EP2006097B1 - Bearing unit for a printing cylinder in a printing machine - Google Patents

Description

The invention relates to storage units for a printing cylinder of a printing press according to the preamble of claim 1.

In printing presses, especially web offset rotary presses, users' desire for increased flexibility based on a small flipping, resulting in single-circumference plate cylinders, coupled with high productivity, resulting in multi-width presses, leads to relatively flexible pressure cylinders and thus to potentially high-end machine concepts Susceptibility to vibration stripes in the printed image.

Various methods for reducing the bending deformation of rotary components can be found in the literature. The individual methods can be differentiated into passive methods and active methods. In contrast to passive methods, eg. B. constructive, temporally constant measures such as reducing the channel impact force by using very narrow cylinder channels, so-called. "Minigaps" or sleeves on the blanket cylinder, is intervened in active method depending on the machine condition, temporally variable and using additional energy in a suitable manner. Active methods can be subdivided according to their mode of action into static and dynamic methods. In static systems, the actuators are updated in longer time scales to change the boundary conditions, such. B. change of production, other consumables or temperature-related changes to compensate. By contrast, dynamic methods have significantly shorter cycle times (in the range of the natural frequencies of relevant vibration modes) in order to counteract the dynamic vibration behavior via actuators. The present invention is concerned with an active Method for the dynamic reduction of the bending vibration amplitudes.

In case of WO 01/50035 A1 as well as the JP 11 170 474 is introduced by introducing axial forces at a distance from the cylinder axis a bending moment that should compensate for the force drop when overrunning the clamping channel.

From the WO 2004/016431 A1 For example, an apparatus near the chucking surface in the cylinder surface is described that forms a radial elevation (attitude and height) for destructive interference with the channel impact force depending on the engine condition (speed).

The active vibration damping techniques described above are almost exclusively used for damping resonantly forced vibrations in machine tools where there is continuous excitation (imbalance, chatter marks, process forces). In this case, low, continuously introduced forces are sufficient for damping, which are derived from a metrological detection of the actual value and a control algorithm.

In contrast, the channel impact vibrations of printing cylinders are caused by a single per revolution or periodic, pulse-shaped excitation. The force is applied by eliminating or reducing the pressing force when the interruption of the lateral surface is overrun (eg clamping channel of the opening for receiving an elevator). Due to the very short-term impact stimulus and the requirement to almost completely suppress the first vibration, which would otherwise already be visible as a quality defect in the printed product, new concepts regarding actuator technology and control are required.

If the actuators are located in the impression cylinder, this leads to high manufacturing and assembly costs and, in addition, to cylinder rotation problems. For example, problems in connection with then required rotary unions or in connection with electronics and actuators, the high centrifugal accelerations are exposed to a maximum of 350 to 400 times the gravitational acceleration.

An additional bearing at a distance from the machine bearing for bending moment introduction leads to numerous technical problems, such. B. too low rigidity of the bearing pin for torque introduction and thus high required strokes and thus length of the actuators and collision with adjacent assemblies such as page register or drive.

From the DE 200 11 948 U1 a bearing assembly for a printing machine is known, wherein between a bearing inner ring and a bearing outer ring rolling elements are arranged and the bearing outer ring has a lateral mounting flange, with which it can be fixed to a housing. At least one piezoelectric adjusting element is arranged between the housing and the bearing outer ring, via which an exact radial positioning of the bearing lying in the micrometer range can be achieved in the housing bore, before the bearing is then fixed in the usual manner by means of screws on the housing. In the printing operation of the printing press, the bearing is thus rigidly fixed relative to the housing.

From the WO 2006/061432 A1 and the DE 10 2005 058 787 A1 are known a method and apparatus for vibration reduction of a cylinder of a rotary printing press, wherein actuators are provided in the form of piezoelectric actuators in a radial bearing receiving carriage-like bearing block of a linear bearing unit, which serve to reduce the cylinder vibrations caused by channel impacts. This publication also discloses the triggering or scaling of the Aktorsollkurve and details of the adaptive pilot concept concerning measuring points, signal conditioning, generation of the setpoint curve u. etc. ..

The invention has for its object to provide storage units for a printing cylinder of a printing press.

The object is achieved by the features of claim 1.

The achievable with the present invention consist in particular that during the printing operation by means of a suitable actuator, d. H. By means of the piezoelectric adjusting elements or piezoelectric actuators, at the bearing points of the printing cylinder, a force can be introduced which compensates for the elimination or reduction of the compressive stress when rolling over a cylinder channel, for example a clamping channel of a plate cylinder, and thus avoids vibration excitation. For this purpose, radial forces are introduced by means of the piezo actuators via the bearing in the printing cylinder, which substantially correspond in size and duration of action of the channel impact force. If the sum of the channel impact force and the actuator force is equal to zero at any time, movement of the center of gravity of the cylinder can be avoided.

The invention enables integration of a suitable actuator for moving the bearing center of the printing cylinder and a suitable measuring system for calculating the Aktorstellkurve in a pre-assembled, compact storage unit that meets the requirements for space and connecting structures of a printing cylinder in a printing press.

The compact and easy-to-install bearing unit, which is pre-assembled, adjusted, eg B. mounted by shrink fit on the shaft seat of the printing cylinder and is mounted completely with the printing cylinder to a side frame of the printing press, resulting in no collision with adjacent modules such as page register or drive; The actuators and the power electronics are mounted on the bearing housing, ie on fixed components.

By the particular orthogonal effective directions of preferably two actuators shifts of the bearing center point in a plane perpendicular to the cylinder axis allows the bearing units are thus for different types of printing units (cylinder angle or channel strike direction) can be used.

Actuator dimensions are required in the currently typical printing unit loads, which can be rounded off in the preferred cross-sectional shape of the bearing unit, that is to say the preload side is rounded and the actuator sides are square. The effective actuator length can thus be increased to approximately 50% of the cylinder radius. After the stroke is proportional to the effective length of piezo actuators Actuators relevant size can be installed, while still sufficient space for radial bearings is guaranteed.

In the case of the present invention, an integration of actuators and sensors in a compact unit in the form of a storage unit is thus possible, with maximum utilization of the available installation space. In the case of a plate cylinder, for example, a web-fed rotary printing press, such as a web-fed rotary offset printing machine, the space constraint in the radial direction essentially results from the requirement to be able to apply several inking or dampening rollers with corresponding adjustment mechanisms around the outer surface of the plate cylinder and between plate cylinder and blanket cylinder the required center distance observed.

According to a preferred embodiment of the invention, the bearing unit may comprise a side register adjustment device, which may include a thrust bearing for axially adjusting the recorded in the storage unit printing cylinder, which may be adjustable by means of a threaded device. Such a storage unit is particularly suitable for use in connection with plate cylinders.

Embodiments of the invention are illustrated in the drawings and will be described in more detail below.

Fig. 1

eine perspektivische Ansicht einer Lagereinheit, mit Blickrichtung auf die Kontaktfläche zum Seitengestell der Druckmaschine;

Fig. 2

die Lagereinheit gemäß Fig. 1 teilweise im Schnitt;

Fig. 3

die Lagereinheit gemäß Fig. 1 und 2, von der anderen Seite, also mit Blickrichtung von der Zylinderstirnfläche gesehen und teilweise im Schnitt;

Fig. 4

eine perspektivische Teilansicht einer weiteren Ausführungsform einer Lagereinheit samt Zylinder, teilweise im Schnitt;

Fig. 5

eine Schnittansicht der Anordnung gemäß Fig. 4.

Show it:

Fig. 1

a perspective view of a storage unit, looking towards the contact surface to the side frame of the printing machine;

Fig. 2

the storage unit according to Fig. 1 partly in section;

Fig. 3

the storage unit according to Fig. 1 and 2 , seen from the other side, so viewed from the cylinder face and partially in section;

Fig. 4

a partial perspective view of another embodiment of a storage unit together with cylinder, partially in section;

Fig. 5

a sectional view of the arrangement according to Fig. 4 ,

First, the first embodiment according to the Fig. 1 to 3 Referenced. The bearing unit 01 is used to hold a cylinder 02 not shown here (see. Fig. 4 ), in particular printing cylinder 02, for example, forme cylinder 02 or blanket cylinder 02 of a printing press, in particular a web-fed rotary printing press, for example a web-fed rotary offset printing press. The printing unit cylinder 02 mounted in the bearing unit 01 can in particular be a printing cylinder 02 with a single cylinder channel on the circumference. The storage unit 01 can be fastened, for example, on a side frame of the printing press, z. B. screwed, it being understood that on both sides of the cylinder 02 each have a bearing unit 01 is provided.

The bearing unit 01 comprises a bearing 03, for example, a roller bearing 03, with an axial bore 04 for receiving a pin 06 (see. Fig. 4 ) The bearing 03 includes a bearing inner ring 08, which defines the bore 04, a bearing outer ring 09 which is rotatably received in the bearing housing 07, and a recorded between bearing inner ring 08 and bearing outer ring 09 Wälzkörpersatz 10. The bearing housing 07 is firmly screwed through threaded holes 11 with a side frame of the printing press, not shown.

The bearing outer ring 09 is received in the bore 14 of the bearing housing 07 with radial play. The bearing outer ring 09 has on both sides a radially outwardly extending flange 12 and a contact shoulder 12, which extends into a correspondingly shaped, adjoining the bore 14 recess 13 on the respective end outer side of the bearing housing 07. In this way, the bearing outer ring 09 in the bearing housing 07 in the radial direction, d. H. in a plane perpendicular to the bearing axis movable, but received immovably in the axial direction due to the double-acting axial sliding of the abutment shoulders 12. The radially outwardly extending abutment shoulders 12 additionally cause a stiffening of the bearing outer ring 09, which is advantageous in view of the bending stress of the bearing outer ring 09 by the actuators 26 described below.

The bearing housing 07 is formed divisible and comprises two housing halves 16; 17, which are joined together by means of dowel pins 18 and are screwed together. The dividing plane of the two housing halves 16; Preferably, the bearing outer ring 09 is divided Peripheral portion 17 of the other housing half 17 is rectangular. The length L1 of the long side of the rectangular housing half 17 may in particular correspond to twice the radius R of the semicircular or semicircular housing half 16 and the length L2 of the short side of the rectangular housing half may in particular correspond to the simple radius R. The bearing unit 01 is used in conjunction with a cylinder 02 having an outer diameter D, wherein preferably the relationships L1 <or = D and R <or = D / 2 apply. This results in a particularly compact and easy to install construction of the storage unit 01 and sufficient space for peripheral components such as inking rollers in the case of use of the storage units 01 in connection with cylinders 02 form.

The bearing 03 or the bearing outer ring 09 is mounted as explained above with play in the bore 14 of the bearing housing 07. Around the camp 03, d. H. the outer bearing ring 09 angularly fixed relative to the bearing housing 07, but to keep movable in a plane perpendicular to the bearing axis, a rotation 19 in the form of a torsionally stiff, but flexible securing plate 19 is provided, which is annular with a ring-like portion 21 and a plurality, in particular four radially outwardly extending cranked arms 22, which preferably extend from each other at an angle of 90 °, and are preferably oriented so that two of the arms 22 extend in the direction of the two corners of the rectangular housing half 17. The annular portion 21 of the locking plate 19 is secured by screws 23 on the bearing outer ring 09, while the cranked arms 22 are fixed by screws 24 on the bearing housing 07, whereby a rotation 19 of the bearing outer ring 09 is created with simultaneous possibility of movement in the radial direction.

In the rectangular housing half 17 of the bearing housing 07 are two piezoelectric actuators 26, z. As actuators 26, for example, two piezo stack actuators 26 with integrated force plate arranged. The actuators 26 are completely received within the bearing housing 07. The actuators 26 extend The plane of each actuator 26 preferably extends perpendicular to the axis of the bearing 03 or the axis of the bearing 03 is preferably in the defined by the respective actuator 26 Level.

The two actuators 26 are arranged at an angle of 90 ° + f 10% to each other, preferably 90 ° +/- 3%, in particular of 90 ° to each other, so in each case each have a vertical direction of action. The actuators 26 act with their radially inner end on the bearing outer ring 09 in the sense of moving the bearing outer ring 09 and thus the entire bearing 03 in a radial plane and are supported at its radially outer end on the bearing housing 07. In order to achieve a decoupling of shear forces, for example, a linear guide 29, z. B. a flat cage guide 29, in particular a needle rollers or balls having needle roller flat cage 29 may be provided.

The two outer corner portions 27 of the rectangular housing half 17 are formed as detachable from the bearing housing 07 caps 27, in which the rear ends of the actuators 26 are encapsulated and supported by synthetic resin. The caps 27 in turn are fastened by means of screws 28 to the rectangular housing half 17.

After high dynamic forces must be introduced into the bearing 03, a short power path and a rigid connection is of great importance: via the actuators 26, the forces are directly over the stiffened by the flanges 12 bearing outer ring 09 in the center plane (therefore no torque input by Aktorkraft ) of the rigid bearing point initiated (the central axis of the actuator 27 is within the Wälzkörperbreiten and / or the working width of the rolling bearing 03); the actuators 26 are based on the bearing housing 07 directly from the rigid side frame of the printing press; to compensate for length or angle tolerances, the actuators 26 on the front side in each case an intermediate element 29 for transverse force coupling to the z. B. needle rollers having flat cage guide 29 is pressed and the back is set on each a spacer between the cap 27 and the bearing housing 07, an adhesive gap, which is poured with epoxy resin.

Transverse forces lead to the destruction of the piezo stack. After the actuators arranged at 90 ° allow the movement in the plane, but thus also displacements of the outer ring occur orthogonal to the actuator center axis, here by a suitable linear guide 29 (preferably Nadelrollenflachkäfige 29) to provide decoupling.

The two actuators 26 opposite, preferably diametrically opposite each a biasing means 31 is provided which counteracts the force of the actuators 26. The biasing device 31 may in particular be formed by a spring device 31, for example by a cup spring assembly 31, which is arranged in the half-round housing half 16, radially aligned, is supported with its radially outer rear side on the housing half 16 and with its radially inner front acting on the bearing outer ring 09, wherein for decoupling of transverse forces turn a flat cage guide 29 may be provided. Preferably, the biasing force of each spring means 31 is adjusted so that the spring means 31 biases its associated piezoelectric actuator 26 with a force corresponding to half the maximum actuating force of the control element 26.

The method for reducing oscillation amplitudes of the bending modes of a printing cylinder 02 is, generally speaking, essentially that at least one bearing point of the printing cylinder 02, preferably at both or all bearing points, a dynamic Fußpunktverschiebung occurs. This dynamic Fußpunktverschiebung takes place in particular by means of at least one piezoelectric Actuator 26 and Aktors 26th

In operation, the actuators 26 by means of a suitable control or regulation, as in principle, for example, from the above-mentioned WO 2006/061432 A1 is known, energized in the required manner to initiate a force in the bearing 03, which counteracts the forces acting on the mounted cylinder 02 forces, for example when rolling over a clamping channel, or compensates for this, to avoid vibration excitations as possible.

However, the different points of application of force may result in flexural deformation of the flexible cylinder 02 about the center of gravity. Thus, while the fundamental can be fully compensated with its maximum in the middle of the bale of the cylinder 02, the second harmonic, which has its maximum at the bearings can be excited by the proposed actuator. In order to solve this problem, it may be preferable to proceed in such a way that a compromise with respect to the amplitudes of the two eigenmodes is aimed for via a suitable control, cf. also WO 2006/061432 A1 ,

The existing clearance or gap between the radially outer bearing outer race 09 and the bore 14 of the bearing housing 07 restricts the maximum deflection of the actuators 26 in the event of overload (eg, in a winder) and thus prevents destruction and / or depolarization the actuators 26 in case of overload. The arrangement of the actuators 26 explained above also leads to an avoidance of transverse forces or bending moments on the actuators 26.

The occurring (high) forces in the case of z. As a paper winder lead to the depolarization of the actuator and thus make the actuator useless. Thus, an optimal gap between the outer ring and housing is required, which is large enough to the maximum Aktorhub (here about 45 microns) - taking into account manufacturing / assembly tolerances - to realize, is small enough to limit the maximum Aktoreinfederung (permissible (F.max-F.block) * C.aktor, here about 32 microns in ideal rigid environment). After the conversion parts have a finite rigidity, the gap was here dimensioned to 65 microns. The game is preferably 10 - 500 microns, in particular 20 - 100 microns.

• steife Ankopplung der Aktoren 26 zwischen Zylinder 02 und Seitengestell (die Piezo-Stackaktoren 26 können als Feder mit Fußpunktanregung modelliert werden, d. h. jede zusätzliche Nachgiebigkeit reduziert die eingekoppelte Kraft);
• geometrische Zusammenhänge Aktorlänge/Aktorhub vs. geringe Achsabstände (= Maximalgröße des Lagers) bei Einfachumfangmaschinen und Schwächung des Lagergehäuses 07 und ausreichend dimensioniertes Wälzlager 03;
• Sicherstellung der Lebensdauer des Zylinderlagers trotz zusätzlicher Aktorkräfte durch optimierte Gestaltung des Außenrings;
• die fertigungs- und montageoptimierte Gestaltung der Lagereinheit 01;
• die Möglichkeit der Ausführung der Lagereinheit 01 als Plattenzylinderlager mit integriertem Seitenregister (vgl. unten) und optimierter Außenkontur zur Anordnung von Farbwalzen.

Further features of the solution can be seen in the following points:

• rigid coupling of the actuators 26 between cylinder 02 and side frame (the piezo stack actuators 26 can be modeled as a spring with Fußpunktanregung, ie any additional compliance reduces the coupled force);
• geometric relationships actuator length / actuator stroke vs. small center distances (= maximum size of the bearing) with single-circumference machines and weakening of the bearing housing 07 and sufficiently sized bearings 03;
• Ensuring the service life of the cylindrical bearing despite additional actuator forces through optimized design of the outer ring;
• the production and assembly-optimized design of the storage unit 01;
• the possibility of the execution of the bearing unit 01 as a plate cylinder bearing with integrated side register (see below) and optimized outer contour for the arrangement of ink rollers.

The second embodiment according to Fig. 4 and 5 is essentially the same as in Fig. 1 to 3 , However, additionally has a built-in storage unit 01 side register adjustment device 32, the axial displacement of the printing cylinder 02, z. B. forme cylinder 02, in particular plate cylinder 02 for Correction of the page register enabled. For this purpose, the pin 06 of the forme cylinder 02 is non-rotatably connected to a pin extension 33, which carries a further bearing 34, namely a thrust bearing 34, for example a thrust ball bearing 34, the housing 36 at its outer periphery with a thread 37, in particular a fine thread 37, For example, a metric fine thread 37 is provided, which meshes with a corresponding thread 38 of a fixed flange 39 which is rotatably connected to the bearing outer ring 09, in particular screwed. A rotation of the housing 36 of the thrust bearing 34 thus causes an axial translational movement of the housing 36 and thus ultimately of the cylinder 02. The possible adjustment range here can be about +/- 1.5 mm.

On the housing 36 of the thrust bearing 34, a ring gear 41 is further mounted, which is rotatable via an additional drive gear 42, in particular spur gear 42 via a drive shaft 43 to the o. G. To generate translational movement of the cylinder 02.

Even assuming a low efficiency η = 20% of the gear ratios results in a favorable ratio between torque M and Axialverschiebekraft F _ax of approx. $$\mathrm{M}\left[\mathrm{nm}\right]\mathrm{:}{\mathrm{F}}_{\mathrm{ax}}\left[\mathrm{N}\right]\mathrm{=}\mathrm{1}\mathrm{:}\mathrm{2500.}$$

Und mit $$M=F_{\tan }*d_m$$

gilt: $$M=\frac{p}{2\pi *\eta *i}*F_{\mathit{ax}}$$

The gearing is considered as an inclined plane, where the following relationships for forces and angles apply: $$\tan \left(\phi \right)=\frac{F_{\tan }}{F_{\mathit{ax}}}\tan \left(\phi \right)=\frac{p}{d_m*2\pi }$$

And with $$M=F_{\tan }*d_m$$

applies: $$M=\frac{p}{2\pi *\eta *i}*F_{\mathit{ax}}$$

In the above relationships: p is the pitch of the thread 37, d _{m is} the mean thread diameter, and i is the gear ratio of the gear transmission (assumed here i = 1: 3.75). For example, to achieve an axial displacement force of 1,000 N, a torque of 0.42 Nm is required.

It should be noted important in this adjustment that the fixed flange 39, in which the drive gear 42 is mounted, is firmly connected to the movable by the actuator bearing outer ring 09. Thus, a clamping of the adjustment is avoided by the Aktorhub.

In a further preferred, unspecified embodiment of the bearing unit 01 as a rubber cylinder bearing, the integration of a macroscopic position adjustment for pressure and rest position of the blanket cylinder 02 is possible, see. also WO 2006/061432 A1 ,

LIST OF REFERENCE NUMBERS

01

storage unit

02

Cylinder, printing cylinder, forme cylinder, plate cylinder, rubber cylinder

03

Bearings, Rolling Bearings

04

Bore (03)

05

-

06

Cones (02)

07

bearing housing

08

Bearing inner ring

09

Bearing outer ring

10

rolling element

11

threaded hole

12

Flange, contact shoulder (09)

13

Recess (07)

14

Bore (07)

15

-

16

Case half, semicircular, peripheral portion

17

Case half, rectangular, peripheral section

18

dowel

19

Anti-rotation lock, locking plate

20

-

21

Section, annular (19)

22

Arm (19)

23

screw

24

screw

25

-

26

Actuator, actuator, piezo stack actuator

27

Corner section, cap

28

screw

29

Linear guide, intermediate element, flat cage guide, needle roller flat cage

30

-

31

Biasing device, spring device, plate spring package

32

Side register adjustment device

33

Zapf extension

34

Bearing, Thrust Bearing, Thrust Angular Contact Ball Bearing

35

-

36

Housing (34)

37

Thread, fine thread (36)

38

Thread (39)

39

flange

40

-

41

sprocket

42

Drive gear, spur gear

43

drive shaft

D

Outside diameter (02)

R

Radius (16)

L1

Length (17)

L2

Length (17)

Claims (62)

1. Bearing unit (01) for a printing unit cylinder (02) of a printing press, having a bearing (03) and a bearing housing (07), incorporating the bearing (03), the bearing (03) comprising a bearing outer ring (09), a bearing inner ring (08) and a roller body set (10) incorporated between the bearing outer ring (09) and bearing inner ring (08), and at least one piezoelectric control element (26) being provided between the bearing housing (07) and the bearing outer ring (09), the bearing outer ring (09) being movably arranged in the bearing housing (07) in a plane perpendicular to the axis of the bearing unit (01) in the printing operation of the printing press at least by means of the at least one piezoelectric control element (26), a side register adjusting device (32) being arranged in the bearing unit (01), characterised in that a transverse force-decoupling intermediate element (29) is arranged between the bearing outer ring (09) and the control element (26).
2. Bearing unit according to Claim 1, characterised in that at least a part of the side register adjusting device (32) is movably arranged by means of the piezoelectric control element (26).
3. Bearing unit according to Claim 1, characterised in that the bearing unit (01) comprises two piezoelectric control elements (26), which seen with respect to the bearing axis are arranged relative to one another at an angle of 90° +/- 10%.
4. Bearing unit according to Claim 3, characterised in that the piezoelectric control elements (26) are arranged with respect to one another at an angle of 90° +/- 3%.
5. Bearing unit according to Claim 1, characterised in that a spring device (31) is assigned to the at least one piezoelectric control element (26).
6. Bearing unit according to Claim 5, characterised in that the spring device (31) is arranged opposite to the assigned piezoelectric control element (26).
7. Bearing unit according to Claim 6, characterised in that the spring mechanism (31) is diametrically opposed to the assigned piezoelectric control element (26).
8. Bearing unit according to Claim 5 or 6, characterised in that the spring device (31) is formed from a disc spring package (31).
9. Bearing unit according to one of Claims 5 to 8, characterised in that the spring device (31) pretensions the piezoelectric control element (26) assigned to it with a force which corresponds to half the maximum control force of the control element (26).
10. Bearing unit according to Claim 1, characterised in that the plane of the piezoelectric control element (26) extends perpendicularly to the axis of the bearing unit (01).
11. Bearing unit according to Claim 1, characterised in that the central axis or force transmission lies in the same direction of the control element (26), preferably within the gap width of the roller body set (10).
12. Bearing unit according to one of Claims 1 to 9, characterised in that the axis of the bearing unit (01) lies in the plane defined by the piezoelectric control element (26).
13. Bearing unit according to Claim 1, characterised in that the piezoelectric control element (26) is included completely within the bearing housing (07).
14. Bearing unit according to Claim 1, characterised in that the bearing housing (07) comprises several housing parts (16; 17).
15. Bearing unit according to Claim 14, characterised in that the bearing housing (07) comprises two housing halves (16; 17).
16. Bearing unit according to Claim 1, characterised in that the bearing housing (07) of the outer ring (09) is split.
17. Bearing unit according to Claim 15, characterised in that a dividing plane of the two housing halves (16; 17) runs through the axis of the bearing unit (01).
18. Bearing unit according to Claim 14, 15 or 17, characterised in that the two piezoelectric control elements (26) are arranged in one housing part (17) of the housing parts (16; 17) and the two spring devices (31) are arranged in the other housing part (16) of the housing parts (16, 17).
19. Bearing unit according to one of Claims 15 to 18, characterised in that the two housing halves (16; 17) can be connected to one another by means of dowel pins (18).
20. Bearing unit according to Claim 1, characterised in that the bearing housing (07) has a round housing half (16) seen in the direction of the axis and a further housing half (17) adjacent thereto.
21. Bearing unit according to Claim 20, characterised in that the round housing half (16) extends over an angle range of preferably 180°.
22. Bearing unit according to Claim 20 or 21, characterised in that the diameter (D) of a printing unit cylinder (02) incorporated by the bearing unit (01) corresponds to the diameter of the round housing half (16) or is smaller than this.
23. Bearing unit according to Claim 15, characterised in that one housing half (16) of the two housing halves (16; 17) contains the round peripheral section (16) and the other housing half (17) contains the other peripheral section (17).
24. Bearing unit according to Claim 5 and according to Claim 23, characterised in that the spring devices (31) are arranged in the housing half (16) with the round peripheral section (16) and the piezoelectric control elements (26) are arranged in the other housing half (17).
25. Bearing unit according to Claim 24, characterised in that the other housing half (17) has an at least essentially rectangular peripheral section (17).
26. Bearing unit according to Claim 20, characterised in that the other peripheral section (17) is at least essentially rectangular.
27. Bearing unit according to Claim 25 or 26, characterised in that the length (L1) of the side of the rectangular peripheral section (17) opposite to the round peripheral section (16) corresponds to the diameter (D) of a printing unit cylinder (02) incorporated by the bearing unit (01) or is smaller than this.
28. Bearing unit according to Claim 1, characterised in that the piezoelectric control element (26) is supported by means of a cap (27) on its rear side turned away from the bearing outer ring (09).
29. Bearing unit according to Claim 28, characterised in that the cap (27) is designed as a detachable part of the bearing housing (07).
30. Bearing unit according to Claim 28 or 29, characterised in that the rear of the piezoelectric control element (26) is cast in the cap (27).
31. Bearing unit according to Claim 28 and according to Claim 26, characterised in that the cap (27) forms a corner section of the rectangular peripheral section (17) of the bearing housing (07).
32. Bearing unit according to Claim 1, characterised in that the bearing unit (01) is designed to be fixable to a side frame of the printing press.
33. Bearing unit according to Claim 32, characterised in that the bearing housing (07) is designed to be screwable to the side frame.
34. Bearing unit according to Claim 1, characterised in that the bearing outer ring (09) is incorporated in the bearing housing (07) with radial play.
35. Bearing unit according to Claim 34, characterised in that the play is 10 - 500 µm.
36. Bearing unit according to Claim 34, characterised in that the play is 20 - 100 µm.
37. Bearing unit according to Claim 1, characterised in that the bearing outer ring (09) is held securely against twisting on the bearing housing (07).
38. Bearing unit according to Claim 37, characterised in that a torsionally stiff (19) securing plate (19) is provided, which, on the one hand is firmly connected to the bearing outer ring (09) and on the other hand to the bearing housing (07).
39. Bearing unit according to Claim 38, characterised in that the securing plate (19) has an internal annular section (21) and arms (22) extending outwardly therefore.
40. Bearing unit according to Claim 39, characterised in that the arms (22) are of cranked design.
41. Bearing unit according to one of Claims 38 to 40, characterised in that the torsional securing plate (19) is pliable.
42. Bearing unit according to Claim 1, characterised in that the bearing outer ring (09) has a radially outwardly extending flange (12) on its two axial ends.
43. Bearing unit according to Claim 42, characterised in that the radially outwardly extending flange (12) is incorporated in a corresponding opening (13) of the bearing housing (07).
44. Bearing unit according to Claim 1, characterised in that the side register adjusting device (32) comprises an axial bearing (34) for the axial adjustment of the printing unit cylinder (02) incorporated in the bearing unit (01).
45. Bearing unit according to Claim 1, characterised in that the side register adjusting device (32) has a drive (37, 38).
46. Bearing unit according to Claim 45, characterised in that the drive (37, 38) has a threading device.
47. Bearing unit according to Claim 45, characterised in that the drive (37, 38) is movable by means of the piezoelectric control element (26).
48. Bearing unit according to Claim 45, characterised in that the axial bearing (34) is adjustable by means of a threading device (37, 38).
49. Bearing unit according to Claim 48, characterised in that an outer drive (37) of the axial bearing (34) engages with a drive (38) connected to the bearing outer ring (09).
50. Bearing unit according to Claim 49, characterised in that a flange (39), on which the drive (38) is arranged, is rigidly fixed to the bearing outer ring (09).
51. Bearing unit according to one of Claims 44 to 50, characterised in that the side register adjusting device (32) comprises a gear device (41, 42, 43) for axial adjustment.
52. Bearing unit according to Claim 51, characterised in that the axial bearing (34) has a gear rim (41), which engages with a drive gearwheel (42).
53. Bearing unit according to Claim 51 or 52, characterised in that the gearwheel device (41, 42, 43) comprises a drive shaft couplable to a drive (43).
54. Bearing unit according to Claim 1, characterised in that the bearing unit (01) is designed as a bearing unit (01) of a plate cylinder (02).
55. Bearing units according to Claim 1, characterised in that the bearing unit (01) is designed as a bearing unit (01) of a printing unit cylinder (02) with a single cylinder channel on the circumference.
56. Bearing unit according to Claim 55, characterised in that the bearing unit (01) is designed as a bearing unit (01) of a printing unit cylinder (02), having a number of cylinder channels on the circumference.
57. Bearing unit according to Claim 1, characterised in that the bearing unit (01) is designed as a bearing unit (01) for a printing unit cylinder (02) of a fed rotary printing press.
58. Bearing unit according to Claim 1, characterised in that the intermediate element (29) contains needle rollers or balls.
59. Bearing unit according to Claim 1, characterised in that the side register adjusting device (32) is integrated into the bearing unit (01).
60. Bearing unit according to Claim 1, characterised in that at least parts of the side register adjusting device (32), together with the bearing unit (01) are separable and/or can be taken out of a side frame of the printing press.
61. Bearing unit according to Claim 60, characterised in that at least the drive of the side register adjusting device (32), together with the bearing unit (01), are separable and/or can be taken out of a side frame of the printing press.
62. Bearing unit according to Claim 1, characterised in that the bearing inner ring (08) is movable relative to the bearing outer ring (09) by means of the side register adjusting device (32).

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