a multi-color web-fed rotary printing press, has a printing unit in which a material web, for. B. paper web, short web one or both sides can be printed.
  • the printing unit has a printing unit 01 with at least one on / Ab bainen cylinder 02; 03, here a double printing unit 01 for the two-sided printing in rubber-against-rubber operation, on (Fig. 1).
  • the double printing unit 01 - in the form of bridge or n-printing or even as a flat printing unit lying in a common plane axes of rotation - is here formed by two printing units 01, each one as a transfer cylinder 02 and a form of cylinder 03 formed cylinder 02; 03, z. B. printing cylinder 02; 03, and each having a not shown inking unit and in the case of wet offset printing additionally have a dampening unit.
  • a (double) pressure point is formed in Anstelllage.
  • the cylinders 02; 03 are each frontally on or in side frames 07; 08 rotatable stored. At least one of two a nip 05 forming cylinders 02; 03 has in the region of its lateral surface at least one axially extending channel 10 with a width b K. The juxtaposed cylinder 02; 03 form the nip 05 of a width b N. The rollover during operation causes channel beats, which in turn vibrations of the cylinder 02; Excite 03 (Fig. 2).
  • bearing arrangements (06; 42: s.u.) Given that allow advantageously counteracting these vibrations by one or more actuators targeted a force in the storage and / or journal is applied.
  • the bearing arrangements (06, 42: see above) can be used as bearing units (06, 42: see above), which contain as assembly both rotational bearings and the actuator (s).
  • a cylinder units 04 executed modules z. B. a cylinder 02; 03 with pin 09 and a pre-assembled on the pin 09 or preassembled (biased and / or preset) storage unit 06 on.
  • Storage unit 06 and cylinder 02; 03 get z. B. already before being inserted into the printing unit their firmly defined position to each other and are collectively introduced into the printing unit.
  • the bearing unit 06 may also be formed in the usual way, but contain an actuator for counteracting vibrations.
  • the cylinder 02; 03 in storage units 06 on side frames 07; 08 rotatably store, which the escape of the side frames 07; 08 not penetrate and / or the cylinder 02; 03 with its bale including its pin 09 a length L02; L03, which is less than or equal to a clear width LW between the printing cylinder 02; 03 to both end faces supporting side frames 07; 08.
  • FIGS. 3 and 4 show a bearing unit 06, preferably based on linear travel ranges, in longitudinal and cross-section.
  • the storage / retrieval mechanism or at least the transmission 11 integrating bearing unit 06 has in addition to a radial bearing 12, for example, a cylindrical roller bearing 12, for rotatably supporting the cylinder 02; 03 also storage means 13; 14 for a radial, in particular linear movement of the cylinder 02; 03 - to print on or print off - on.
  • the bearing unit 06 (after mounting the cylinder unit 04 frame-fixed) carrier-resistant bearing elements 13 and the movable against these bearing elements 14.
  • the carrier-fixed and movable bearing elements 13; 14 are as cooperating linear elements 13; 14 and formed together with corresponding sliding surfaces or rolling elements between them as a total of linear bearings 13, 14.
  • the linear elements 13; 14 take z. B. in pairs a radial bearing 12 receiving bearing block 16, z. B. slide 16 between them.
  • Bearing block 16 and the movable bearing elements 14 may also be made in one piece.
  • the carrier-fixed bearing elements 13 are arranged on a carrier 17, which in total with the respective side frame 07; 08 is connected or is.
  • the carrier 17 can be designed as a base plate or enclosure (circular, rectangular or other basic shape), for example, at least on a drive side a not shown recess 18 (corresponding to FIG.
  • the side frame 07; 08 on the drive side preferably has a recess 19, in particular as a slot, or an opening 19 for a drive shaft, not shown, with the pin 09 rotatably connected to.
  • a recess 18 nor a recess 19 must be provided on the opposite side of the drive side.
  • the advantageous arrangement of the two bearing block 16 encompassing linear bearings 13, 14 allows a backlash-free setting, as opposed to the two linear bearings 13, 14 in such a way that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 02; 03 learn or record.
  • the two linear bearings 13, 14 (in each case with bearing elements 13 and 14) are designed with respect to their direction of adjustment S in parallel with respect to.
  • the linear bearings 13, 14 are thus adjustable in the direction to which it is at play-free positions of the cylinder 02; 03 also arrives.
  • the frame-fixed bearing elements 13 are arranged substantially parallel to each other and define a direction of adjustment S.
  • non-penetration and the above definition with respect to the inside width LW should be understood in a broader sense to mean that, at least in the region of the intended end position, the cylinder 02; 03 and at least on a continuous path from a side frame edge to the location of the end position such a “non-penetration” is present, so that the cylinder unit 04 from an open, between the two end-side side frames 07; 08 lying side without tilting, ie brought in a position with the side frame plane perpendicular axis of rotation to the end position and there are arranged between the two side frame inner walls, in particular attached to the side frame inner walls can.
  • This is z.
  • the effective inner surface of the radial bearing 12 and the outer effective lateral surface of the pin 09 can be made cylindrical instead of conical, since both the assembly of Bearing unit 06 on the pin 09 and the setting of the bearing clearance can still be done outside the printing unit.
  • a cylindrical shaft seat between pin 09 and radial bearing 12 is provided.
  • the bearing unit 06 or the radial bearing 12 can be shrunk, for example, and the assembly of the preassembled cylinder unit 04 complete with storage in the side frame 07; 08 done.
  • the bearing preload is achieved here by the fit of shaft seat roller bearing inner ring, and does not need during assembly of the cylinder 02; 03 can be set in the printing unit (time saved in the assembly).
  • the bearing unit 06 in particular linear bearing unit 06, thus has the movable part as the linearly movable carriage 16 (guide slide), which receives the radial bearing 12 and possibly a thrust bearing (eg., For side register adjustment of the cylinder 03), and a degree of freedom has perpendicular to the cylinder axis.
  • the fixed part (carrier 17 with bearing elements 13) of the bearing unit 06 is on the side frame inside of the side frame 07; 08 attached, z. B. screwed.
  • a - in particular backlash-free or biased - gear 11 is integrated, which transforms a introduced from outside the storage unit 06 on a member of the transmission 11 adjusting movement in a linear movement of the carriage 16.
  • a trained gear 11 is integrated, which is the rotational movement of a merely schematically indicated adjusting 21 (adjusting means 21) via, for example, a shaft 22 in a linear movement of the carriage 16 perpendicular to the shaft 22 and axis Adjusting drive 21 and / or perpendicular to the cylinder axis converts.
  • This gear 11 may include, for example, a driven by the shaft 22 rotating gear, which cooperates with a the movable part associated rack.
  • the adjusting drive 21 is preferably designed as a rotary drive (manually or preferably as an electric motor, in particular remote-controlled). This is advantageous on the Rear side of the storage unit 06, in particular on the side facing away from the storage unit 06 side of the side frame 07; 08 (mounting surface to the side frame) arranged, z. B. flanged.
  • the axis of rotation of the adjusting drive 21 preferably extends substantially parallel, but offset from the cylinder axis.
  • Rotary actuator 21 (ideally stepper motor 21 for synchronization between the two frontal side frames 07; 08, matching gear (ideally as a planetary gear mounted upstream of the actuator 21), bevel gear (self-locking worm gear as shown in FIGS. 3 and 5, as axes drive motor and linear travel orthogonal ), Transfer gear rotatory - linear (preloaded and thus backlash ball screw as shown in Fig. 3 and 5).
  • a force measurement in particular for the radial force in the adjustment, integrated as part of the storage or the drive by, for example, the current consumption of the actuating means 21, z.
  • z. B. the torsional moment of the spindle, etc. is determined and evaluated.
  • a printing unit with at least three cylinders 02 acting together as a printing unit 01; 03 (for example with impression cylinder) are at least two of the three Cylinder 02; 03 in such linear bearings 13, 14 are each movably mounted along a direction of adjustment S, which with one of the axes of rotation of the cylinder to be positioned and following in the adjusting direction 02; 03 formed connecting plane at most forms an angle of 15 °.
  • the movable cylinder 02; 03 is then in each case only in this cylinder 02; 03 associated bearing units 06 described above stored.
  • the linearly movable cylinders 02; 03 preferably preassembled with each end bearing units 06 as a cylinder unit 04 or preassembled.
  • these cylinders 02; 03 as a unit with bales and two end pins 09, z. B. an o. G. maximum length L02; L03 on.
  • a printing unit 01 embodied as a double printing unit 01, preferably at least the two forme cylinders 03 and at least one of the two transfer cylinders 02 are mounted so as to be linearly movable.
  • the second transfer cylinder 02 can be operationally fixed to the frame, but in particular adjustable in its position, be stored. However, in one variant, all four cylinders 02; 03 be mounted so linearly movable.
  • a three-cylinder printing unit 01 for the single-sided printing are at least two, in particular at least the two ink-carrying, cylinder 03; 02, z. B. Form and transfer cylinder 03; 02, in one variant, however, all three cylinders 03; 02 mounted so linearly movable.
  • the bearing 06 at least one actuator 23, z. B. piezoelectric actuator 23, by means of which a force is allowed in the bearing contact point.
  • the actuators 23 in the above-mentioned linear bearing unit 06.
  • two load cells at an angle not equal to zero, preferably by 90 ° or 120 °, with respect to a Circumferentially spaced, provided. If only one actuator 23 per bearing unit 06 is provided, then only one sensor can be provided.
  • a possible embodiment represent piezoelectric sensors, in an advantageous version simultaneously usable as an actuator 23.
  • the printing unit 01 are to enable resultant directions of force in each direction of the sheet plane of Fig. 4, two actuators 23 and at least one spring element 24, designed here as a disc spring package required.
  • the spring element 24 is preferably arranged substantially opposite the actuators 23.
  • two spring elements 24 are provided for the provision as an abutment to the actuators 23.
  • the piezoelectric actuator 23 preferably has a stiffness of z. B. at least 400,000 N / mm, preferably at least 500,000 N / mm, z. B. about 600,000 N / mm.
  • the spring element 24 has z. B. a rigidity of at least 2,500 N / mm, in particular at least 3,000 N / mm.
  • the two actuators 23 are z. B. in each case by an angle ⁇ , z. B. greater than 20 °, in particular between 20 ° and 45 °, for example. about 30 ° inclined to the defined by the direction S straight line.
  • actuator 21 for the on / off movement on the one hand (actuator 21 designed as actuator 21) and for the vibration compensation (actuator 23); 23 provided.
  • the actuators 23 are available for control with a control and / or control device 57, z. B. a schematically shown in Fig. 12 by dashed lines adaptive controller 57, in signal communication.
  • FIGS. 6 and 7 show a second advantageous bearing unit 06 based on linear travel paths in longitudinal and cross-section.
  • the bearing unit 06 which integrates the on / off mechanism, has a cylindrical bearing 02 for rotational support.
  • 03 bearing means 13, 14 for a radial movement of the cylinder 02; 03 - to print on or print off - on.
  • the bearing unit 06 (after mounting the bearing unit 06 frame-fixed) carrier-resistant bearing elements 13 as well as against these movable bearing elements 14.
  • the carrier-fixed and movable bearing elements 13; 14 are as cooperating linear elements 13; 14 and formed together with corresponding sliding surfaces or rolling elements between them as a total of linear bearings 13, 14.
  • the linear elements 13; 14 take in pairs a radial bearing 12 receiving bearing block 16, z. B. slide 16 between them. Bearing block 16 and the movable bearing elements 14 may also be made in one piece.
  • the carrier-fixed bearing elements 13 are arranged on a carrier 17, which in total with the side frame 07; 08 is connected or is.
  • the support 17 is embodied, for example, as a support plate 17 which, for example, has at least one drive side a recess 18 for the passage of a drive shaft 20 shown in dashed lines in a pin 09 of the cylinder 02, not shown in FIG. 03 has.
  • the side frame 07; 08 on the drive side preferably has a recess 19 or an opening 19 for a drive shaft 20. On the drive side opposite end face neither a recess 18 nor a recess 19 must be provided (Fig. 6).
  • the advantageous arrangement of the two bearing block 16 encompassing linear bearings 13, 14 allows a backlash-free setting, as opposed to the two linear bearings 13, 14 in such a way that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 02; 03 learn or record.
  • the bearings are thus adjustable in the direction to which it is at play-free positions of the cylinder 02; 03 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 02; 03 and at least on a continuous path from a side frame edge to the location of the end position such a "non-penetration" is present, so that the cylinder unit 04 from an open, between the two end-side side frames 07; 08 lying side without tilting, d. H.
  • the bearing units 06 are in the manner on the inner walls of the side frames 07; 08 arranged that the cylinder 02; 03, in particular their bearing units 06 on the cylinder 02; 03 side facing by the side frame 07; 08, which offers static and mounting advantages.
  • corresponding means 28, e.g. B. clamping screws 28 may be provided (Fig. 6).
  • the bearing unit 06 - at least to the cylinder side - protected by a cover 29 largely against contamination or even encapsulated executed as a unit.
  • Fig. 6 is schematically the cylinder 02; 03 marked with pin 09 and a preassembled storage unit 06.
  • This module can thus be preassembled between the side frames 07; 08 of the printing unit used assembly-friendly and attached to designated locations.
  • the bearing units 06 for forming and transfer cylinders 03; 02- if applicable, except for the permitted operational size of the travel - identical design.
  • the effective inner surface of the radial bearing 12 and the outer effective lateral surface of the pin 09 can be cylindrical instead of tapered, since both the assembly of the bearing unit 06 on the pin 09 and the adjustment of the bearing clearance can be done outside the printing unit.
  • the storage unit 06 can be shrunk, for example.
  • the frame-fixed bearing elements 13 are arranged substantially parallel to one another and define a positioning direction S (FIG. 7).
  • a pressure is applied by moving the bearing block 16 in the direction of the pressure point by means of a force F applied to the bearing block 16 by at least one actuator 31, in particular by a force-controlled or force-defined actuator 31, by means of which a defined or predetermined position is used for the adjustment .
  • definable force F in print-on direction on the bearing block 16 can be brought (Fig. 7).
  • the decisive for the color transfer and thus the print quality, inter alia, line force in the nipples 05 is therefore not by a travel, but by the force equilibrium between the force F and between the cylinders 02; 03 resulting line force F L and the resulting equilibrium defined.
  • cylinder 02; 03 employed in pairs to each other by the bearing block 16 is acted upon by the corresponding set force F via the / the actuator (s) 31.
  • cylinder 02; 03 employed in pairs to each other by the bearing block 16 is acted upon by the corresponding set force F via the / the actuator (s) 31.
  • bearing block 16 even during operation - at least in one direction away from the pressure point against a force, eg. B. spring force, in particular a definable force, is movably mounted.
  • a force eg. B. spring force, in particular a definable force
  • This will - in Contrary to the pure travel limit - on the one hand a maximum line force when working together cylinder 02; 03 defined, and on the other hand, a yield, for example, in a web break with subsequent winder on the cylinder 02; 03, allows.
  • the storage unit 06 - At a pressure point facing side, the storage unit 06 - at least during the adjustment - a movable stop 39, which limits the travel along the direction of adjustment S to the pressure point out.
  • the stop 39 can be moved in such a way that the stop surface 33, which acts as a stop, can be varied along the direction of adjustment S at least in one region.
  • an adjusting device adjustable stop
  • the placement of the stop 39 can in principle be done manually or by means of an actuator 34 (see below).
  • a holding or clamping means not shown in FIGS.
  • the applied force F, the restoring force F R and the position of the stop 39 is selected such that no significant force ⁇ F is transmitted between the stop 39 and the abutment surface 33 of the bearing block 16 in the set position.
  • the contact force between the cylinders 02; 03 substantially determined by the voltage applied by the actuator 31 force F.
  • the decisive for the color transfer and thus the print quality, inter alia, line force in the nipples 05 is therefore not primarily defined by a travel, but at quasi-free stop 39 by the force F and the resulting balance. Basically, after finding the basic setting with the appropriate forces F, a removal of the stop 39 or a corresponding fixation, which is effective only during the basic setting, would be conceivable.
  • the actuator 31 can basically be embodied as any desired actuator 31 applying a defined force F.
  • the actuator 31 is designed as actuatable by pressure means actuating means 31, in particular as a piston 31 movable by a fluid.
  • Advantageous with regard to possible tilting is the arrangement of several, here two, such actuators 31.
  • As fluid is preferably because of their incompressibility, a liquid, eg. As oil or water, used.
  • a controllable valve 37 is provided in the bearing unit 06. This is performed, for example, electronically controlled and provides the hydraulic piston 31 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 present.
  • a non-designated leakage line is provided here for safety.
  • a portable, force-limited stop 38 as overload protection 38, z. B.
  • spring element 38 may be provided, which in the operational pressure-Ab, ie the piston 31 are relieved and / or retracted, although serve as a stop 38 for the bearing block 16 in pressure-off position, in the case of a railway winder or other excessive forces but gives way from the pressure point and releases a larger path.
  • a spring force of this overload protection 38 is therefore selected to be greater than the sum of the forces from the spring elements 36.
  • the stop 39 is in the illustrated embodiment (Fig. 7) designed as a transverse to the direction of adjustment S movable wedge 39, wherein the same moves the position of the respective effective stop surface 33 along the direction of adjustment S varies.
  • the wedge 39 is supported for example on a carrier-fixed stop 32.
  • the stop 39 embodied here as a wedge 39 is movable by an actuator 34, for example a pressure medium-actuatable actuating means 34 such as a piston 34 which can be actuated with pressure medium in a working cylinder with a (double-acting) piston or an electric motor via a threaded spindle.
  • This actuator 34 can either be effective in both directions or, as shown here, be designed as a one-way actuator, which operates against a return spring 41 when activated.
  • the force of the return spring 41 is from o. G. Reasons (largely force-free stop 39) chosen so weak that the wedge 39 is held only against gravity or vibration forces in its correct position.
  • the stop 39 can also be designed in a different way (eg, as a plunger adjustable and fixable to the setting direction S, etc.) in such a way that it has a stop surface 33 which can be fixed in the setting direction S and, at least during the setting process forms for the movement of the bearing block 16 in the direction of pressure point.
  • a location of the stop 39 is done for example directly parallel to the actuating direction S by a drive means, for example a cylinder which can be actuated with pressure medium with a (double-acting) piston or an electric motor.
  • the executed as a double printing unit 01 printing unit 01 of Figure 8 shows schematically per cylinder 02; 03, a bearing unit 06.
  • the centers of rotation of the cylinder 02; 03 an imaginary connecting line or plane E (hereinafter referred to as "linear double printing").
  • the plane E and the incoming or outgoing web preferably enclose an interior angle of between 19 and 38 °, in particular from 80 to 41 °, deviating from 90 °.
  • the storage unit 06 of the transfer cylinder 02, in particular all cylinder 02; 03 are in the mounted state in the embodiment shown in Figure 8 on the side frame 07; 08 arranged such that their adjusting directions S - z. B.
  • a maximum angle of 15 ° includes, z. B. an acute angle of about 2 ° to 15 °, in particular 4 to 10 ° form together (not shown).
  • this arrangement when the adjustment direction S is horizontal and the web is substantially vertical.
  • the adjustment direction S can also run parallel to the plane E.
  • the direction of the introduction of force through the channel impact (resulting main vibration level at Nipp bestory) in substantial proportions also the actuating or force direction of the actuators 31.
  • a counteracting the vibrations by the channel impact is in this embodiment with the same actuators 31 as the On / Off possible.
  • the same actuators 31 are thus provided for the on / off movement on the one hand and for the vibration compensation on the other hand.
  • Double printing unit 01 is to be understood as the plane E 'of the connecting plane of the cylinder forming the pressure point and level E "the connection plane between the forming and transfer cylinders 03, 02, and the above to the angle ⁇ on the direction of adjustment S at least one of the pressure point forming cylinders 02 and the forme cylinder 03 and the plane E 'and E "are related.
  • One of the pressure point forming cylinder 02 can also stationary and operationally inoperable (but possibly adjustable) in the side frame 07; 08 are arranged, while the other is mounted along the direction of adjustment S.
  • a control wherein the size of the signal or the force either depending on machine codes, etc. may be maintained or possibly can be determined adaptively.
  • This measurement signal can z. B. from a displacement or acceleration measurement on the bearing unit 06 (in particular on the bearing block 16 or pin 09) or as a pressure measurement in the hydraulic system for pressure medium supply of the pressure on / off position bewerkstellenden actuators 31 be.
  • the generation of these force pulses takes place by means of the actuators 31 effecting the pressure on / off position.
  • quick control valves are provided in the hydraulic system upstream of the actuators 31.
  • the actuators 31 and quick control valves are available for the modulation of the applied pressure with a higher than the contact pressure higher pressure to act on the signal / force pulse z. B. again with a control and / or control device 57 in conjunction.
  • z. B. piezoelectric actuators 40 may be provided, which also act on the bearing block 16. These can (dashed lines in Fig. 7 indicated) z. B. be integrated into the plunger of the pistons of the actuators 31.
  • the low-frequency positioning movements are performed by the actuators 31 performing the pressure on / off position and the high-frequency movements / force pulses counteracting the vibrations by other actuators 40 (or 23).
  • the additional piezo actuators 40 (or 23) are available for the modulation of the contact force z. B. again with a control and / or control device 57 in conjunction.
  • the solution specified in the second exemplary embodiment (FIGS. 6 to 8) (with or without additional piezoactuator 40) of the vibration damping can advantageously be used for vibration damping since the direction of the compressive forces between two cylinders 02; 03 and the direction of movement in the storage unit 06 are in line.
  • the feed movement does not take place in the same direction as the pressure forces.
  • the linear bearing (as in FIG. 3 to 5 or in Fig. 6 to 8), the feed movement is in the same direction as the pressure forces. This allows a force pulse which acts in the same direction as the glitch (channel beat) and causes a vibration damping.
  • Fig. 7 indicated variant of the second embodiment of the second embodiment (different drives for adjusting movement vibration compensation) of the actuators 23 having bearing block 16 of FIG. 4 (but without the actuator of FIGS. 3 and 5) in be driven by the actuators 31 with respect to the adjusting movement driven bearing assembly 06.
  • This z For example, as in FIGS. 6 to 8 by means of at least one actuator 31.
  • the one or more integrated in the bearing block 16 actuators 23 is shown in FIG. 7 by way of example indicated by dashed lines.
  • the arrangement mentioned for the arrangement of the actuators 23 for the first example is the same as that for the bearing arrangement 06 (omitting the actuator 40) of the second example.
  • a bearing assembly 42 for receiving the pin 09 of the cylinder 02; 03 as usual, on or in the side frame 07; 08 arranged radial bearing 42, z. B. executed as a multi-ring bearing 42.
  • the bearing assembly 42 may be designed as an eccentric bearing, wherein by pivoting an eccentric outer ring, the axis of the mounted cylinder 02; 03 is displaced in the radial direction. This is done for example by a drive, not shown, for. B. actuator for the on / off position, such as motor or pneumatic via appropriate transmission.
  • the bearing assembly 42 has at least one (in FIGS. 9 and 10 divided) ring 43, z. B.
  • eccentric intermediate ring 43 and at least one ring 46, z. B. inner ring 46, on, between which rolling elements 47 (or sliding surfaces) allow relative rotation.
  • the split intermediate ring 43 has z. B. a radially further outward, z. B. eccentric ring 48 and a ring 49 located further inside.
  • the eccentric ring 48 is for example via a Radial bearing 51, z. B. a sliding or needle bearing 51, pivotally mounted in an outer ring 52.
  • actuators 44 are arranged, which in the radial direction, a force between the rings 43; 46; 48; 49 exercise and can cause an associated (possibly infinitesimal small) relative movement.
  • the intermediate ring 43 is made in two parts and accommodates between the two rings 48 and 49 a plurality, but at least two, circumferentially spaced actuators 44, in particular piezoelectric elements 44.
  • These actuators 44 are for targeted application to a control and / or control device 57th in signal connection. This includes z. B. an algorithm which provides the actuator 44 a waveform.
  • At least two actuators 44 are arranged, of which z. B. one in the angular range of the here indicated only by the circled reference numeral 05 Nippstelle 05 (to the next cylinder 02, 03) and the other is opposite this.
  • pairs of opposing groups of actuators 44 may be arranged in a certain angular range around the nip point 05 and opposite. These pairs of opposing actuators 44 are then, for example, each opposite to each other acted upon to allow the movement of the inner ring 46 and the pin 09.
  • the arrangement of a plurality of mutually circumferentially mutually offset in the circumferential direction pairs of actuators 44 makes it possible to influence the vibration through the nip 05 "oscillation even in the range decaying vibrations by force pulses, as excited by the channel impact oscillation plane with the cylinder 02; 03 (in contrast to the intermediate ring 43) rotates.
  • actuators 44 and actuators 44 may be spaced apart in the axial direction of the bearing. This is depending on Triggering a bending moment on the bearing inner ring 46 and thus the pin 09 applicable.
  • the timing of the actuation of the actuators 44 for example, speed-dependent (see also below) and possibly in addition depending on parameters such as temperature and / or contact force of the cylinder 02; 03 and / or blanket behavior.
  • the control takes place in this case, for example, with respect to the time and possibly the waveform controlled correlated with the angular position of the relevant cylinder 02; 03, finding the optimal or sufficient signal level, however, may be subject to an adaptive control process (see below).
  • the actuation of the actuators 44 can take place with respect to their transitions (on or off) with parabolic, sinuinal or other higher-order functions.
  • a variant of the bearing assembly 42 of FIG. 9 is shown schematically, wherein z. B. in a Nippstelle 05 facing half space between the outer and inner ring 48; 49 lying gap over a larger angular range of z. B. 45 ° to a maximum of 90 ° reaching actuator 44 is arranged.
  • a plurality of actuators 44 may be arranged side by side between the inner and outer ring 48; 49 may be arranged.
  • intermediate spaces 55 should be provided in the circumferential direction between the actuators 44 attributable to the side (half space) of the nip point 05 and the opposite side, so that the inner ring 49 remains movable within certain limits in the direction of the nip point 05.
  • the actuators 44 attributable to the nip point 05 and attributable to the opposite side are again actuated in the opposite direction, as mentioned above.
  • a double bearing that is to say a double bearing, is provided for the aforementioned embodiments.
  • H each with two axially spaced bearings, used on each pin 09.
  • dynamic bearing each closer to the ball seated bearing in the manner of a bearing assembly 06; 42 with one of the vibration counteracting highly dynamic actuator 23; 31; 44 (hereinafter "dynamic bearing” 06, 42) executed, the more distant bearing, however, as a bearing assembly 53 without highly dynamic actuator 23; 31; 44 (hereinafter "fixed bearing” 53).
  • both types of bearings have a pressure on / off adjustment.
  • the fixed bearing 53 may, for example, except for the actuator 23; 31; 44 in the same way to the dynamic bearing 06; 42 be formed.
  • the dynamic bearing 06; 42 may in this case in the manner of one of the bearing units 06 described above; 42 be executed from Fig. 3 to 10.
  • the fixed bearing 53 may also be formed according to the bearing unit 06, but this quick control valves can be omitted.
  • the pin 09 between the two bearings or storage units 06; 42; 53 of a double bearing is advantageously made soft. Ie. the distance between the two bearings is large and / or the pin 09 is formed with a comparatively small diameter, so that upon radial movement by the actuator 23; 31; 44 no large additional forces caused by acting as a support bearing second bearing unit 53.
  • a thick, long pin 09 is advantageous over a short, thin pin 09, since the former has a greater torsional stiffness with the same flexural softness.
  • a gear 54 should be arranged on the pin 09 for its rotary drive, this is preferably arranged close to the bearing unit 53 lying further outward. Due to the proximity of the gear 54 to the "fixed" bearing 53, there is less torque input into the cylinder 02; 03 via the meshing of adjacent gears 54th
  • a static bending moment can be initiated to compensate for the cylinder bend.
  • This adjustment can be done in one embodiment by a static deflection of the actuator 23 (in particular piezoelectric actuator 23), which is superimposed on the dynamic deflection for vibration reduction.
  • the introduction of the static bending moment takes place by an adjustment of the bearing blocks 16 of the outer, in particular solid bearings 53 against the inner, in particular dynamic, bearings 06; 42nd
  • an expected force profile (dependent on time or angle of rotation) is determined.
  • F 0 ( ⁇ ) can be reproduced with sufficient accuracy for theoretical considerations.
  • An absolute height can be taken into account via a scaling factor K.
  • the function should preferably be differentiable once at least on its rising and falling edges and scalable by a factor.
  • the terms “fundamental”, “first harmonic”, “second harmonic”, etc. do not simply mean all modes (including the various modes of a “mode group") ascending to the frequencies.
  • the order in the sense designated here takes place according to fashion groups, d. H. with first, second, third harmonic is meant the first, second, third mode group.
  • fundamental vibration are thus to be understood those vibration modes in which the dynamic bending line of the individual cylinder between the bearing points is substantially mirror-symmetrical to the center of the bale and has no nodes of vibration on the bale.
  • the first harmonic is to be understood as meaning all vibration modes in which the dynamic bending line of the individual cylinders between the bearing points is substantially point-symmetrical with respect to the center of the bale and has exactly one vibration node on the bale.
  • the second harmonic is (all) those vibration modes in which the dynamic bending line of the individual cylinders between the bearings is substantially mirror-symmetrical to the center of the bale and has exactly two nodes of vibration on the bale.
  • the oscillation frequencies of the mode groups among one another are usually further separated from one another than the oscillation frequencies within a mode group.
  • Aktorkraft-time curve is now up to a height-determining scaling factor K from the o. G. Procedure (purely theoretical or by measurement) assumed channel impact force course given and maintained in a control and / or regulating device 57 or a force profile generator 59.
  • the control and / or regulating device 57 may include the force profile generator 59 in addition to corresponding storage and / or computing means.
  • Actuator-time curve can be understood here to mean the equivalent actuator-angular position curve, since these are directly related to one another via the machine speed.
  • the actuator 23; 31; 44 is preferably given a time course, which, however, is formed using the held Aktorkraft angular position course taking into account the machine speed or speed, etc.
  • an Aktorkraft-time curve or an Aktorkraft angular position curve is thus formed from this course and maintained as a function of the angle (discrete values of a table or as a mathematical function).
  • the actuators 23; 31; 44 now according to the predetermined Aktorkraft-time course (or Aktorkraft angular position course) driven.
  • This force-time profile is thus predetermined and, in contrast to a pure regulation (action only after a measured reaction out) obtains a pre-tax.
  • Goal of a z. B. subsequent adaptive control it may now be to find the optimal scaling factor K (signal level). It does not become a waveform or a time course generated by the control, but adapted only the height of the predetermined course.
  • the at the various actuators 23; 31; 44 of a cylinder 02; 03 introduced forces are for a given channel strike preferably always in the same relationship to each other. These ratios can be calculated from machine dynamic calculations of the system "printing unit with actuator" and then recorded.
  • the common prefactor, ie scaling factor K is determined by the iterative optimization so that the above-mentioned maximum amplitude becomes minimal.
  • the introduction of force preferably takes place only within the narrow time window of the channel rollover.
  • the predetermined actuator force-time course (or Aktorkraft angular position course) is selected accordingly.
  • the information about the state of rotation of the cylinder 02; 03 is z. B. by a rotational angle position detecting sensor 58, z. B. rotary encoder, received.
  • the duration of the channel rollover is thus detectable due to the structural conditions by a Kanalschlag gardenings- and Kanal juxtaposdwinkel.
  • the time of admission so controlled as a function of the angular position.
  • the vibration waveform of the cylinder vibrations is detected by the appropriate sensor 56 (see below) from a start angle> channel impact angle, for a given time period or up to a given sensor end angle (before the next channel impact occurs).
  • the signal obtained is analyzed for the magnitude of the vibrations present. This is advantageously done with a digital signal processing, the z. For example, the difference between successive extreme values is determined, and the result is the absolute value of the first of these differences, or the maximum of the absolute value of these values. This result will be referred to as the total amplitude below.
  • the method can be applied separately to any mode.
  • the two mainly existing mode amplitudes (eg A0 and A2) are measured or filtered and the o. Maximalamplitude calculated theoretically in any place of the cylinder 02; 03 results.
  • ⁇ K z. For example, set as follows:
  • the maximum mode amplitudes (calculated from the measured ones described above) of the successive steps are compared with each other.
  • the difference between the last and newly detected maximum amplitude is then decided whether a sign change of ⁇ K is required and the scaling factor K of the force introduction is changed to K + ⁇ K.
  • the time duration for the execution of an iteration step is advantageous in a cylinder rotation cycle. By choosing the size of ⁇ K, it is ensured that even with speed changes with typical accelerations of »40,000 rpm / min, the oscillation minimum can be kept continuous.
  • the bearing rigidity is reduced compared with conventional mounting (eg directly in the frame), so that a measurement of the movement in the region of the bearing arrangement 06; 42 is possible.
  • a measurement of the bearing forces eg via strain gauges (DMS) or via the actuator 23, 31, 44 itself
  • DMS strain gauges
  • the actuators 23 to be used for the active vibration damping; 31; 44 preferably have a very fast response time (response for one cycle> 100 Hz, especially> 300 Hz) and high rigidity.
  • the actuator 31 used there for short distances must have sufficiently fast reaction cycle times (second example).
  • actuators 23; 44 may instead of the mentioned piezo actuators 23; 44 in the aforementioned examples also designed as electromagnets actuators 23; 44 are used.
  • the size of the contact pressure or the contact force between two cylinders 02; 03 and / or between a distance defining attacks affects the rigidity of the system and thus the position and / or height of the resonant frequency.
  • the required for printing "static" Anstellkraft is usually suitably pre-selected and by means of the responsible for the pressure on / off position - z.
  • B. adjusting means 21, actuator 31 or the multi-ring bearing 42 makesdes adjusting means - set.
  • "static" setting-up force means that, unlike the above-described higher-frequency modulation, the setting force is left at a desired value over an extended period of time, ideally during the entire print job, but at least over several cylinder revolutions. This static contact force may be a dynamic share such.
  • the system properties can be influenced.
  • the cylinder movements for example cylinder vibrations due to the channel impact
  • the cylinder movements are formed in the hydraulic column of the pressure-actuable actuating means 31 and its supply system.
  • this change in the pressure of the hydraulic column is provided to detect this change in the pressure of the hydraulic column, to evaluate it metrologically, and to slightly exceed the static pressure P (hydraulic pressure) or its nominal value when a certain level (eg a limit or threshold value A G ) is exceeded until the vibration level falls again below the mentioned limit value A G of the level, however, this pressure P may not be lowered below the level necessary for the adjustment of the pressure
  • the hydraulic column can be evaluated both the pure amplitude curves and, for example, RMS values.
  • the pressure P for a longer period of time, for. B. be changed for at least more than one full cylinder revolution by a constant offset .DELTA.P.
  • the static contact pressure is then at the new level to z. B. by the evaluation of the measurement signals a renewed excess is detected.
  • the changed pressure P ' may be present, for example, in an angular position range which encloses the channel overrun in the nip position. If there are several nip passages per revolution (ie there are several, eg two, channels on the circumference of the cylinder in the circumferential direction), several, eg. B. two, angular ranges with a pressure P and several, z. B.
  • a sensor detecting the angular position for. B. on the cylinder 02; 03 or on the engine integrated angular position sensor to provide, which in a fixed angular relationship to the considered cylinder 02; 03 is.
  • Fig. 13 shows a schematic diagram of the method, wherein the cylinder 02; 03 on two bearing units 06 in side frames not shown to a second, not cylinder is stored off / off stored.
  • the bearing units 06 (42) an adjusting means 31; 21, in particular a pressure-medium actuable actuating means 31, on.
  • a force-displacement sensor eg., Strain gauges
  • an optical sensor e.g., a characterizing the vibration or the vibration amplitude determining magnitude A and the control and / or control device 62 is supplied.
  • a variable A determined by a pressure gauge 63 arranged in the hydraulic column and converted into electrical signals, characterizing the vibration or the vibration amplitude in the hydraulic column, is given to the control and / or control device 62.
  • Advantage of the detection of the size A via the hydraulic column is the detection of the relevant data, which is for the respective cylinder 02; 03 directly about its storage.
  • this variable A is now compared with a limit or threshold value A G stored in the regulating and / or control device 62.
  • the existing default value for the pressure P in general: a setpoint value P, P '
  • the pressure P is varied. This is done, for example, by adding or subtracting an offset ⁇ P, which z. B. has a fixed but adjustable step size.
  • a new pressure P 'of P + ⁇ P is formed in the control and / or control device 62 and an actuator 64, z.
  • a pressure control device 64 such as a remotely controllable pressure control valve 64 or adjustable pressure reducer 64, as a new setpoint.
  • the evaluation of the size A and / or the application of the pressure P 'different from the pressure P takes place only in the relevant angular position range including the channel rollover.
  • the control and / or control device 62 of an o.g. the angular position detecting sensor 58 provided the information about the angular position.
  • Fig. 14 is an embodiment of an interconnection of a pressure medium supply suitable for the implementation of o.g. Procedure presented.
  • the illustration is here for a possible embodiment, wherein for all the movable cylinder 02; 03 of a printing unit 01, in particular double printing unit 01, whose Anstelltik is determined by a common pressure level for the pressure P and the changed pressure P 'by a common supply.
  • a design may be particularly advantageous (but more complex), according to which the two forme cylinders 03 have a common supply system with its own pressure control valve 64 and the two transfer cylinders 02 have a supply system with a separate pressure control valve 64 separated therefrom.
  • the transfer cylinder 02 and the forme cylinder 03 can be independently brought out of their resonance frequency.
  • all cylinders 02; 03 of the printing unit 01 are brought independently of each other from its resonant frequency.
  • An outwardly open or closed fluid reservoir 67 is at a pressure level of a pressure P L (eg, ambient pressure) which is lower than a pressure corresponding to the restoring force F R of the spring members 36 of a bearing unit 06.
  • the Pressure medium (fluid) is passed through a compressor 68, z.
  • a pressure level P H or a pressure P H which corresponds to at least the pressure level P or pressure P required for the contact force F.
  • compressed fluid can advantageously be stored in a pressure accumulator 69 on the pressure P H.
  • a supply path 71 is depressed via the actuator 64, in particular the adjustable pressure reducer 64, the pressure level P of which through the pressure reducer 64 to the pressure level P suitable for the pressure on position and / or Pressure P (corresponding force F, possibly taking into account the restoring force F R and possibly force F) is set or adjustable.
  • the aggregates fluid reservoir 67, compressor 68, pressure accumulator 69 and adjustable pressure reducer 64 required for supplying the pressure medium are connected in dashed lines to form a supply system 72.
  • the valves 37 are arranged close to the cylinder outside of the supply system 72, but could also be integrated centrally in this.
  • the fluid reservoir 67 could also be commonly available outside of the supply system 72, centrally available to multiple supply systems 72.
  • control device 62 The setting and the above-described varying the default value for the pressure P of the pressure reducer 64 by the control and / or control device 62, in short: control device 62.
  • control device 62 Preferably, the adjustment via a signal line 73 remotely operated by the control device 62 ago.
  • three pressures P1, P2 and P3 are denoted by different levels or pressure levels P1, P2 and P3, which in an advantageous embodiment optionally by appropriate control of the pressure reducer 64 in the supply path 71 as Base pressure is available.
  • These pressure levels P1, P2 and P3 correspond to different power levels for the pressure on position for different printing conditions (eg different paper types and / or blanket properties).
  • valves 37 in particular multi-way valves, per ritaem cylinder 02; 03 are now connected to the supply line 71 of the pressure P (or P1, P2, P3).
  • P the pressure
  • P DS pressure point
  • the outputs of the valves 37 are, for. B. via a common return line 74, connected to the fluid reservoir 67.
  • the valves 37 are connected by a control device 76, z. B.
  • a two control devices 62 and 76 comprehensive common control device, adjustable The adjustment preferably takes place remotely actuated by the control device 76 via a signal line 77.
  • base values for the prints P can also be stored, which are possibly varied by the method as described above. In the second case, these are fed to the control device 62 and optionally varied by the method as described above.
  • an input of a valve 78 connected to the associated actuator 34 communicates with a supply path 79 different from the supply path 71, for example, depending on the configuration of the actuator 34 (acting double - acting in both directions or only in one of two possible directions) .
  • two outputs of the valve 78 are connected to one or two inputs of the actuator 34.
  • the valves 78 are preferably by a control device, for. B. by means of the control device 76 adjustable.
  • the setting is also remote-controlled by the control device 76 via a signal line 80.
  • an actuatable holding means 81 for example a plunger, is also provided for fixing the stop 39, by means of which the stop 39 can be held in its essentially force-free position without being relieved of pressure-off to change its position.
  • this holding means 81 may be connected for the purpose of actuation or release via corresponding lines and other valves 82 to the pneumatic supply path 79, and advantageously provided by the control device 76.
  • the holding means 81 is designed to selectively clamp the stopper 39 (when activated) with respect to the bearing block 16.
  • control and / or control device 62 itself or in the control device 76 may also contain information on critical speeds of the printing unit 01 and an instruction for handling the default value for the pressure P at this speed, z. B. to be set a changed pressure level P 'as a base value for this speed or at this speed to be added offset ⁇ P, be kept. This can be maintained in tabular form for several critical rotational speeds in the control device 62 itself or else in the control device 76 (with transfer to the control device 62).
  • each system or printing unit 01 can react differently or the resonance frequencies for it can be slightly different (even with identical units), a so-called "teach-in mode" can be run through during commissioning, so that in the rule and / or Control device 62 or in the control device 76, such a table with resonance frequencies and provided therefor "alternative values" for the pressure P as P 'is deposited.
  • This can then be used to a kind of feedforward control.
  • Access to this table can then advantageously be possible and changeable via an input mask (possibly accessible only via a password-protected commissioning mask, for example). In this case, for example, in addition to the self-adaptation of the system, an external intervention by the (commissioning) staff is possible.
  • the basic procedure is also on the other embodiments of the storage unit 06; 42 adapted to be transferred to the training of the respective actuating means.
  • the contact force can be varied via the adjusting means 21 by appropriate setpoint specification.
  • the adjusting force is variable via the actuator system and / or a displaceable stopper not shown there, the pivoting.
EP07100903A 2006-02-16 2007-01-22 Procédé destiné à la réduction de vibrations Withdrawn EP1820643A3 (fr)

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DE200610007179 DE102006007179A1 (de) 2006-02-16 2006-02-16 Verfahren zur Schwingungsreduktion

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009044319A2 (fr) * 2007-10-03 2009-04-09 Antonio Maccari Procédés et dispositifs permettant de contrôler le fonctionnement de machines de décoration
DE102007062338A1 (de) 2007-12-22 2009-06-25 Manroland Ag Rotationsdruckmaschine mit energieautarken Sensorsystemen
DE102008040174C5 (de) * 2008-07-04 2013-05-23 Koenig & Bauer Aktiengesellschaft Verfahren zum Betrieb einer Maschine mit zumindest einem rotierenden Bauteil
EP3838595A1 (fr) * 2019-12-17 2021-06-23 Heidelberger Druckmaschinen AG Procédé de fonctionnement d'une machine à imprimer rotative

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102008022634A1 (de) * 2008-05-08 2009-11-12 Manroland Ag Verfahren zum Betreiben einer Druckmaschine
DE102010042991A1 (de) * 2010-10-27 2012-05-03 Manroland Ag Druckmaschinenmodul

Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62228730A (ja) 1986-03-29 1987-10-07 Agency Of Ind Science & Technol 回転軸の振動抑制装置
EP0331870A2 (fr) 1988-03-11 1989-09-13 Maschinenfabrik GOEBEL GmbH Palier
DE19652769A1 (de) 1996-12-18 1998-06-25 Voith Sulzer Papiermasch Gmbh Verfahren und Vorrichtung zur Dämpfung von Kontaktschwingungen
DE19930600A1 (de) 1998-08-06 2000-02-10 Voith Sulzer Papiertech Patent Vorrichtung zum aktiven Schwächen unerwünschter Schwingungen einer rotierenden Walze, Vorrichtung zum Behandeln einer Materialbahn, insbesondere aus Papier oder Karton, Walze
DE20011948U1 (de) 2000-07-10 2000-12-07 Skf Gmbh Lageranordnung
DE10107135A1 (de) 2001-02-15 2002-08-29 Windmoeller & Hoelscher Rollendruckmaschine sowie Verfahren zur Schwingungsdämpfung hieran
WO2003064763A1 (fr) 2002-02-01 2003-08-07 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour reduire des vibrations sur des composants en rotation
DE10253997C1 (de) 2002-07-19 2003-12-11 Koenig & Bauer Ag Verfahren und Vorrichtung zur Verminderung von Schwingungen an rotierenden Bauteilen sowie schwingungsgedämpftes rotierendes Bauteil
WO2004085154A1 (fr) 2003-03-26 2004-10-07 Koenig & Bauer Aktiengesellschaft Cylindre et procede permettant de reduire les vibrations du cylindre

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5038680A (en) * 1989-12-18 1991-08-13 Rockwell International Corporation Printing press blanket cylinder assembly and method of making same

Patent Citations (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62228730A (ja) 1986-03-29 1987-10-07 Agency Of Ind Science & Technol 回転軸の振動抑制装置
EP0331870A2 (fr) 1988-03-11 1989-09-13 Maschinenfabrik GOEBEL GmbH Palier
DE19652769A1 (de) 1996-12-18 1998-06-25 Voith Sulzer Papiermasch Gmbh Verfahren und Vorrichtung zur Dämpfung von Kontaktschwingungen
DE19930600A1 (de) 1998-08-06 2000-02-10 Voith Sulzer Papiertech Patent Vorrichtung zum aktiven Schwächen unerwünschter Schwingungen einer rotierenden Walze, Vorrichtung zum Behandeln einer Materialbahn, insbesondere aus Papier oder Karton, Walze
DE20011948U1 (de) 2000-07-10 2000-12-07 Skf Gmbh Lageranordnung
DE10107135A1 (de) 2001-02-15 2002-08-29 Windmoeller & Hoelscher Rollendruckmaschine sowie Verfahren zur Schwingungsdämpfung hieran
WO2003064763A1 (fr) 2002-02-01 2003-08-07 Koenig & Bauer Aktiengesellschaft Procede et dispositif pour reduire des vibrations sur des composants en rotation
DE10253997C1 (de) 2002-07-19 2003-12-11 Koenig & Bauer Ag Verfahren und Vorrichtung zur Verminderung von Schwingungen an rotierenden Bauteilen sowie schwingungsgedämpftes rotierendes Bauteil
WO2004085154A1 (fr) 2003-03-26 2004-10-07 Koenig & Bauer Aktiengesellschaft Cylindre et procede permettant de reduire les vibrations du cylindre

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2009044319A2 (fr) * 2007-10-03 2009-04-09 Antonio Maccari Procédés et dispositifs permettant de contrôler le fonctionnement de machines de décoration
WO2009044319A3 (fr) * 2007-10-03 2009-07-23 Antonio Maccari Procédés et dispositifs permettant de contrôler le fonctionnement de machines de décoration
DE102007062338A1 (de) 2007-12-22 2009-06-25 Manroland Ag Rotationsdruckmaschine mit energieautarken Sensorsystemen
DE102008040174C5 (de) * 2008-07-04 2013-05-23 Koenig & Bauer Aktiengesellschaft Verfahren zum Betrieb einer Maschine mit zumindest einem rotierenden Bauteil
EP3838595A1 (fr) * 2019-12-17 2021-06-23 Heidelberger Druckmaschinen AG Procédé de fonctionnement d'une machine à imprimer rotative
US11504961B2 (en) 2019-12-17 2022-11-22 Heidelberger Druckmaschinen Ag Method of operating a rotary printing press

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