DE102005058786A1 - Vibration reduction method e.g. for damping vibration of cylinder of strip-processing machine, involves determining functional correlation for force course of channel passage through nip point formed by second cylinder - Google Patents

Abstract

The method involves determining a functional correlation for a force course of a channel passage through a nip point formed by a second cylinder. The functional correlation is pre-defined up to a scaling factor determining the height as a time course for an actuator force time course, and is kept in a control and or regulating device. The vibration or the amplitude is measured during the operation of a point of the cylinder by a sensor. The maximum amplitude created on the roll body is then calculated from the measuring value, and the actuators are controlled by the control and or regulating devices according to the pre-defined actuator force time course. An independent claim is included for a device.

Description

The The invention relates to a method and a device for vibration reduction a cylinder according to the preamble of claim 1 or 7.

By the DE 102 53 997 C1 a method and a device for reducing vibrations is known, wherein an elevation in the region of the lateral surface of a rotating component in their height and / or position is variable.

The WO 03/064763 A1 discloses a method and a device for Reduction of vibrations, by means of actuators on pins and / or Warehouse is acted upon. This is an admission of a dependent on an angular position of the component held signal waveform, wherein the reserved control signals can be adapted adaptively.

In the 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.

By the DE 200 11 948 U1 a bearing assembly for a cylinder of a printing machine is known, wherein piezoelectric adjusting elements are arranged for the exact positioning of the bearing between the outer ring and a frame bore.

In JP 62-228730 A vibrations of a rotating shaft by means of Piezo elements reduced.

By the DE 101 07 135 A1 a method for vibration damping of a cylinder of a printing machine is known, 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. In this case, 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.

Of the Invention is based on the object, a method and an apparatus to create vibration reduction of a cylinder.

The The object is achieved by the Characteristics of claim 1 or 7 solved.

The particular advantages of the invention are that by the precontrol with a predefined force curve the required fast reaction times and the high dynamics is reachable. By predetermining one to the channel impact course adapted waveform of the force to be generated by the actuator, is only an adjustment of the signal level required.

From great It is also an advantage that in addition to the channel strike and the excitation through the actor itself into the calculation algorithm. hereby is the vibration as a whole, so also fashions, which by the Actuator itself caused to reduce. Otherwise exists the danger that although a Eigenmoder of the channel impact-induced cylinder vibration diminished but a mode caused by the actuator is increased.

Also Of considerable advantage is that - especially considering both theoretically by the channel strike and by the actuator generated vibration - off the measured value at a fixed location on the cylinder-pin system on a on the cylinder present highest amplitude is closed and this is based on the iterative adjustment of the pulse height is placed. The reading alone would only show a section and possibly lead to significantly wrong conclusions.

Especially Advantageously, the procedure by bearing arrangements feasible, wherein an actor indirectly (via a radial bearing or a radial bearing bearing block) or acts directly on a cylinder pin. Really important Here is the warranty a high dynamics, which in an advantageous embodiment by Use of a piezoelectric actuator is achieved. In an education hydraulically acting actuators can do this by arranging quick control valves be achieved in the hydraulic system.

Of particular advantage with regard to short travel easy mounting is also an embodiment of a bearing assembly of the cylinder, wherein the relevant cylinder in linear bearings to a second cylinder on / off. Here, preferably both the linear bearing elements, the rotary bearing and the vibration compensating actuator are arranged as a unit in a mountable as a whole bearing unit.

In an execution, wherein one of the vibration opposing actuator from an adjusting movement Acting actuator is different, it advantageous the former Actuator to integrate in the movable part of the storage. This remains the effect of the first-mentioned actuator regardless of an arrival / Abstelllage.

embodiments The invention are illustrated in the drawings and are in following closer described.

It demonstrate:

1 a plan view of a double printing;

2 a schematic representation of a Nippdurchganges;

3 a side section through a storage unit;

4 a schematic cross section through a storage unit with actuators;

5 a cross section through the storage unit 3 ;

6 a second embodiment of a bearing with linear adjustment;

7 the camp out 6 in another section;

8th the arrangement of several bearings of a printing unit;

9 a third embodiment of a bearing;

10 a schematic representation of the embodiment according to 9 ;

11 a version with double frontal storage;

12 a schematic representation of the control with adaptive control.

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, short web one or both sides can be printed. The printing unit has a printing unit 01 with at least one on / off cylinder 02 ; 03 , here a double printing unit 01 for two-sided printing in rubber-against-rubber operation, on ( 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 by two printing units 01 formed, each one as a transfer cylinder 02 and one as a form cylinder 03 trained cylinder 02 ; 03 , z. B. printing cylinder 02 ; 03 , And each having an unillustrated inking unit and in the case of wet offset printing additionally have a dampening unit. In each case between the two transfer cylinders 02 is formed in Anstelllage a (double) pressure point.

The cylinders 02 ; 03 are each frontally on or in side frames 07 ; 08 rotatably mounted. At least one in 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 on. The huddled cylinders 02 ; 03 form the nip 05 a width b _N out. The rollover during operation causes channel beats, which in turn vibrations of the cylinder 02 ; 03 stimulate ( 2 ).

The following are exemplary embodiments for the mounting of a cylinder 02 ; 03 by means of bearing arrangements ( 06 ; 42 : su) given, which allow in an advantageous manner counteracting these vibrations by a force in the region of the bearing and / or pin is selectively applied by one or more actuators.

The bearing arrangements ( 06 ; 42 : see below) can be used as storage units ( 06 ; 42 : see below) which contain as assembly both rotary bearings and the actuator (s).

In a first advantageous embodiment have as cylinder units 04 executed modules z. B. a cylinder 02 ; 03 with cones 09 and one already on the cone 09 pre-assembled or pre-assembled (pre-tensioned and / or pre-set) storage unit 06 on. storage unit 06 and cylinders 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 storage unit 06 However, it can also be formed in the usual way, but contain an actuator for counteracting vibrations.

In an advantageous embodiment, it is provided, the cylinder 02 ; 03 in storage units 06 on side frames 07 ; 08 rotatable to store, which the Escape the side frames 07 ; 08 do not penetrate and / or the cylinders 02 ; 03 with her bale including her cones 09 a length L02; L03, which is less than or equal to a clearance LW between the printing cylinder 02 ; 03 to both end faces supporting side frames 07 ; 08 , At the printing cylinders 02 ; 03 to both end faces supporting side frames 07 ; 08 it is preferably not laterally so open side frames, so that the cylinder 02 ; 03 axially removed, but to side frames 07 ; 08 which in the axial direction at least partially overlap with the end face of the mounted cylinder 02 ; 03 have, ie the cylinder 02 ; 03 , in particular its bearing (see below), is frontally through the two side frames 07 ; 08 at least partially framed. In principle, however, can also be a detachable insert in the side frame 07 ; 08 be provided, which is the storage units 06 (42) bears ( 1 ).

Preferably, all four printing cylinder 02 ; 03 (at least three) per end face own storage unit 06 on, in which the on / off mechanism or at least one the relative movement between frame-fixed and movable bearing part bewerkstellendes transmission 11 already integrated. It can also work for two out of three or three of the four cylinders 02 ; 03 the arrival / Abstellmechanismus having bearing units 06 and for the third and fourth cylinders, respectively 02 ; 03 Storage units be provided without on / off mechanism.

3 and 4 show a preferably based on linear trajectories bearing unit 06 in longitudinal and cross section. The on / off mechanism or at least the transmission 11 integrating storage unit 06 points next to a radial bearing 12 , For example, a cylindrical roller bearing 12 , for rotational storage of the cylinder 02 ; 03 also storage media 13 ; 14 for a radial, in particular linear movement of the cylinder 02 ; 03 - for pressure on or pressure off - on. For this purpose, the storage unit 06 (after assembly of the cylinder unit 04 fixed to the frame) carrier-resistant bearing elements 13 as well as against these movable bearing elements 14 on. The carrier-fixed and movable bearing elements 13 ; 14 are as cooperating linear elements 13 ; 14 and together with corresponding sliding surfaces or intermediate rolling elements as a whole linear bearing 13 . 14 educated. The linear elements 13 ; 14 take z. B. in pairs one the radial bearing 12 receiving storage block 16 , z. B. slide 16 between themselves. bearing block 16 and the movable bearing elements 14 can also be made in one piece. The carrier-fixed bearing elements 13 are on a carrier 17 arranged, 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), which, for example, at least on a drive side a recess, not shown 18 (corresponding 6 ) for the passage of a drive shaft, not shown, for a pin 09 a cylinder 02 ; 03 having. Also the side frame 07 ; 08 on the drive side preferably has a recess 19 , in particular as a slot, or a breakthrough 19 for a not shown, with the pin 09 rotatably connected to the drive shaft. On the opposite side of the drive side neither has a recess 18 another recess 19 be provided.

The training of linear bearings 13 . 14 in such a way that the cooperating bearing elements 13 ; 14 both on the assembly storage unit 06 - and not a part of the side frame 07 ; 08 the pressure unit - are provided, allows pre-assembly and pre-adjustment or adjustment of the bearing voltage. The advantageous arrangement of the two the bearing block 16 encompassing linear bearings 13 . 14 allows a backlash-free adjustment, as the two linear bearings 13 . 14 are opposed 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 (each with bearing elements 13 and 14 ) are formed parallel with respect to their direction of adjustment S with respect to a plane perpendicular to the axis of rotation of the cylinder 02 ; 03 Seen spaced apart from each other and preferably the bearing block 16 between them. 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.

As the cylinder 02 ; 03 including pins 09 and storage unit 06 the side frame 07 ; 08 not penetrate, these are already pre-assembled and the bearings (radial bearings 12 as well as linear bearings 13 . 14 ) pre-set or correctly preloaded as module cylinder unit 06 can be used in the printing unit. The term "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 frontal 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. B. then also possible Lich, although provided on the inside while Angussteile or other surveys, but a said continuous assembly path is provided.

For correct placement assembly aids, not shown, for. B. dowel pins in the side frame 07 ; 08 be provided, to which the storage unit 06 the fully assembled cylinder unit 04 is aligned before releasing by releasable holding means, for. As screws, or even cohesively by welding to the side frame 07 ; 08 get connected. For the adjustment of the bearing preload in the linear bearings to be adjusted before insertion into the printing unit and / or post-insertion adjustment 13 . 14 can corresponding means, not shown, for. B. clamping screws may be provided. Preferably, the storage unit 06 - At least to the cylinder side - protected by a cover, not shown, largely against contamination or even encapsulated executed as a unit.

Preferably for a modular design are the storage units 06 for forming and transfer cylinders 03 ; 02 - if necessary, except for the permitted operational size of the travel - identical design. The pre-assembled design allows the effective inner surface of the radial bearing 12 and the outer effective lateral surface of the pin 09 be cylindrical instead of tapered, as both the mounting of the bearing unit 06 on the cone 09 as well as the setting of the bearing clearance can still be done outside the printing unit. Preferably, a cylindrical shaft seat is between pins 09 and radial bearings 12 intended. The storage unit 06 or the radial bearing 12 For example, can be shrunk and the assembly of the pre-assembled cylinder unit 04 complete with storage in the side frame 07 ; 08 respectively. 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 be set in the printing unit (time saved in assembly).

The storage unit 06 , in particular linear bearing unit 06 , Thus, has the movable part as the linearly movable carriage 16 (Guide carriage) on which of the radial bearing 12 and possibly a thrust bearing (eg for lateral register adjustment of the cylinder 03 ) and has a degree of freedom perpendicular to the cylinder axis. The fixed part (carrier 17 with bearing elements 13 ) of the storage unit 06 will be on the side frame inside of the side frame 07 ; 08 attached, z. B. screwed.

In this fixed part of the storage unit 06 is a - in particular backlash-free or biased - gearbox 11 integrated, which one from outside the storage unit 06 on a link of the transmission 11 introduced adjusting movement in a linear movement of the carriage 16 reshapes. Preferably, as in 3 indicated, is such a trained transmission 11 integrated, which is the rotational movement of a merely schematically indicated adjusting drive 21 (Adjusting means 21 ) about, for example, a wave 22 in a linear movement of the carriage 16 perpendicular to the shaft 22 or axis of the adjusting drive 21 and / or perpendicular to the cylinder axis converts. This gear 11 For example, a through the wave 22 driven rotary gear, which cooperates with a movable part of the associated rack. However, it can also be carried out in other ways. The adjustment 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 back of the storage unit 06 , in particular on the storage unit 06 opposite 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 is preferably substantially parallel, but offset from the cylinder axis.

Alternative to the above rack solution, the following variant is more advantageous: Rotary actuator 21 (ideally stepper motor 21 for synchronization between the two frontal side frames 07 ; 08 , Adaptation gear (ideally as a mounted planetary gear in front of the actuator 21 ), Angular gear (self - locking worm gear as shown in 3 and 5 , as axes drive motor and linear travel orthogonal), transfer gear rotary - linear (preloaded and thus backlash ball screw as shown in 3 and 5 ).

• – Kantenmaß (Länge L06 der Lagereinheit 06 × Breite B06 der Lagereinheit 06, Querschnitt zu Zylinderstirnfläche) < Durchmesser D des Zylinders- oder Schmitzrings, vorzugsweise Eckenmaß e < D
• – L06 oder B06 < 300 mm, vorzugsweise e < 300 mm, in einer günstigen Ausführung L06, B06 < 200 mm, in einer besonders vorteilhaften Ausführung L06 und B06 jeweils kleiner 150 mm.

The space should preferably be smaller in cross-section or at most equal to the cross-sectional area of the cylinder 02 ; 03 (Bearer ring diameter):

• - Edge dimension (length L06 of the bearing unit 06 × width B06 of the storage unit 06 , Cross section to cylinder face) <diameter D of the cylinder or bearer ring, preferably corner dimension e <D
• - L06 or B06 <300 mm, preferably e <300 mm, in a favorable design L06, B06 <200 mm, in a particularly advantageous embodiment L06 and B06 each less than 150 mm.

Advantageously, a force measurement, in particular for the radial force in the adjustment, integrated as part of the storage or the drive, for example, by the current consumption of the actuating means 21 , z. B. the engine 21 or a moment in the transmission, z. B. the torsional moment of the spindle, etc., is determined and evaluated.

In a printing unit with at least three as printing unit 01 together acting cylinders 02 ; 03 (For example, with impression cylinder) are at least two of the three cylinders 02 ; 03 in such linear bearings 13 . 14 each movably supported 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 connection level a maximum angle of 15 °. The movable cylinder 02 ; 03 is then in each case only in this cylinder 02 ; 03 assigned, described above storage units 06 stored.

As already mentioned, the linearly movable cylinders 02 ; 03 preferably with respective end bearing units 06 as a cylinder unit 04 pre-assembled or pre-assembled. For this purpose, these cylinders 02 ; 03 as a unit with bales and two frontal cones 09 , z. B. an above maximum length L02; L03 on.

In one as a double printing unit 01 trained printing unit 01 are preferably at least the two form cylinder 03 and at least one of the two transfer cylinders 02 stored linearly movable. The second transfer cylinder 02 can be operationally fixed to the frame, but in particular adjustable in its position, be stored. In one variant, however, all four cylinders can also be used 02 ; 03 be mounted linearly movable.

In a three-cylinder printing unit 01 for the one-sided printing are at least two, in particular at least the two ink-carrying, cylinder 03 ; 02 , z. B. forming and transfer cylinder 03 ; 02 , in a variant, however, all three cylinders 03 ; 02 stored linearly movable.

For the above-mentioned active vibration damping in the storage area - as in 4 indicated - the camp 06 at least one actor 23 , z. B. piezoelectric actuator 23 on, by means of which an introduction of force in the bearing contact point is made possible. Particularly advantageous is the integration of the actuators 23 in above-mentioned linear bearing unit 06 , Advantageously, in order to detect the vibrations, two force transducers are provided at an angle not equal to zero, preferably at 90 ° or 120 ° apart from each other with respect to a circumferential direction. Is only an actor 23 per storage unit 06 provided, it may also be provided only a sensor. A possible embodiment represent piezoelectric sensors, in an advantageous version at the same time as an actuator 23 available.

In general education of the printing unit 01 are to force resulting directions in each direction of the leaf level 4 to enable two actuators 23 and at least one spring element 24 , here designed as a disc spring package required. The spring element 24 is preferably the actuators 23 arranged substantially opposite one another. For reasons of space here are two spring elements 24 for the provision as an abutment to the actuators 23 intended. The actors 23 have for example in the direction of action (radial direction of the pin 09 out) considers a length of z. B. at least 10 mm, advantageously at least 15 mm, in particular at least 20 mm. So that a) sufficiently large moment / force can be applied, the actuator points 23z , B. a cross-sectional area perpendicular to the direction of action of z. B. at least 50 mm ² , in particular at least 60 mm ² . The piezo 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 actors 23 are z. B. in each case by an angle β, z. B. greater than 20 °, in particular between 20 ° and 45 °, z. B. about 30 ° inclined to the defined by the direction S straight.

In an advantageous embodiment of the printing unit 01 , wherein the axes of rotation of the printing cylinder 02 ; 03 lie in a common plane E, is basically only an actor 23 in the storage unit 06 sufficient. However, this must be designed according to high performance. The effective direction of this one actor 23 then preferably runs substantially in this common plane E and perpendicular to the axis of rotation.

In the first embodiment are thus for the arrival / Abstellbewegung one hand (as adjustment 21 trained actor 21 ) and for vibration compensation (actuator 23 On the other hand, different actuators 21 ; 23 intended.

The actors 23 are for control with a control and / or control device 57 , z. B. a schematically in 12 dashed lines shown adaptive control 57 , in signal connection.

6 and 7 show a second advantageous, based on linear trajectories bearing unit 06 in longitudinal and cross section. The bearing unit which integrates the on / off mechanism 06 points next to a radial bearing 12 , For example, a cylindrical roller bearing 12 , for rotational storage of the cylinder 02 ; 03 bearing means 13 . 14 for a radial movement of the cylinder 02 ; 03 - for pressure on or pressure off - on. For this purpose, the storage unit 06 (after mounting the bearing unit 06 fixed to the frame) carrier-resistant bearing elements 13 as well as against these movable bearing elements 14 on. The carrier-fixed and movable bearing elements 13 ; 14 are as cooperating linear elements 13 ; 14 and together with corresponding sliding surfaces or intermediate rolling elements in total as a linear bearing 13 . 14 educated. The linear elements 13 ; 14 in pairs take a radial bearing 12 receiving storage block 16 , z. B. slide 16 between themselves. bearing block 16 and the movable bearing elements 14 can also be made in one piece. The carrier-fixed bearing elements 13 are on a carrier 17 arranged, which in total with the side frame 07 ; 08 is connected or is. The carrier 17 is for example as a carrier plate 17 executed, which, for example, at least on a drive side a recess 18 for the passage of a drive shaft shown in dashed lines 20 one in 7 not shown pin 09 the cylinder 02 ; 03 having. Also the side frame 07 ; 08 on the drive side preferably has a recess 19 or a breakthrough 19 for a drive shaft 20 on. On the opposite side of the drive side neither has a recess 18 another recess 19 be provided ( 6 ).

The training of linear bearings 13 . 14 in such a way that the cooperating bearing elements 13 ; 14 both on the assembly storage unit 06 - and not a part of the side frame 07 ; 08 of the printing unit 01 - Are provided, allows pre-assembly and pre-adjustment or adjustment of the bearing voltage. The advantageous arrangement of the two the bearing block 16 encompassing linear bearings 13 . 14 allows a backlash-free adjustment, as the two linear bearings 13 . 14 are opposed 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 in which it is at play-free positions of the cylinder 02 ; 03 also arrives.

As the cylinder 02 ; 03 including pins 09 and storage unit 06 the side frame 07 ; 08 not penetrate, these are already pre-assembled and the bearings (radial bearings 12 as well as linear bearings 13 . 14 ) pre-set or correctly preloaded as module cylinder unit 04 can be used in the printing unit. The term "non-penetration" and the above definition with respect to the clear width is to 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 frontal 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. Example, even if possible on the inside while Angussteile or other surveys are provided, a named continuous assembly path is provided, however.

The storage units 06 are in the way on the inner walls of the side frames 07 ; 08 arranged that the cylinder 02 ; 03 , in particular their storage units 06 on the cylinder 02 ; 03 facing side through the side frame 07 ; 08 are supported, which has static and mounting advantages.

For correct placement, mounting aids 26 , z. B. dowel pins 26 in the side frame 07 ; 08 be provided, to which the storage unit 06 the fully assembled cylinder unit 04 is aligned before passing through releasable holding means 27 , z. B. screws 27 , or even cohesively by welding with the side frame 07 ; 08 get connected. For the adjustment of the bearing preload in the linear bearings to be adjusted before insertion into the printing unit and / or post-insertion adjustment 13 . 14 can appropriate means 28 , z. B. clamping screws 28 be provided ( 6 ). Preferably, the storage unit 06 - At least to the cylinder side - through a cover 29 largely protected against contamination or even encapsulated executed as a unit.

In 6 is schematically the cylinder 02 ; 03 with cones 09 and a preassembled storage unit 06 characterized. This assembly can thus be preassembled between the side frames 07 ; 08 the pressure unit assembly-friendly used and attached to designated locations. Preferably for a modular design are the storage units 06 for forming and transfer cylinders 03 ; 02 - if necessary, except for the permitted operational size of the travel - identical design. The pre-assembled design allows the effective inner surface of the radial bearing 12 and the outer effective lateral surface of the pin 09 be cylindrical instead of tapered, as both the mounting of the bearing unit 06 on the cone 09 as well as the setting 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 ).

Pressure on is done by moving the bearing block 16 towards the pressure point by means of a by at least one actuator 31 on the storage block 16 applied force F, in particular by a force-controlled or via a force defined actuator 31 , By means of which for employment a defined or definable force F in pressure-on direction to the bearing block 16 can be brought ( 7 ). The decisive for the color transfer and thus the print quality, among others, decisive line force in the nipples 05 is therefore not by a travel, but by the balance of power between the force F and between the cylinders 02 ; 03 resulting line force F _L and the resulting equilibrium defined. In a first, not specifically illustrated embodiment are cylinders 02 ; 03 in pairs put together by the bearing block 16 with the corresponding adjusted force F via the actuator (s) 31 is charged. If several (eg three or four) are adjacent to one another in direct succession, each cylinder interacting in pairs 02 ; 03 executed without a possibility for fixing or limiting the travel with a purely force-dependent control mechanism, so it is indeed a. With respect to the required pressures (line forces) set system off and subsequently correct again, make a basic setting is due to the z. T. overlapping reactions difficult.

For basic adjustment of a system (with corresponding elevators, etc.), it is therefore provided in an advantageous embodiment that at least the two middle of the four cylinders 02 In other words, at least all of the two outer cylinders 03 different cylinders 02 at least during a period when setting in a defined position, advantageously in the Anstelllage found by the balance of forces, fixed or at least wegbegrenzbar.

Particularly advantageous is an embodiment, wherein the 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. This will - in contrast to pure Wegbegrenzung - on the one hand, a maximum line force when acting 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.

To a pressure point facing side, the storage unit 06 - At least during the setting process - a portable stop 39 on, which limits the travel along the direction S to the pressure point. The stop 39 is locatable in such a way that the stop surface effective as a stop 33 along the direction of adjustment S at least in a range is variable. It is thus provided in an advantageous embodiment, an adjusting device (adjustable stop), by means of which the position of a pressure near the end position of the bearing block 16 is adjustable. For Wegbegrenzung / adjustment serves z. B. a wedge drive described below. Placing the stop 39 can always be used manually or via an actuator ( 34 , see below) 34 respectively. Next is an advantageous embodiment in 6 and 7 not shown holding or clamping means provided by means of which the stop 39 set in the desired location. Next is at least one spring-acting element 36 , z. B. spring element 36 , provided, which on the storage block 16 a force F _R from the stop 39 in a direction away from the pressure point. Ie. the spring element 36 causes a pressure-off in the event that the bearing block 16 is not prevented from moving in any other way. Pressure on is done by moving the bearing block 16 towards the stop 39 by at least one actor 31 , In particular a force-controlled actuator 31 , By means of which for employment either a defined or definable force F in pressure-on direction to the bearing block 16 can be brought. Is this force F greater than the restoring force F _{R of} the spring elements 36 , so takes place with appropriate spatial training a hiring of the cylinder 02 ; 03 to the adjacent cylinder 02 ; 03 and / or hiring the storage block 16 to the stop 39 ,

Ideally, the applied force F, the restoring force F _R and the position of the stop 39 chosen so that between stop 39 and the stop surface 33 of the storage block 16 no significant force .DELTA.F is transmitted in the set position, for example, | ΔF | <0.1 · (F - F _R ), in particular | ΔF | <0.05 * (F - F _R ), ideally | ΔF | ≈ 0. In this case, the contact force between the cylinders 02 ; 03 much above that by the actor 31 applied force F determined. The decisive for the color transfer and thus the print quality, among others, decisive line force in the nipples 05 is therefore not primarily by a travel, but at quasi-free stop 39 defined by the force F and the resulting equilibrium. Basically, after finding the basic setting with the appropriate forces F would be a removal of the stop 39 or a corresponding, effective only during the basic setting fixation conceivable.

The actor 31 can basically as any, a defined force F applying actuator 31 be executed. The actuator is advantageous 31 as actuatable by pressure medium actuating means 31 , in particular as a piston movable by a fluid 31 executed. Advantageous in terms of possible tilting is the arrangement of several, here two, such actuators 31 , As fluid preferably comes because of their incompressibility a liquid, for. As oil or water, used.

To operate here as a hydraulic piston 31 executed actuators 31 is in the storage unit 06 a controllable valve 37 intended. This is performed, for example, electronically controlled and provides the hydraulic piston 3i in a position without pressure or at least to a lower pressure level, while in another position of the force F bedin low pressure P is present. In addition, a non-designated leakage line is provided here for safety.

In order to avoid excessive stopping / stopping distances and still to secure track winders, it can be found on the side of the bearing block away from the pressure side 16 a Wegbegrenzung by a mobile, force-limited stop 38 as overload protection 38 , z. B. spring element 38 be provided, which in the operational pressure-Ab, ie the piston 31 are relieved and / or retracted, although as a stop 38 for the storage block 16 serve in pressure-off position, in the case of a railway winder or other excessive forces from the pressure point but gives way and gives a greater way free. A spring force of this overload protection 38 is therefore chosen larger than the sum of the forces from the spring elements 36 , When operational on / off is therefore only a very short travel, z. B. only 1 to 3 mm, providable.

The stop 39 is in the illustrated embodiment ( 7 ) as transversely to the direction of adjustment S movable wedge 39 executed, wherein when moving the same position of the respective effective stop surface 33 varies along the direction of adjustment S. The wedge 39 is supported, for example, on a carrier-resistant stop 32 from.

The one here as a wedge 39 executed stop 39 is by an actor 34 , For example, a pressure medium actuatable actuating means 34 such as a pressure medium actuated piston 34 in a working cylinder with (double-acting) piston or an electric motor via a threaded spindle, movable. This actor 34 may be either in both directions effective or, as shown here, designed as a one-way actuator, which when activated against a return spring 41 is working. The force of the return spring 41 is for the above reasons (largely force-free stop 39 ) so weak that the wedge 39 is kept in its correct position only against gravity or vibration forces.

Basically, the stop 39 in another way (eg, as a plunger adjustable and fixable to the setting direction S, etc.) in such a way that it can be varied in the adjustment direction S, and - at least during the adjustment process - fixable stop surface 33 for the movement of the storage block 16 forms in the direction of the pressure point. In a non-illustrated embodiment, a place of the stop takes place 39 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.

This as a double printing unit 01 executed printing unit 01 of the 8th shows schematically each cylinder 02 ; 03 a storage unit 06 , In an advantageous embodiment, shown here form the centers of rotation of the cylinder in pressure-on position 02 ; 03 an imaginary connecting line or plane E (hereinafter referred to as "linear double printing unit"). Preferably, the plane E and the incoming or outgoing web define an internal angle deviating from 90 ° between 19 and 38 °, in particular from 80 to 41 ° a. The storage unit 06 the transfer cylinder 02 , in particular all cylinders 02 ; 03 , are in the assembled state in the in 8th illustrated embodiment of the side frame 07 ; 08 arranged such that their adjusting directions S - z. B. for reasons of a force-defined pressure-on setting - with the connection plane E 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). Particularly advantageous in terms of assembly, this arrangement, when the adjustment direction S is horizontal and the web is substantially vertical. In an in 8th illustrated embodiment, the adjustment direction S can also extend parallel to the plane E. In both variants, the direction of the introduction of force by the channel impact (resulting main vibration level during Nippdurchtritt) in substantial proportions also corresponds to the actuating or force direction of the actuators 31 , Counteracting the vibrations by the channel impact is in this embodiment with the same actuators 31 as possible on / off.

In the illustrated second embodiment are thus for the on / off movement on the one hand and for the vibration compensation on the other hand, the same actuators 31 intended.

In a modified version of an angular (n or u printing unit 01 ) arranged double printing unit 01 is below the plane E ', the connecting plane of the pressure point forming cylinder 02 and under plane E '', the connection plane between the forming and transfer cylinders 03 ; 02 be understood, and the above to the angle β in the direction of adjustment S at least one of the pressure point forming cylinders 02 or the form cylinder 03 and the plane E 'or E''are related.

One of the cylinder forming the pressure point 02 Can also be stationary and operationally inoperable (but possibly adjustable) in the side frame 07 ; 08 be arranged while the other is stored along the direction of adjustment S.

At the channel strike, ie the Nippdurchgang the 2 To counteract oscillations arising, can now simultaneously or out of phase to the channel strike / Nippdurchgang a force pulse directly or indirectly on the pin 09 or the storage block 16 the storage unit 06 be executed.

Two approaches are possible. In a first embodiment, the time for the force pulse from the (known) angular position of the cylinder 02 ; 03 certainly. Ie. it is provided for damping the vibration actuator (actuator 31 or an additional actuator 40 or 23 (see below)) as a function of the angular position of the cylinder in question 02 ; 03 acted upon by a corresponding signal or manipulated value. In this case, with respect to the point in time 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.

In the second embodiment, the application of the signal or control value in response to measurement signals, ie in a real control loop. This measurement signal can z. B. from a displacement or acceleration measurement on the storage unit 06 (especially at the storage block 16 or cones 09 ) or as a pressure measurement in the hydraulic system for pressure medium supply of the pressure on / off position bewerkstellenden actuators 31 be.

For the generation of the oscillation counteracting force pulse two embodiments are possible. In the first embodiment, the generation of these force pulses is effected by the actuators acting on the pressure on / off position 31 yourself. For this purpose are in the actuators 31 upstream hydraulic system, not shown, fast control valves provided. The actors 31 or quick control valves are available for the modulation of the applied pressure with a higher pressure beyond the Anstelldruck for acting on the signal / force pulse z. B. again with a control and / or control device 57 in connection.

In a second embodiment, in addition to the pressure on / off position bewerkstellenden actuators 31 further, in particular highly dynamic acting actuators 40 , z. B. piezoelectric actuators 40 be provided, which also on the storage block 16 Act.

These can (dashed in 7 indicated) z. B. in the plunger of the pistons of the actuators 31 be integrated. In the case of two different actors 31 ; 40 are the low-frequency positioning movements by the pressure on / off position bewerkstellenden actuators 31 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 connection.

The in the second embodiment ( 6 to 8th ) specified solution (with or without additional piezoelectric actuator 40 ) of the vibration damping is advantageous for vibration damping used, since the direction of the pressure forces between two hired cylinders 02 ; 03 and the direction of movement in the storage unit 06 lie in a line. In hitherto often customary embodiments, wherein the pressure-on movement is carried out by means of eccentric bearing, the feed movement does not take place in the same direction as the pressure forces. For linear bearings (as in 3 to 5 or in 6 to 8th ), 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.

In an advantageous, only in 7 indicated variant of the second embodiment of the second embodiment (different drives for adjusting movement vibration compensation) can the actuators 23 bearing block 16 out 4 (but without the actuator from the 3 and 5 ) in by the actuators 31 with respect to the actuating movement driven bearing assembly 06 be arranged. This z. B. the transmission 11 of the 3 and 5 , on / off, for example, as in the 6 to 8th by means of at least one actuator 31 , One of one or more in the warehouse block 16 integrated actuators 23 is in 7 indicated by dashed lines as an example. The arrangement of the actuators 23 to the first example is the same as that to the bearing assembly 06 (with the omission of the actor 40 ) of the second example.

In a third embodiment ( 9 and 10 ) is a bearing assembly 42 for receiving the pins 09 the cylinder 02 ; 03 as usual, on or in the side frame 07 ; 08 arranged radial bearing 42 , z. B. as a multi-ring bearing 42 executed. For engagement and deactivation, the bearing assembly 42 be executed as an eccentric bearing, wherein by pivoting an eccentric outer ring, the axis of the bearing 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 arrangement 42 has at least one (in 9 and 10 split) 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 inside 49 on. The eccentric ring 48 is for example via a radial bearing 51 , z. B. a sliding or needle bearing 51 , swiveling in an exterior ring 52 stored. In the structure of the storage unit 42 are between at least two adjacent rings 43 ; 46 ; 48 ; 49 . 52 (here the two rings 48 ; 49 of the split intermediate ring 43 ) Actors 44 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. In the example, the intermediate ring 43 executed 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 actors 44 are for targeted admission to a control and / or control device 57 in signal connection. This includes z. B. an algorithm which the actuator 44 provides a waveform.

Preferably, at least two actuators 44 arranged, of which z. B. one in the angular range of the circled here only by the reference numeral 05 indicated Nippstelle 05 (to the next cylinder 02 ; 03 ) as well as the other opposite. In addition or instead, however, in pairs opposite groups of actuators 44 in a certain angular range around the nip 05 be arranged around and opposite. These pairs of opposing actuators 44 Then, for example, each opposite to each other acted upon the movement of the inner ring 46 or the pin 09 to enable. The arrangement of a plurality of circumferentially mutually offset in the circumferential direction pairs of actuators 44 allows it through the nip 05 To influence "spinning" vibration even in the range decaying vibrations by force pulses, as excited by the channel impact vibration level with the cylinder 02 ; 03 (unlike the intermediate ring 43 ) turns.

In addition to several circumferentially distributed actuators 44 can also actors 44 be spaced apart in the axial direction of the bearing. This is depending on the control a bending moment on the bearing inner ring 46 and with it the pin 09 be applied.

The time course of the activation of the actuators 44 For example, it can be speed-dependent (see also below) and possibly additionally depending on parameters such as temperature and / or contact force of the cylinders 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 correlates with the angular position of the respective cylinder 02 ; 03 However, finding the optimum or sufficient signal level can be subject to an adaptive control process (see below). The activation of the actuators 44 can be done with their transitions (on or off) with parabolic, sinuidal or other higher-order functions.

In 10 schematically is a variant of the bearing assembly 42 of the 9 shown, wherein z. B. in a Nippstelle 05 pointing half space between 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. In the Nippstelle 05 Opposite area can also be such an extended actuator 44 or as indicated several actuators 44 next to each other between the inner and outer ring 48 ; 49 be arranged. As indicated, there should be gaps in the circumferential direction 55 between the side (half space) of the nip 05 attributable and attributable to the opposite side actuators 44 be provided so that the inner ring 49 in the direction of Nippstelle 05 remains movable within certain limits. The Nippstelle 05 attributable and attributable to the opposite side actuators 44 are addressed as mentioned above again in reverse.

In the case of very slim cylinders, in addition to the problem of channel impact, there is also the problem of static cylinder bending due to the compressive stress. As a result, the Drucktucheindrückung is reduced in the middle of the bale, which can lead to color transfer problems. On the other hand, it can come with teeth of two cylinder spur gears to a torque when the cylinder 02 ; 03 are moved towards each other and there is a tangential motion component. The latter may for example be the case when the cylinders 02 ; 03 of the printing unit 01 not linear, but n-, u- or z-shaped are arranged.

To compensate for the deflection is in a further development ( 11 ) to the aforementioned embodiments, a double bearing, ie, each with two axially spaced bearing points, on each pin 09 used. In this case, preferably, each closer to the bale seated bearing in the manner of a bearing assembly 06 ; 42 with a highly dynamic actuator counteracting the vibration 23 ; 31 ; 44 (in the following "dynamic camp" 06 ; 42 ) executed, the more distant bearing, however, as a bearing assembly 53 without highly dynamic actuator 23 ; 31 ; 44 (in the following "fixed camp" 53 ). However, both types of bearings have a pressure on / off adjustment. The solid camp 53 for example, except for the actuator 23 ; 31 ; 44 in the same way to the dynamic bearing 06 ; 42 be educated. The dynamic camp 06 ; 42 may be in the manner of one of the above-described storage units 06 ; 42 out 3 to 10 be executed. In the case of the bearing arrangement 06 according to 6 to 8th can the solid bearing 53 also according to the storage unit 06 be formed, but this can account for quick control valves.

The pin 09 between the two bearing points or bearing units 06 ; 42 ; 53 a double bearing is advantageously made soft. Ie. the distance between the two bearings is large and / or the pin 09 designed with a comparatively small diameter, so that during radial movement through the actuator 23 ; 31 ; 44 no large additional forces due to the second bearing unit acting as a support bearing 53 arise. However, a thick, long pin is advantageous 09 opposite a short, thin pin 09 because the former has greater torsional stiffness with the same bending softness.

Should be on the pin 09 to the rotary drive a gear 54 be arranged, this is preferably close to the outer storage unit 53 be arranged. By the proximity of the gear 54 to the "fixed" camp 53 it comes to lower torque introduction into the cylinder 02 ; 03 via the meshing of adjacent gears 54 ,

By changing the radial position of the two adjacent bearings 06 ; 42 respectively. 53 a static bending moment can be introduced to compensate the cylinder bending. This adjustment can 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. in another, especially in connection with the linearly movable bearing blocks 16 The first and second embodiments of advantageous embodiment, the initiation of the static bending moment takes place by an adjustment of the bearing blocks 16 the outer, especially solid, bearing 53 towards the inner, especially dynamic, camps 06 ; 42 ,

Advantageous for adjusting the counter-bending is a force measurement in both camps 06 ; 42 ; 53 of the double bearing.

In training the camp 06 ; 53 with linearly movable bearing blocks 16 and a mechanism with adjustment 21 for the on / off movement, which carries out a hiring away defined (eg 3 to 5 ), the size of the bending moment introduction required to compensate for the static deflection can be determined, for example, as follows: First, the bearing blocks 16 all four camps 06 from pressure off to the pressure on position (eg synchronously). From the resulting force change at the outer and inner bearings 06 ; 53 can about the cylinder geometry (as well as the distance between outer and inner bearing 06 ; 42 ) the effective line force (as well as the already acting counterbending moment) are calculated. The additionally necessary counterbending moment can then be achieved by only moving the bearing blocks 16 the outer camp 53 be generated in the pressure-down direction on the pin bend.

• – Die Kompensationsgüte soll unempfindlich gegenüber der Variation folgender Betriebsparameter sein: Drucktuch-Typ, Zustellung (bedingt durch Unterzüge und/oder Drucktuch-Dicken),
• – Das Konzept soll auf ein breites Spektrum an Maschinenklassen (Zeitung/Akzidenz) und Formate (Doppel- und Einfachumfang) weitestgehend unverändert anwendbar sein
• – Die durch den Kanalschlag entstehenden Schwingungen sollen bei allen Drehzahlen optimal minimiert werden. Optimal bedeutet hierbei nicht zwangsläufig eine vollständige Eliminierung. Vielmehr ist es das Ziel die Schwingungen so niedrig zu halten, dass im Druckprodukt keine Streifen mehr wahrnehmbar sind
• – Die Schwingungen sollen über die gesamte Drucklänge minimiert bzw. eliminiert sein.

The following is a particularly suitable procedure (but also advantageous in connection with a device suitable for this purpose, eg according to example one, two or three and optionally the double bearing arrangement 06 ; 42 ; 53 out 11 ) for an active vibration compensation that meets the following requirements:

• - The compensation quality should be insensitive to the variation of the following operating parameters: blanket type, infeed (due to beams and / or blanket thicknesses),
• - The concept should be applicable to a wide range of machine classes (newspaper / commercial) and formats (double and single circumference) largely unchanged
• - The vibrations caused by the channel impact should be optimally minimized at all speeds. Optimal does not necessarily mean complete elimination. Rather, the goal is to keep the vibrations so low that in the printed product no more stripes are perceptible
• - The vibrations should be minimized or eliminated over the entire printing length.

• – Eine Aktorik, die mittels elektrischer Signale in der Größe vorgebbare Kraft- oder Biegemoment am Lager einleitet, wodurch die Biegung des Zylinders dynamisch bzw. statisch verändert werden kann. Die Kraft- oder Biegemomenteinleitung erfolgt hierbei im wesentlichen nur während der Dauer des Kanalsschlags.
• – Eine Sensorik, die in der Lage ist die Größe vorhandener Schwingungen, insbesondere der Biegegrundschwingung und der ersten und zweiten Biegeoberschwingung, zu detektieren, und in elektrische Signale umzuwandeln.
• – Eine adaptive Steuerung, welche aus den aktuellen Sensorsignalen und vorausgegangenen Sensorsignalen die Aktor-Signalvorgaben für den nächsten Überrollungszyklus ableitet. Ist es notwendig mehrere Schwingformen zu reduzieren, so ist das Ziel nicht alle Amplituden vollständig zu eliminieren, sondern aller diese Schwingungen auf ein drucktechnisch irrelevante Größe zu reduzieren.

These requirements are fulfilled by one or more of the following points:

• - An actuator that initiates by means of electrical signals in size specifiable force or bending moment at the camp, whereby the bending of the cylinder can be dynamically or statically changed. The force or bending moment introduction takes place essentially only during the duration of the channel strike.
• - A sensor that is able to detect the size of existing vibrations, in particular the bending fundamental and the first and second bending harmonic, and convert it into electrical signals.
• - An adaptive control, which derives the actuator signal specifications for the next rollover cycle from the current sensor signals and previous sensor signals. If it is necessary to reduce several vibration modes, then the goal is not to completely eliminate all amplitudes, but to reduce all these vibrations to a value irrelevant to printing technology.

First, in a preparatory step on the basis of the geometrical dimensions for the anticipated or desired Nippbreite in pressure-on and for the known channel width an expected force curve (temporally or drehwinkelabhän gig). Such a functional relationship or relationship F ₀ (φ) 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. By a function found in the manner for the theoretically resulting channel impact force curve, it is possible to make statements on the mode shape of natural oscillations and expected mode amplitudes together with geometric data by means of machine dynamic calculations.

to disambiguation the following should be noted: Coupled to a system Cylinders are always on several modes, where the bending shape are very similar to each individual cylinder, which "only" by the phase relationship the cylinder movements differ from each other. These are similar Fashions would be in the present context z. For example, as a "fashion group" As a rule, the frequencies of these modes of the "fashion group" are comparatively narrow together (eg all in the range 150 ... 200 Hz).

in the present context is now under the names "fundamental", "first harmonic", "second Harmonic "etc. not simply all modes (including the different modes of a "mode group") according to the frequencies meant in ascending order. The order takes place in the sense described here by fashion groups, d. H. with first, second, third harmonic is meant the first, second, third mode group. This would then correspond something like that like the modes of the uncoupled cylinder.

Under Fundamental vibration are thus those vibration modes to understand where the dynamic bending line of the individual cylinder between the bearings essentially mirror-symmetrical to the center of the bale is and has no nodes on the bale.

Under first harmonic are (all) those vibrational modes too understand where the dynamic bending line of the individual Cylinder between the bearings substantially point-symmetrical to the middle of the ball is and exactly one node on the ball Has.

Under second harmonic are (all) those vibration modes understand where the dynamic bending line of the individual Cylinder between the bearings substantially mirror symmetry to the middle of the bale and exactly two nodes of vibration on the bale Has.

The Oscillation frequencies of the mode groups are i.d.R. further separated from each other, as the vibration frequencies within a Fashion Group.

As an alternative to the purely theoretical (geometrical considerations) definition of the shape of the channel impact force curve (context F ₀ (φ)), another favorable embodiment of the determination / determination of the channel force profile by force measurement in quasi-static overrun, ie below the excitation of a vibration. This can, for example, at machine speeds less than 20 m / min, or z. B. at infeed speed of 3 to 8 m / min machine speed (= peripheral speed of the cylinder 02 ; 03 ) respectively.

For the Aktorkraft-time curve is now up to a height-determining scaling factor K of the above-mentioned method (purely theoretical or by measurement) assumed channel impact force course and in a control and / or regulating device 57 or a force curve generator 59 maintained. The control and / or regulating device 57 can in addition to appropriate storage and / or computing means the force curve generator 59 included. Under certain circumstances, knowing the transfer function of the actuator 23 ; 31 ; 44 for the reproached output signal already the distortion are considered backwards to ultimately the desired course as a force on the actuator 23 ; 31 ; 44 to obtain. 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 actor 23 ; 31 ; 44 Preferably, a time course is predetermined, which is, however, formed using the held Aktorkraft angular position course taking into account the machine speed or speed, etc.

Independent of the manner of obtaining the channel impact force curve thus becomes an Aktorkraft-time course or an Aktorkraft angular position course this course formed and as a function of the angle (discrete values of a table or as a mathematical function).

The further procedure is now based on the requirement that in minimizing the vibration both by the channel impact, as well as by the actuator 23 ; 31 ; 44 self-induced vibration modes. This is done z. B. in that in the calculation of the maximum amplitudes on the bale, the corresponding modes are taken into account.

The further procedure is exemplified by the 12 clarified. During the Operation will now be at least one point of the cylinder 02 ; 03 (including pins 09 ) by means of a sensor 56 (eg a mechanical force transducer or an optical measurement) measures the oscillation or the amplitude at this location, or a variable representing the oscillation or the amplitude at this location. However, this only reflects the deflection at this particular location and still gives no direct indication of anywhere on the bale of the cylinder 02 ; 03 resulting amplitudes.

In the next step is now -. B. by a calculation algorithm in a computing means of the control and / or regulating device 57 - arithmetically the maximum somewhere on the ball of the cylinder 02 ; 03 For this purpose, the measured signal with respect to the amplitudes of the main participating modes (fundamental and / or first harmonic and / or second harmonic in the above sense) can be evaluated in an advantageous embodiment by appropriate filter. From the measured or filtered mode amplitudes of the fundamental oscillation (channel beat) and by the actuator 23 ; 31 ; 44 additionally excited (second) harmonics) (in the above sense), the maximum amplitude anywhere on the bale is calculated. This is possible by knowing the mode shape of the eigenmodes, which can be computed dynamically (see above).

By the control and / or regulating device 57 become the actors 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). No curve shape or a time course is generated by the control, but only the height of the predetermined curve is adjusted. The at the different actors 23 ; 31 ; 44 a cylinder 02 ; 03 introduced forces are preferably always in the same proportion to each other for a given channel strike. 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 maximum amplitude is minimal.

The Force introduction preferably takes place only within the narrow Time window of the channel overrun. The predetermined actuator force time course (or actuator force angular position curve) is corresponding selected.

The information about the state of rotation of the cylinders 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 Kanalschlaganfangs- and Kanalschlagendwinkel. The time of admission so controlled as a function of the angular position.

As a feedback input for the optimization of the vibration curve of the cylinder vibrations by the appropriate sensor 56 (see below) from a start angle> channel impact end 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.

Basically you can apply the procedure separately to any mode. In an advantageous execution but finds only the amplitude of the channel beat fundamental mode (ngroup) input, as well as in dependence from the force introduction form, if necessary, also the mode amplitude of the second Harmonics (not stacked channel) and with stacked channels of the first harmonic entrance into consideration.

According to o. G. is for suppression a channel strike finding the appropriate scaling factor K required, which in the context of adaptive-iterative control advantageous with the help of the measured amplitude of the fundamental (A0) and the second Moder (A2) is iteratively optimized.

• – entweder K0 = 0 (d. h. keine Aktorwirkung),
• – oder einem festen Referenzwert K_REF,
• – oder dem Wert des vorausgegangenen Betriebszustandes.

The following measures can be used for the iteration: First of all, a fixed start value for K is started, eg. B.

• - either K0 = 0 (ie no actuator effect),
• Or a fixed reference value K _REF ,
• - or the value of the previous operating state.

Subsequently, the two mainly existing mode amplitudes (eg A0 and A2) are measured or filtered and the abovementioned maximum amplitude is calculated, which is theoretically in any one place of the cylinder 02 ; 03 results.

• – entweder fest vorgegeben werden,
• – oder im Sinne einer adaptiven Schrittweitensteuerung selbst Ziel einer Optimierung sein.

Then the scaling factor K is increased by an amount ΔK. The size of ΔK can basically

• - either fixed,
• - or be in the sense of an adaptive step size control itself the goal of optimization.

The fixed specification represents an advantageous procedure. The size of ΔK is z. For example, set as follows:
An actuator force application with K = ΔK without channel rollover causes vibration excitation of the cylinders 02 ; 03 , The magnitude of the total oscillation amplitudes of the relative cylinder movement resulting from this in the vibration-sensitive nipple should be clearly below the critical limit value for the generation of the oscillation strip (eg by a factor of> safety factor 5.) Since the resulting amplitudes are predicted from machine dynamic considerations Alternatively, this value can be obtained, for example, during commissioning of the machine, also by measuring the oscillation amplitudes so that, for example, not too many iterations are necessary for the starting value selection K0. the safety factor should not be too large (eg <30).

in the following iteration step will be the maximum mode amplitudes (calculated from the measured ones as described above) of each other following steps compared.

In dependence from the sign of the amplitude change, d. H. the difference between last and newly determined maximum amplitude it is then decided whether a sign change of ΔK is required and the scaling factor K of the force introduction is changed K + ΔK. This completes the iteration step i, and begins the step i + 1. The time duration for execution an iteration step is advantageous in a cylinder rotation cycle. By the choice of the size of ΔK is guaranteed, that even with speed changes with typical accelerations of »40,000 rpm / min, the minimum vibration can be held continuously.

• – die Schwingungen an allen Zylindern 02; 03 zu detektieren. Solange die Kopplungen zwischen den Zylindern 02; 03 hinreichend stark sind (die Zylindersteifheit im Vergleich zur Drucktuch-Federkonstante also klein ist), kann es sogar ausreichend sein, die Schwingungen nur an einem Zylinder 02; 03 zu detektieren, um ein hinreichend großes Messsignal zu erhalten. In der Regel wird es aber notwendig sein die Detektion an einem unmittelbar am Kanalschlag beteiligten Zylinder (d. h. einem der beiden Zylinder, die den Nipp bilden, in welchem der Kanalschlag stattfindet) durchzuführen.
• – mehr als einen Sensor 56 zur Detektion einer Mode zu verwenden, denn die Amplitudenverhältnisse im gesamten System sind bereits durch die Amplitude an einer Stelle eindeutig bestimmt. In Bezug auf den Ort der Detektion gilt, dass diese nicht in einem Schwingungsknoten der entsprechenden Messgröße liegen darf. Bei einer Wegmessung ist im Interesse eines hinreichend großen Messsignals ein Schwingungsmaximum besonders günstig. Dies wäre für die Kanalschlag-Eigenmoden etwa in Ballenmitte. Allerdings ist dieser Ort aus Bauraumaspekten, sowie in Bezug auf die Halterung (mögliche Sensor-Schwingungen) ungünstig. Bei einer nicht zu hohen Lagersteifheit ist auch eine Messung im Lager (z. B. in der Lageranordnung 06; 42) bzw. in Lagernähe möglich.
• – für jede Mode einen eigenen Sensor 56 vorzusehen, denn die Eigenmoden können durch Filtern (Bandpass) aus einem Signal erhalten werden. Problematisch ist dies allerdings dann, wenn die Eigenfrequenzen so eng benachbart sind, dass diese aufgrund der Kantensteilheit des Filters nicht getrennt werden können (bzw. das
• – Messsignal der einzelnen Mode durch zu hohe Kantensteilheit verfälscht wird). In diesem Fall bietet es sich an, die Signale zweier (oder mehrerer) Sensoren durch Bildung von Linearkombinationen der Messsignale zu verknüpfen, um die einzelnen Moden isoliert zu erhalten.

Since the channel beat eigenmodes are native oscillations, it is not necessary

• - the vibrations on all cylinders 02 ; 03 to detect. As long as the couplings between the cylinders 02 ; 03 are sufficiently strong (the cylinder stiffness compared to the blanket spring constant is so small), it may even be sufficient, the vibrations only on a cylinder 02 ; 03 to detect in order to obtain a sufficiently large measurement signal. In general, however, it will be necessary to perform the detection on a cylinder directly involved in the channel impact (ie one of the two cylinders forming the nib in which the channel impact takes place).
• - more than one sensor 56 to use for the detection of a mode, because the amplitude ratios in the entire system are already uniquely determined by the amplitude at one point. With regard to the location of the detection, this does not apply to a vibration node of the corresponding measured variable. In the case of a displacement measurement, a vibration maximum is particularly favorable in the interest of a sufficiently large measurement signal. This would be approximately in the middle of the bale for the channel beat eigenmodes. However, this location is unfavorable for reasons of space, and in terms of the holder (possible sensor vibrations). If the bearing stiffness is not too high, a measurement in the bearing (eg in the bearing arrangement 06 ; 42 ) or near the warehouse possible.
• - a separate sensor for each mode 56 provided, because the eigenmodes can be obtained by filtering (bandpass) from a signal. This is problematic, however, if the natural frequencies are so closely adjacent that they can not be separated due to the edge steepness of the filter (or the
• - Measuring signal of each mode is falsified by excessive edge steepness). In this case, it makes sense to combine the signals of two (or more) sensors by forming linear combinations of the measurement signals in order to obtain the individual modes in isolation.

to suppression of vibrations that do not belong to the channel beat eigenmodes (z. B. frame vibrations), as well as other disorders (concentricity / imbalance, Sensor noise), it is generally advantageous to have a high or band pass filter using only the channel beat eigenmodes.

In an indirect printing process (such as offset printing), in which the transfer cylinder 02 Channels, it is to minimize the number of necessary sensors 56 advantageous, the vibrations only on the transfer cylinder 02 to be detected, since this is directly involved in the channel beats in both Nipps (form cylinder transfer cylinder and transfer cylinder impression cylinder).

Due to the finite actuator stiffness, the bearing stiffness is reduced compared to conventional mounting (eg directly in the frame), so that also a measurement of the movement in the area of the bearing arrangement 06 ; 42 is possible. Alternatively, a measurement of the bearing forces (eg via strain gauges (DMS) or via the actuator 23 ; 31 ; 44 self) possible. In the case of a bending moment initiation over the pin 09 can basically z. B. also the bending moment by DMS strips on the pin 09 be detected. The signal transmission of the detection on the rotating pin 09 but then represents an increased effort.

In the case of stacked channels (channels which extend over only part of the cylinder length but are offset from one another in the circumferential direction), the detection is finally carried out at both end-face bearing points (eg bearing arrangements 06 ; 42 ) is advantageous, since by summation of the two signals, the fundamental and even harmonics, and by subtracting the first harmonic and odd harmonics can be obtained. The amplitudes of the modes contained in these two signals can then possibly be obtained again by the above-mentioned filter methods. Thus, the mode amplitudes can be determined.

• – eine große Dynamik (Anstieg/Abfall innerhalb der Kanalschlagdauer). Die Definitionen der Kanalschlag- und Aktor-Kraftverläufe mit Skalierungsfaktor K stellen „minimale" Dynamik bei vorgegebener Zeitdauer (Kanalschlagdauer) dar. Für übliche schmale Kanäle von 3 mm Breite bedeutet dies einen Anstieg/Abfall innerhalb der Kanalschlagdauer von 0.002 s, bei schnelllaufenden Maschinen auch kleiner oder gleich 0.00019 s. Treten drucktechnisch unzulässig große Schwingungsamplituden nur bei niedrigen Drehzahlen auf, können diese Anforderungen um einen Faktor 2..3 reduziert werden, d. h. die geforderte Zeit für den Anstieg/Abfall größer sein.
• – Die Kraft- und Weganforderungen hängen von der Krafteinleitungsform ab Im allgemeinen wird die Ansteuerung der Aktoren 23; 44 (31); elektrische durch eine Steuerspannung (oder Strom) erfolgen, z. B. über einen D/A-Wandler. Dann kann es günstig sein, das Übertragungsverhalten der Aktoren selbst (aufgrund der Massenträgheit (Aktor-Eigenfrequnezen) und/oder der Ansteuereinheit (Grenzfrequenz des Verstärkers) bei der Vorgabe der Steuerspannung (-strom) durch Rückrechnung bereits zu berücksichtigen, damit der gewünschte Kraftverlauf gemäß der Vorgaben auch realisiert wird.

Advantageous embodiments of the actuator 23 ( 31 ; 44 ) are:

• - a large dynamic (increase / decrease within the channel impact duration). The channel impact and actuator force curve definitions with scaling factor K represent "minimum" dynamics for a given duration (channel beat duration). For common narrow channels of 3 mm width, this means an increase / decrease within the channel impact duration of 0.002 sec, also for high speed machines Less than or equal to 0.00019 s If pressure oscillation is impermissibly large vibration amplitudes only at low speeds, these requirements can be reduced by a factor of 2..3, ie the required time for the increase / decrease to be greater.
• - The force and travel requirements depend on the force introduction form In general, the control of the actuators 23 ; 44 (31); electrical by a control voltage (or power), z. B. via a D / A converter. Then it may be favorable to already consider the transmission behavior of the actuators themselves (due to the inertia (actuator Eigenfrequnezen) and / or the drive unit (limit frequency of the amplifier) in the specification of the control voltage (current) by recalculation, so that the desired force curve according to the specifications is also realized.

The actuators to be used for active vibration damping 23 ; 31 ; 44 preferably have a very fast response time (response for one cycle> 100 Hz, especially> 300 Hz) and high stiffness.

Preferably is a path of at least 20 μm, advantageously <40 μm per actuator afford to.

Preferably, for the vibration reduction other actuators 23 ; 44 used as the drives responsible for the on / off movement (first and third examples).

For the execution of a common drive for the vibration compensation and the on-stop movement, the actuator used there must 31 for short distances have sufficiently fast reaction cycle times (second example).

As actors 23 ; 44 can instead of the mentioned piezoelectric actuators 23 ; 44 in the above examples also designed as electromagnets actuators 23 ; 44 be used.

01

Printing, Double printing

02

Cylinder, transfer cylinder, Printing cylinders

03

Cylinder, Form cylinder, printing cylinder

04

cylinder unit

05

nip point

06

Bearing arrangement, Bearing unit, linear bearing unit, bearings

07

side frame

08

side frame

09

spigot

10

channel

11

transmission

12

Radial, Cylindrical roller bearings

13

Bearing means bearing element

14

Bearing means bearing element

15

16

Pillow Block carriage

17

carrier

18

recess

19

recess breakthrough

20

drive shaft

21

Regulators, Adjusting drive, stepper motor, motor, actuator

22

wave

23

actuator, piezo actuator

24

spring element

25

26

Mounting aid, dowel

27

Holding means, screw

28

Medium, clamping screw

29

cover

30

31

actuator, Adjusting means, pistons, hydraulic pistons

32

attack

33

stop surface

34

Regulators, actuator

35

36

Element, spring element

37

Valve

38

Stop, overload protection, spring element

39

Attack, wedge

40

actuator, piezo actuator

41

Return spring

42

Bearing arrangement, Bearing unit, radial bearing, multi-ring bearing, bearing

43

Ring, intermediate ring

44

actuator, piezo element

45

46

Ring, inner ring

47

rolling elements

48

Ring, Outside

49

Ring, Inside

50

51

Radial, Plain bearing, needle roller bearings

52

outer ring

53

Bearing arrangement, Storage unit, warehouse

54

gear

55

gap

56

sensor

57

Rule- and / or control device, control

58

sensor

59

Force pattern generator

A0

fundamental

A2

mustiness

B06

width

L02

length

L03

length

L06

length

D

diameter

e

Level, Connection line, connection level

F

force

K

scaling factor

P

print

S

setting direction

LW

clear width

b _K

Width ( 10 )

b _N

Width ( 05 )

.DELTA.K

amount

β

angle

Claims (22)

Method for reducing the vibration of a cylinder ( 02 ; 03 ) of a web-processing machine, in particular rotary printing machine, by direct or indirect loading of a pin ( 09 ) of the cylinder ( 02 ; 03 ) by means of at least one actuator ( 44 ), characterized in that for vibration reduction at least one in the structure of a multi-ring bearing ( 42 ) arranged actuator ( 44 ) is applied, and that the application with respect to the timing and possibly the waveform controlled in accordance with the angular position of the relevant cylinder ( 02 ; 03 ) he follows. Method according to Claim 1, characterized in that the time profile of the activation of the actuators ( 44 ) speed dependent occurs. Method according to Claim 1, characterized in that the time profile of the activation of the at least one actuator ( 44 ) as a function of the temperature and / or the force of the cylinder ( 02 ; 03 ) and / or a characteristic size for the blanket behavior. Method according to claim 1, characterized in that that finding an optimal or sufficient signal level an adaptive control process takes place. A method according to claim 1, characterized in that a control of the at least one actuator ( 44 ) with respect to their transitions between active and inactive state with a function of parabolic or sinuidalen course. A method according to claim 1, characterized in that two with respect to a center of the multi-ring bearing ( 42 ) opposing actuators ( 44 ) are acted upon in opposite direction of action. Device for vibration reduction of a cylinder ( 02 ; 03 ) of a web-processing machine, in particular rotary printing press, with an actuator ( 44 ) for the direct or indirect application of force to the cylinder ( 02 ; 03 ) or a pin ( 09 ), characterized in that the actuator ( 44 ) in the structure of a multi-ring bearing ( 42 ) formed storage unit ( 42 ) is arranged and with a control and / or regulating device ( 57 ) is in signal connection, by means of which in response to signals of a vibration characterizing sensor ( 56 ) the actuator ( 44 ) Signals can be acted upon for control. Apparatus according to claim 7, characterized in that a the angular position of the cylinder ( 02 ; 03 ) or pin ( 09 ) detecting sensor ( 58 ) is provided, which with the control and / or regulating device ( 57 ) is in signal communication, and that the actuator ( 44 ) in response to a rotational angle position of the vibration opposing signals can be acted upon. Apparatus according to claim 7, characterized in that the at least one actuator ( 44 ) between at least two adjacent rings ( 43 ; 46 ; 48 ; 49 . 52 ) of the multi-ring bearing ( 42 ) is arranged. Device according to claim 9, characterized in that the at least one actuator ( 44 ) between two rings ( 48 ; 49 ) of a split ring ( 43 ), in particular intermediate ring ( 43 ) is arranged. Apparatus according to claim 7, characterized in that in the circumferential direction of the multi-ring bearing ( 42 ) considers several actuators ( 44 ) in the structure of the multi-ring bearing ( 42 ) trained La unit ( 42 ) are arranged. Apparatus according to claim 7, characterized in that in the axial direction of the multi-ring bearing ( 42 ) considers side by side several actuators ( 44 ) in the structure of the multi-ring bearing ( 42 ) formed storage unit ( 42 ) are arranged. Device according to claim 7, characterized in that the actuator ( 44 ) of a an on / Abstellbewegung of the cylinder ( 02 ; 03 ) Acting drive is different. Device according to claim 7, characterized in that the actuator ( 44 ) as a piezoelectric actuator ( 44 ) is trained. Device according to claim 7, characterized in that the actuator ( 44 ) with respect to its effective direction substantially in the radial direction to the pin ( 09 ) is oriented. Apparatus according to claim 11, characterized in that in the circumferential direction of the multi-ring bearing ( 42 ) considers a pair of two actuators ( 44 ) are provided, which with respect to the center of the multi-ring bearing ( 42 ) are arranged substantially symmetrically opposite. Apparatus according to claim 16, characterized in that in the circumferential direction of the multi-ring bearing ( 42 ) considers a plurality of pairs of actuators ( 44 ) are arranged. Apparatus according to claim 7, characterized in that in one of a Nippstelle ( 05 ) to a second cylinder ( 02 ; 03 ) facing half space a first actuator ( 44 ) and in the Nippstelle ( 05 ) remote half space a second actuator ( 44 ) is provided. Apparatus according to claim 18, characterized in that a plurality of second actuators ( 44 ) are provided side by side in the circumferential direction. Apparatus according to claim 18, characterized in that the first actuator ( 44 ) is formed in the manner of a circular segment extending over an angular range of 45 ° to 90 °. Apparatus according to claim 18, characterized in that between the first and second actuator ( 44 ) in the circumferential direction a gap ( 55 ) is provided. Apparatus according to claim 9 or 10, characterized in that one of the two rings ( 48 ; 49 ) Eccentric ring is formed with an eccentrically arranged bore.