Title of Invention

A ROTATING CYLINDERS OF A PRINTING PRESS

Abstract

The invention relates to a drive unit of a rotating component (06; 07) of a printing press, said component (06; 07) being disposed on lateral frames (11; 12) by means of a bearing assembly (14) so as to be movable in one direction, perpendicular to the axis of rotation of the component (06; 07). The component (06; 07) is rotatably driven by an independent driving motor (81) while a journal (21; 22) of the component (06; 07) does not penetrate an alignment of the lateral frame (11; 12) in the mounted state. A rotor (84) of the driving motor (81) is joined to the journal (21; 22) of the component (06; 07) in a torsion-proof, detachable manner. The bearing assembly (14) is provided with a movable bearing block (34) for accommodating the journal (21; 22) of the component (06; 07), which is located on the inside of the bearing assembly relative to the alignment of the lateral frame (11; 12). A stator (86) of the driving motor (81) is rigidly and removably connected to the movable bearing block (34).

Full Text

Description Rotating cylinders of a printing machine with end sided necks. The invention refers to rotating cylinders of a printing machine with end sided necks as per generic term of claims 1 or 2. Through the EPO 699 524 Bl drive pullings of printing units are revealed in doing so in an execution a single drive of the printer cylinder takes place through a single motor. In a design of the drive motor the rotor carrying the windings is movable axially opposite to a rack fixed stator. The DE 195 34 651 Al reveals a printing unit with cylinders lying in one plane, in doing so three from four cylinders are supported movable linear along cylinder plane for print-on or rather print-off position. On a front side of the cylinders their bearing takes place in jaws traversable away from each other, which from their side are rested on carriers which are supported on guide items assembled on the rack internal wall. The cylinders through pressure medium operated working cylinders are on-/off adjustable to each other and are rotatable in each case through drive motor. The stators of adjustable cylinders are assembled at the respective bearing holding device, the rotors are assembled on respective cylinder necks. On one of both rack sides the cylinder neck does not appear to penetrate the alignment of the side rack. On the machine side showing the jaws, the jaws admitting the necks with regard to the alignment of the side rack appear to be assembled on the internal side. In the WO 02/08 1218 A2 individual linear bearings for two transmission cylinders supported each in slide are known, in doing so the slide is rested on an input which comes out in direction cylinder from the alignment of the side rack. The drive of the cylinder takes place pair wise or individually through internal drive motors, in doing so the motor can be rack fixed in represented execution and can not be designed carried along in more closely represented way. Through the WO 03/025 406 Al a bearing assembly for cylinder is revealed in which one slide enclosing a linear guide is movable through an actuator assembled on the rack. The EP 1175 300 Bl shows a flexo printing machine with a plate cylinder driven directly on the neck, in doing so the motor is rested on a sliding item which is assembled on a carrying shoulder of the machine rack. Through the WO 98/06 581 Al a drive of a cylinder is revealed whose cylinder neck projecting in the alignment of the side rack via a coupling as for example a balancing coupling is combined with the rotor shaft of the drive motor. The stator is preferably assembled at an eccentric cam in which the cylinder neck is supported for the purpose of bearing change of cylinder axle. The EP 1052 093 A2 reveals a drive of a printer cylinder, in doing so a rotor is combined directly with the stub axle of the cylinder. The stator is combined via a 1 follow-up equipment with the side rack. The drive motor is design wise built as inserted motor, which can be executed as 3- phase current servomotor in synchronous design with permanent magnets. The EP 1052 093 A2 shows however no closer specific positioning direction, no cylinder neck which does not penetrate the alignment of the side rack, no cylinder whose length together with both necks is smaller / equal to clear span, no stator of the motor combined firmly in such way to the bearing block so that it moves along in adjustment and also no stator movable in axial direction and no execution with rotor movable axially relative to the rotating component. In the EPO 722 831 A2 like wise a drive of a printing unit cylinder is revealed, in doing so a rotor is combined directly with the stub axle of the cylinder. The rotor is movable together with the rotating component relative to the side rack. The stator is combined via a follow-up equipment with the side rack, in doing so via an additional linking equipment the eccentric disk carrying the stator may be coupled to each other firmly optionally, with an eccentric disk carrying the drive shaft. In not more closely described execution - in order to follow up the stator for maintaining of a sufficient air gap - a linear motor can engage on a supported stator shiftable axially. The EPO 722 831 A2 shows however like wise no closer specified positioning direction, no cylinder neck, which does not penetrate the alignment of the side rack, no cylinder whose length together with both necks is less in length to the clear span, no drive motor designed as synchronous motor with permanent magnet activation and no execution with axially movable rotor relative to the rotating component. The DE 102 19903 Al reveals a friction cylinder, in doing so a rotor of a motor driving the friction cylinder is fixed on the cylinder neck and it's stator is fixed on the wall. The assignment lies at the base of the invention, to provide rotating cylinder of a printing machine with end sided necks simply built and yet powerful drives. The assignment is solved as per invention through the features of claim 1 or 2. The advantages to be obtained with the invention comprise in particular therein, mat a specially simple drive of an individually driven, movably rested rotation body of the printing machine is found. Through the special assembly of the bearing, the short neck and the detachable assembly of the motor on the movable bearing block or the side rack, the erection and the design is specially simple and serves over and above the vibration minimizing. Further in special execution through permanent magnet activated motors a specially stronger drive of the rotation body is achieved in small dimensions. In an advantageous execution, in which a motor internal bearing between stator and rotor can be dispensed with, the motor is specially simple designed and / or with regard to wearing parts specially requires little maintenance. In an advantageous execution as permanent excited motor the motor is designed with specially high drive capacity at simultaneously small structure size. Further to this, 2 herein electrical transmission media as for example sliding contact on a rotating component as for example the rotor are dispensed with when the rotor for the formation of magnet field has instead of electro-magnetically excited coils permanent magnets. Through an input of linear guides for the printer cylinders an ideal assembly position of the cylinders in relation to possible cylinder vibrations is reached. In addition through the cylinder bearing in linear guides minor actuator travels are realized and therefore also no synchronous spindle is required. The expensive assembly of three- ring bearing is dispensed with. The bearing inside on the side racks allows in addition to the simple assembly also the shortening of cylinder neck which is also effective as vibration reducer and also space saver. In the execution as per invention with the stator assembled on movable bearing block a simple coupling of cylinder and motor is provided. The further development of the linear bearing with movable stops makes possible a print relevant adjustment of the cylinder and further to this an automatic base adjustment- for a new configuration, a new off-set blanket etc. Execution examples of the invention are represented in the drawings and are described closer in the following They show: Figure 1 : a schematic representation of a printing unit Figure 2 : a first operating position of a first execution of a printing unit. Figure 3 : a second operating position of a first execution of a printing unit Figure 4 : a schematic representation of the modularity of a printing unit Figure 5 : a plan view of a double printer. Figure 6 : a schematic longitudinal section through a bearing unit. Figure 7 : a schematic cross section through a bearing unit Figure 8 : a magnified representation of the linear bearing out of Figure 6. Figure 9 : a coupling of a cylinder to a page recording drive. Figure 10: a coupling, not belonging to the invention, of a drive motor to a cylinder 3 Figure 11 : an execution not belonging to the invention for the drive of a printer Figure 12 : an execution for the coupling of a drive motor to a cylinder Figure 13 : a schematic 3-D representation of a rotor Figure 14 : a further schematic representation of a stator Figure 15 : a variant of the drive motor from Figure 12 not belonging to the invention Figure 16 : a variant of the drive motor from Figure 12 not belonging to the invention Figure 17: a variant of the drive motor out of Figure 12 not belonging to the invention Figure 18 : a variant of the drive motor from Figure 12 not belonging to the invention Figure 19 : a variant of the drive of a rotation body in particular cylinder not belonging to the invention. Figure 20 : a variant of the drive of a rotation body in particular cylinder not belonging to the invention Figure 21 : a drive motor adjacent to an axially shifted assembly. Figure 22 : a segmented, execution of the drive of a rotation body in particular cylinder not belonging to the invention Figure 23 : variants of a segmented drive motor with axle parallel assembly. Figure 24 : variants of a segmented drive motor with axle vertical assembly not belonging to invention. Figure 25 : variants of a segmented drive motor with axle vertical assembly Figure 26 : variants of a segmented drive motor with axle vertical assembly not belonging to the invention. Figure 27 : assembly of drive motor adjacent to stator segment Figure 28 : a design of a stator segment for a movable component not belonging to the invention. Figure 29 : variants for the control of stator segments 4 Figure 30 : a further execution for the coupling of the drive motor to a rotating component with integrated axial drive. Figure 31 : a basic diagram of a printing machine Figure 32 : a front view of a roller changer. Figure 33 : a folded structure Figure 34 : a schematic diagram of a folding device. Figure 35 : a second execution of a folding device. Figure 36 : a third execution of a folding device. Figure 37 : an execution example of a drive of a printing machine. A printing machine, as for example reel fed rotary press, in particular a multi ink reel fed rotary press shows a printing unit 01 in which a print material 02, as for example a material path 02, short path 02 both side wise single or in particular in series both side wise in multiple as for example here four times or yet more number of paths at the same time may be printed in single way or in multiple ways through printer 04. Also one or more number of printing units 01 or rather printers 04 can be planned, in which one path 02 on the print position 05 is printable only one sided. The printers 04 have printer cylinders 06, 07 which are to be adjusted in print-on pair wise to each other. The solutions shown in the following can also be applied advantageously to printer 04 in which the print material 02 is designed not as path shaped but as arch. Now it is advantageous that one or more number of printer cylinders 06, 07 and/or other rotating components - an internal, at least mechanically independent from other printers 04 or rather other aggregates - have drive motor (see below). This is preferably assembled mainly co-axially to the printer cylinder 06, 07 and in advantageous execution is coupled without intermediately connected gears to the printer cylinders 06; 07. The execution and coupling of the drive motor can be designed in manifold ways and is described closer below. Like wise these executions can be input in printers 04 or rather printing units 01 or also for other driven rotating components of most different design, in doing so in the following the input is described with the help of an advantageous execution of a printing unit 01 or rather advantageous design of a printer 04. The printing unit 01 shows in the example present here multiple number (in present case four) of vertically one above the other assembled double printers 03 for the both sided print in rubber-against-rubber-operation. 5 The double printer 03-here in shape of bridges-or-n-printers represented - are built in each case through two printers 04, which show each cylinders 06; 07 as for example printer cylinders 06; 07 designed one as transmission cylinder 06 and one as plate cylinder 07 as well as in each case one inking unit 08 and in case of wet off set print additionally a moist unit 09. In each case between the both transmission cylinders 06 in adjustment position a (double-) print position 05 is built. The mentioned components are denoted only on top most double printer 03 of Figure 1, in doing so the (double-) printers 03, 04 assembled one above the other however mainly - in particular in the design of the features relevant for the invention - are executed identically. The double printers 03 - without the advantageous features of linear assembly described below - can be equally well executed against the representation in Figure 1 as U-unit opening upwards. As described to Figure 2 and 3 the printing unit 01 can be executed in an advantageous execution as for example centrally that means in the area of double print positions 05 or yet as represented in Figure 4, between plate cylinders 07 and inking unit 08 divisible operationally. In the upper double printer 03 of Figure 2 exemplany bearing assembly 14 are represented which - as for example for the purpose of on-/off positions-makes possible a movement of the respective cylinder 06; 07 in a direction vertical to it's rotation axle. This can in principle be an eccentric bearing assembly, a lever assembly or else in advantageous execution (see below) a linear bearing assembly, as for example a bearing unit 14. As likewise indicated as example in Figure 2 and 4, the ink units 08 (and if required moist units 09) can be designed as module having already multiple number of rollers with internal rack 16 or rather a frame structure 16 and can be designed as pre- erectable module applicable in the print unit 01. As explained below more in details, the cylinders 06, 07 with bearing units 14 allocated to them can be designed as pre- erectable or rather pre-erected cylinder units 17. In advantageous execution the rotation axles of the printer cylinders 06, 07 of a printer 04 can be executed in print-on mainly lying in a common plane E. The plane E takes in as for example an angle between 76° and 87°, in particular between 80° and 85° to the plane of the entering path 02. In the following Figures 2 and 3 an advantageous execution of the printing unit 01 is represented in doing so this in the area of their double print positions 05, operation point of view, that means for set-up-and maintenance purpose (in contrast to disassembly or rather a demolition), is executed divisibly. Both the parts separable from each other are denoted here with part print units 01.1 and 01.2. For this the printer cylinders 06, 07 of multiple number (four) of double printers 03 assembled one above the other, are rested rotatably in or rather on a right and a left rack-or rather wall section 11:12 as for example side rack 11, 12 in the way that both the printer cylinders 06,07 of a same printer 04 are allocated to the same rack or rather 6 wall section 11, 12. Preferably the printer cylinders 06, 07 of more number, in particular of all printers 04 printing the path 02 on the same side are rested on the same rack-or rather wall section 11,12. Printer cylinders 06; 07 can be supported in principle only one sided, that means over hung on only just one front sided rack section 11. Favourably however per part print unit 01.1; 01.2 two front sided rack sections 11; 12 assembled to the cylinders 06; 07 are planned. Both the part print units 01.1 and 10.2 separable from each other have the respective rack sections 11,12 and printer 04 (printer cylinder 06; 07 and inking unit 08 as well as if required moist unit 09). The part print units 01.1; 01.2 are movable along a direction vertical to the rotation axle of the cylinders 06; 07, one on top of other towards or rather away from each other in which one from both preferably space fixed (here part print unit 01.1) that means as for example on a floor 13 of the printing unit space, on a space fixed carrier 13, on a fitting plate 13 or on a fitting frame 13 for the printing unit 01 is stationarily rested and the other (here part print unit 01.2) movably is rested against the floor 13 or rather carrier 13 or rather fitting plate 13 or fitting frame 13 (in the following carrier 13). For this the external rack sections 12 are rested corresponding to each other, in not represented bearing items of the rack section 12 and of the carrier 13, as for example forming jointly a linear guide 15. These can be executed as rolls running on rails or else also as slide-or rolling element supported linear guide items allocated to each other. Preferably the wall sections 11; 12 are designed such that they are designed in their operating position A (Fig 2) on their side turned to each other pair wise in mainly shape complementary to each other and driven together on their separating lines or rather joint lines yet form mainly a closed side front. Figure 3 shows a maintenance position B of the printing unit 01 (without the bearing units 14 indicated in Figure 2), in doing so the relative position of the part print units 01.1; 01.2 to each other is caused through movement of rack sections 12. The relative position can also be basically reached in another execution in which both the part print units 01.1; 01.2 or rather their rack sections 11; 12 are movably rested. In a variant (Figure 4) of a divisible printing unit 01 the side rack 11; 12 is not divisible in the way that the printer cylinders 06; 07 are separated at the print position 05, but the printer cylinders 06; 07 in rather on a joint side rack 11; 12 are supported not divisibly, while to both sides the wall section 18 admitting the ink unit 08 may be brought up in an operating position A (not represented) or a maintenance position & (represented). The division takes place here between plate cylinder 07 and ink- as well if required moist unit 08; 09. Plate-and transmission cylinder 07; 06 can be designed in an advantageous format design with roll barrel length of at least four as for example four or also for specially high production push six, print pages in news paper format in particular, in broad 7 sheet format existing assembled side by side. Thus a double wide path 02 side by side with four or rather one three times wide path 02 side by side with six newspaper pages can be printed and the plate cylinder 07 corresponding with four or rather six printing blocks, in particular with their ends aligned to each other can be assigned side by side. In a first format design the cylinders 06, 07 show a circumference which mainly corresponds to two one after the other assembled print pages in a newspaper format, in particular in the broad sheet format. In the executions of the printing unit 01 with plate cylinders 07 double large formats (two newspaper pages in the circumference one after the other) shows this in advantageous way two channels in circumference direction shifted around 180° to each other for admission of printing blocks, which preferably are designed via the totally effective roll barrel length through out The plate cylinder 07 can be fitted then with four or rather six print blocks side by side and each two print blocks one behind the other. The transmission cylinder 06 shows in double large format (two newspaper pages in the circumference one after the other) in an execution as for example only one channel for admission of one or more number of off-set blankets assembled side by side which is designed preferably over the entirely effective roll barrel length, through out. The transmission cylinder 06 can then be fitted with one off-set blanket going through via roll barrel length and reaching over mainly the full circumference or with two or three off-set blankets side by side reaching over mainly the full circumference. In another execution of double large transmission cylinders 06 this can have two or three off-set blankets side by side, in doing so these are shifted to each other around 180° in circumference direction. These off-set blankets shifted to each other can be held in two or rather three channel sections, which likewise are shifted in longitudinal direction of the cylinder 06 side by side, the respectively adjacent channel section, however around 180° to each other in circumference direction. In another execution the cylinders 06; 07 however also with single circumference- a print page in particular newspaper page in circumference direction-can be designed. Also the transmission cylinder 06 with double circumference and the plate cylinder 07 with single circumference can be designed. In the printers 04 for the job printing the cylinders 06; 07 can be designed with circumference which corresponds to four lying tabloid pages. Basically the ink unit 08 can be designed in different way. It can be designed as represented as an example in Figure 1 as for example as intaking roller ink unit 08 as for example with two friction cylinders (as for example out of newspaper print) or else as example shown in Figure 2 and Figure 3 as short ink unit 08 under use of a raster roller having cups. In not represented execution it can also be executed as roller ink unit 08 with two ink drawings and as for example three friction cylinders (as for example out of job printing). 8 In the case of dry off-set per printer 04 an inking unit 08, however no damping unit 09 is planned. In the moist off-set, through the damping unit 09, strictly separated from inking unit 08 or else parallel combined via a stripper roller with the inking unit 08, moist medium is supplied. The damping unit 09 can be designed as damping unit 09 with at least three rollers (represented in Figure 1). Preferably the damping unit 09 is executed as so called contact less damping unit 09 in particular spray damping unit 09. As indicated like wise in Figure 2 and Figure 3 the printers 04 can have in each case a handling device 19 for support of the printing block change. In preferred execution the handling device 19 is executed as at least part automatic or even fully automatic printing block changer 19. Independent from the advantageous design of the bearing described below, as bearing unit 14, it's special design and assembly, the coupling of the drive to the cylinder 06; 07 a print-on-position from printer cylinder 06; 07 or rather at least a print-on-position in the frame work of the presetting of a position limited stop, by means of at least one actuator 43 can take place, in particular through a power controlled or rather via a power defined actuator 43 by means of which for positioning a defined or rather definable force F may be brought in print-on-direction on the cylinders 06; 07 or rather it's necks 21; 22. The specific loading in the nipping positions decisive for the ink transmission and with it the print quality among others, is therefore defined not through an indirect parameter like as for example a measured printing strip, but rather through the force equilibrium between the force F and the specific loading FL resulting between the cylinders 06; 07 and the resultant equilibrium. The planned actuator 43 in the projecting execution of the bearing units 14 is designed for that to prepare a suitable actuator travel As for the on-or rather off position and has therefore preferably at least one As corresponding stroke. The actuator 43 is planned for adjustment of the position print of rollers or rather cylinders 06, 07 positioned to each other and/or for carrying out of print-on-/ off-position and is correspondingly designed. The actuator travel As (or rather stroke) amounts at least as for example 0.5mm for the plate cylinder 07 in particular at least 1mm. For base adjustment of a system therefore it can be planned in an advantageous execution that at least one cylinder 06 (07) may be set-up during a time gap in adjustment - without effective path limitation for print positions 05 - only power controlled on the adjacent cylinder 06 (07). Advantageously at least during a definite time gap of the adjustment process one cylinder 06 involved in the print position 05 is fixable or rather at least in direction of the print position 05 path limitable in a definite position, advantageously in the adjustment position found through the power equilibrium. In the following the principle of the power conn-oiled positioning (at least during the adjustment process) is explained in advantageous executions for the bearing and the actuator. 9 Figure 5 shows in plan view on the side racks in bearing units 14 rotatably supported cylinder 06, 07. In the execution with modules executed as cylinder units 17 (see below to Figure 6 and Figure 7) they show as for example a cylinder 06,07 with necks 21, 22 and a pre-erected bearing unit 14 (pre-stressed and / or pre-adjusted) on the necks 21, 22. Bearing unit 14 and cylinder06, 07 receive already before the input in the print unit 01 their firmly defined position to each other and may be brought in together in the print unit 01. In an advantageous execution of the print unit 01 it is planned to rest the cylinders 06, 07 rotatably in bearing unit 14 on the side racks 11, 12 which do not penetrate the alignment of the side racks 11, 12 and/or cylinders 06; 07 with their barrels 26; 27 show including their necks 21; 22 a length L06; L07 which is smaller or equal to a clear span L between the side racks 11; 12 (Figure 5) carrying the printer cylinders 06; 07 to both front sides. In the side racks 11; 12 carrying the printer cylinders 06; 07 to both front sides it does not deal preferably side wise with such open side racks so that the cylinders 06; 07 are axially removable rather with side racks 11,12 which show in axial direction one at least partly over lapping with the front side of the erected cylinder 06; 07 mat means the cylinder 06,07, in particulars it's bearing (see below) is surrounded front sided through the both side racks 11; 12 at least partly. Preferably all four printer cylinders 06; 07 (at least however three) have an internal bearing unit 14, in which the on-/off position mechanism is already integrated. It can also be planned for three or four cylinders 06; 07 bearing units 14 showing the on-/off position mechanism and for the fourth bearing unit 14 without on/off position mechanism. Figure 6and 7 show a preferred bearing unit 14 in schematically length- and cross section, based on linear actuator travels. The bearing unit 14 integrating the on-/off position mechanism shows in addition a bearing 31 as for example radial bearing 31, as for example a cylinder roller bearing 21, for rotational bearing of the cylinder 06; 07 bearing medium 32, 33 or rather bearing item 32, 33 for a radial movement of the cylinder 06; 07- for print-on-or rather print-off position. For this the bearing unit 14 (after fitting of the bearing unit 14 rack fixed) shows carrier fixed bearing items 32 as well as the bearing items 33 movable against this. The carrier fixed and movable bearing item 32; 33 are designed as jointly working linear items 32; 33 and jointly with corresponding sliding surface or in between lying rolling elements altogether as linear bearing 29. The linear items 32; 33 admit pair wise between them a bearing block 34 as for example slide 34 admitting the radial bearing 31. Bearing block 34 and the movable bearing item 33 can also be executed as single piece. The carrier fixed bearing items 32 are assembled on a carrier 37 which altogether is combined with side rack 11,12. The carrier 37 is as for example executed as carrier plate 37, which as for example has at least on one drive side a recess 38 for the engagement of a shaft 39 as for example drive shaft 39 of a neck 21; 22 of a cylinder 06; 07 not represented in Figure 7. Also the side rack 11; 12 on the drive side shows preferably a cut out or rather a break-out for a drive shaft 39. On the front side lying opposite to the drive side a recess 38 or a cutout in side rack 12; 11 must not be planned compulsorily. 10 Preferably a length of the linear bearing 29, in particular at least a length of the rack fixed bearing medium 32 in fitted condition, of the linear bearing 29 in the position direction S, is considered smaller than a diameter of the allocated printer cylinder 06; 07. The design of the linear bearing 29 in the way that the jointly working bearing item 32, 33 both are planned on the component bearing unit 14 - and not a part on the side rack 11,12 of the print unit 01 - makes possible a pre-assembly and pre adjustment or rather adjustment of the bearing tension. The advantageous assembly of both the linear bearings 29 engaging bearing block 34 makes possible a free from back lash adjustment, since both the linear bearings 29 lie opposite to each other in the way that the bearing pre-stress and the bearing forces receive or rather admit a main component in a direction vertical to rotation axle of the cylinder 06,07. The linear bearings 29 are thus adjustable in that direction on which it comes to the free from back lash position of the cylinder 06; 07. The assembly of the linear bearings 29 contains also special advantage with regard to the stiffness and stability. This is specially required in connection with an execution of a coupling of a stator (86, see below) on the bearing block 34. The linear bearings 29 (32,33) identifiable in Figure 6 and Figure 7 show thus in each case pairs corresponding, jointly working bearing medium 32 and 33 or rather their guide or working areas, designed as sliding surface (not represented) or with intermediately assembled rolling elements 23. As represented in Figure 8 in preferred execution at least of one of both, advantageously bom linear bearings 29 of a bearing unit 14 is executed such that both corresponding bearing media 32 and 33 in each case have at least two guiding areas 32.1; 32.2; 33.1; 33.2 which lie in planes El; E2 inclined to each other. Both the guiding areas 32.1; 32.2; 33.1; 33.2 (or rather their planes Ei, E2) of the same bearing medium 32; 33 are as for example inclined to each other V-shaped as for example with an intermediate angle between 30 to 60°, in particular between 40 and 50°. Both the guiding areas 33.1; 33.2; 32.1; 32.2 of the jointly working bearing medium 33; 32 are inclined for this shape complementarity. At least one of both the pairs of jointly working guide areas 32.1; 32.2; 33.1; 33.2 lies parallel to a plane Ei which has a component unequal to zero in radial direction of the cylinder axle and through it prevents the movement degree of freedom in a purely axial direction of the cylinder 06; 07. Preferably both the pairs lie to plane Ei; E2 which both show a component unequal to zero in radial direction of the cylinder axle, however in reverse inclination against the cylinder axle and through it prevent the movement degree of freedom in both axial directions of the cylinder 06; 07. A section line of bom planes Et; E2 runs parallel to the position direction S. In case, as identified in Figure 6, the bearing block 34 is enclosed between the both linear bearings 29 showing each two pairs jointly working guide areas 32.1; 33.1 and 32.2; 33.2, in particular pre-stressed with pre-stressing, then the bearing block 34 has yet only one single movement degree of freedom along the position direction S. The inclined working - or rather guide areas 32.1; 32.2; 33.1; 33.2 are assembled in such way that they work oppositely to a relative movement of bearing parts of linear bearing 29 in axial direction of the cylinder 06; 07 that means the bearing is fixed in 11 axial direction. Preferably the linear bearings 29 of both bearing units 14 allocated to a cylinder 06; 07 front sidedly, show two such type pairs of jointly working guide areas 32.1; 32.2; 33.1; 33.2 assembled to each other. In this case however in an advantageous way at least one of both the radial bearings 31 of both the bearing units 14 has minor bearing end float A31 in axial direction. In Figure 6 and 8 the guide areas 32.1; 32.2; show the rack fixed bearing medium 32 of the linear guide 29 in the semi space turned to the necks 21; 22. Hie rack fixed bearing medium 32 engage here the bearing block 34 assembled between mem. The rack fixed guide areas 32.1; 32.2 of both the linear bearings 29 engage thus partly the guide areas 33.1, 33.2 of the bearing block 34 with regard to an axial direction of the cylinder 06; 07. For correct placing of the bearing units 14 or rather cylinder units 17, together with bearing unit 14 erection aids 51, as for example dowel pins 51 can be planned in side rack 11; 12 to which the bearing unit 14 of the fully fitted cylinder unit 17 is aligned before they are combined through detachable holding medium 53, as for example screws 53 or even material fittingly through welding with side rack 11; 12. For the adjustment of the bearing pre-stressing in the linear bearing 29 to be taken up already before the input in the printing unit 01 and or after the input to be readjusted corresponding medium 54 as for example tension screws 54 can be planned (Figure 6). Preferably the bearing unit 14- at least for cylinder side there-is protected through a cover 57 extensively against pollution or rather even executed as capsuled as component. In Figure 6 schematically the cylinder 06; 07 is identified with necks 21; 22 and a pre- erected bearing unit 14. This component can be input pre-erected between the side rack 11, 12 of the print unit 01 in erection friendly way and can be fixed to the planned sides for this. Preferably for a module form of construction the bearing units 14 for plate-and transmission cylinders 07; 06 - if required till the permitted operational size of the actuator travel - are executed as per design. Through the pre- erectable execution the effective internal area of the radial bearing 31 and the external effective casing area of the necks 21; 22 can be executed cylindrical instead of taper, since the fitting of the bearing unit 14 on the necks 21; 22 as well as the adjustment of the bearing end float can take place out side of print unit 01. The bearing unit 14 can be as for example shrink-fitted. The assembly (bearing unit 14) erectable as whole is advantageously in the type of if required partly open housing out of as for example carrier 37 and/or as for example a frame (Figure 7) as for example the four side carriers 61; 62; 63; 64 as for example the side plates 61; 62; 63; 64 limiting the bearing unit 14 to all four sides towards out side and/or as for example the cover 57 (Figure 6). Inside of this housing or rather of this frame work the bearing block 34 showing the radial bearing 31, the linear bearing 29 as well as in advantageous execution as for example the actuators 43 or the actuators 43 are accommodated. The rack fixed bearing items 32 are assembled mainly parallel to each other and define a positioning direction S (Figure 7). 12 A print-on-position takes place through movement of the bearing block 34 in direction print position 05 by means of a force F brought up through at least one actuator 43 on the bearing block 34, in particular through a force controlled or rather via a force defined actuator 43, by means of which for positioning of a defined or rather definable force F in print-on-direction may be brought up on the bearing block 34 (Figure 7). The specific loading in the nipping positions decisive for the ink transmission and with it the print quality among others is therefore not defined through actuator travel, rather through the force equilibrium between the force F and specific load F1 resulting between the cylinders 06; 07 and the resulting equilibrium. In a first, not particularly represented execution cylinders 06, 07 are pair wise positioned to each other in which the bearing block 34 is charged with the correspondingly adjusted force F via the actuator (s) 43. In case more number (as for example three or four) of cylinders 06, 07, in each case working jointly pair wise adjacent to each other in direct following are executed without a possibility for fixing or limiting of the actuator travel with a pure force dependent position mechanism, then in fact a system adjusted already in relation to the required pressure (specified load) is again correctly adjusted in sequence and followingly to take up a base adjustment on ground of partly over lapping reaction it is only hardly possible. For base adjustment of a system (with corresponding equipments etc) it is therefore planned in an advantageous execution that at least both the middle of four cylinders 06 - or other wise expressed, at least all of cylinders 06 different from both the external cylinders 07 at least during a time gap in adjustment in a definite position are fixable or rather at least position limitable advantageously in the adjustment position found out through force equilibrium. An execution is specially advantageous, wherein the bearing block 34 - also during the operation - at least is movably supported in one direction from the print position 05 away against a force as for example spring force, in particular a definable force. With it - in contrast to pure path limitation - at one side a maximum specific load in joint working of the cylinders 06; 07 is defined and on the other side a compliance as for example a path tearing with following winder on cylinder 06; 07 is made possible. To a side turned to the print position 05, bearing unit 14 - at least during the adjustment process - has a location changeable stop 41 which limits the actuator travel to the print position 05. The stop 41 is location changeable in the way, that the stop area 44 effective as stop is variable along the position direction S at least in one area. An adjustment device is thus planned in an advantageous execution (shiftable stop 41), by means of which the position of a print position near end - of - run position of the bearing block 34 is adjustable. For path limitation / adjustment, as for example a wedge drive serves as described below. The positioning of the stop 41 can basically take place manually or via an adjusting medium 46 executed as actuator 46. Further in advantageous execution, in Figure 6 and 7 not represented a holding or clamping medium is planned by means of which the stop 41 is fixed in the desired position. Further at least a resiliently working item 42 as for example a spring item 42 13 is planned, which brings a force FR from stop 41 in a direction from the path, on the bearing block 34. That means the spring item 42 causes a print-off-position for the case that the bearing block 34 is not impeded in other ways on the movement. A print- on-position takes place through moving of the bearing block 34 in direction stop 41 through at least one actuator 43 in particular a force operated actuator 43 by means of which for positioning selectively a definite or definable force F in print-on-direction may be brought up on the bearing block 34. In case this force is greater than the re- setting force FR of the spring item 42, then in corresponding spatial design a adjustment of the cylinder 06,07 to the adjacent cylinder 06,07, and/or an adjustment of the bearing block 34 at the stop 41 takes place. In ideal case the brought up force F, the re-setting force FR and the position of the stop 41 is selected such that between stop 41 and stop area of the bearing block 34 in adjustment position no essential force ∆F is transmitted, that as for example, it is valid /AF/0.l* (F - FR), in particular /∆F/ mis case the adjustment force between the cylinders 06; 07 is determined mainly via the clinging force F through the actuator 43. The specific loading in the nipping positions decisive for the ink transmission and with it the print quality among others is therefore primarily not defined through an actuator travel but in case of quasi free stop 41 through the force F and the resulting equilibrium. Basically after finding of the base adjustment with the force F fitting for this a removal of stop 41 or rather a corresponding effective fixing only during base adjustment is thinkable. The actuator 43 can be executed basically as optional, actuator 43 bringing up a definite force F. advantageously the actuator 43 is executed as positioning medium 43 to be operated through pressure medium in particular as piston 43 movable through a fluid. Advantageously with regard to possible tilting the assembly is of multiple number, here two such type actuators 43. The actuator (s) can either be integrated in the side carriers 63 or in the slide 34, or else as represented these can be assembled in a special component as for example an actuator item 59 and can be input in the bearing unit 14. As fluid preferably because of it's non-compressability a liquid as for example oil or water comes to input. In an other execution the actuator 43 also can be designed as piezo (piezo electric power bring up) or as magnet (magnetic force bring up), in particular electro magnet. For operation of the actuators 43 executed as hydraulic piston 43 either inside or out side of the bearing unit 14 a controllable valve 56 is planned. This is executed as for example as electronically controllable and places the hydraulic piston 43 in a position pressure less or at least on a minor pressure level, while in an other position the pressure P causing the force F exists. Additionally here for safety a not described leakage line is planned. In order to avoid too great on -/ off position path and even then to protect track winder, on the print position distant side of the bearing block 34 a path limitation through a location changeable, power limited stop 49 as overload safety 49 as for example spring item can be planned, which in operational pressure - off mat means 14 the pistons 43 are de-pressurised and/or retracted, in fact serve as stop 49 for the bearing block 34 in print-off position however complies in the case of a path winder or other excessive forces from the print position 05 and releases a greater path. A spring force of this over load safety 49 is selected greater than the sum of the forces from the spring items 42. In case of operational on- off adjustment therefore only a very short actuator travel as for example only 1 to 3 mm, may be planned. The stop 41 is executed as wedge 41 movable transverse to the positioning direction S in the represented execution (Figure 7), in doing so in movement of the same the position of the respective effective stop areas 44 varies along the position direction S. The wedge 41 supports as for example on a carrier fixed stop 58. The carrier fixed stop 58 is formed here as for example through a side carrier 61 of the bearing unit 14. The stop 41 executed as wedge 41 is movable through an actuator 46, as for example a pressure medium operating positioning item 46 like a piston 46 to be operated with pressure medium in a working cylinder with (double acting) piston via a transmission item 47 executed as for example as piston rod 47 or through an electromotor via a transmission item 47 executed as threaded spindle. This actuator 46 can be effective either in both directions or even, as represented here, may be executed as single way reactor which works in activation against a resetting spring 48. The force for the resetting spring 48 is selected so weak out of above mentioned reasons (widely power free stop 44) that the wedge 41 is held only against gravity - or vibration forces in it's correct position. Basically the stop 41 can also be executed on other type (as for example adjustable to the position direction, and fixable ram etc) in the way, that it forms in position direction S a variable and - at least during adjustment process - fixable stop area 44 for the movement of the bearing block 34 in direction print position 05. In not represented execution a positioning of the stop 41 takes place as for example directly parallel to the position direction S through a drive medium, as for example a cylinder with (double acting) piston or an electromotor to be operated with pressure medium. In Figure 2 on the printer 03 executed as double printer 03 schematically per cylinder 06;07 a bearing unit 14 assembled on side rack 11 is indicated. In an advantageous, here represented execution the rotation centers of cylinders 06; 07 form in print-on- setting an assumed connecting line or rather - plane E (in the following denoted as "linear double printer"). Preferably the plane E and the in- or rather out running path 02 include an internal angle between 75 and 88°, in particular from 80 to 86° deviating from 90°. The bearing unit 14 of the transmission cylinder 06 in particular of all cylinders 06; 07 are assembled in the erected condition in the execution represented in Figure 2 on the side rack 11 in such way that their position directions S - as for example out of ground of a power defined print - on - setting - encloses maximum angle of 15° with the connecting plane E, as for example a peak angle of about 2° to 15 , in particular form 4 to 10° with each other. In particular this assembly is of advantage with regard to the fitting when the positioning direction S runs horizontal and the path 02 runs mainly vertical. 15 In modified execution (Figure 1) of an angular (n-or u- printer) assembled double printer 03, under the plane E' the connecting plane of the cylinders 06 forming the print position 05 and under planes E" the connecting plane between plate and transmission cylinders 07, 06 will be understood and the above mentioned are related to the angle on the positioning directions at least of one of the cylinders 06 forming the print positions 05 or rather the plate cylinder 07 and the plane E' or rather E". One of the cylinders 06 forming the print position 05 can also be assembled stationary and operationally non-adjustable (if required however adjustable) in side rack 11; 12 while the other is supported movable along the positioning direction S. An operational actuator travel to on -/ off-setting, along the position direction S between print-off and print-on - setting lies as for example in transmission cylinders 06 at 0.5 to 3 mm, in particular at 0.5 to 1.5 mm and in the plate cylinders 07 at 1 to 5 mm in particular at 1 to 3 mm. In execution as linear double printer 03 the plane E is inclined towards the plane of the in running and out running path 02 as for example an angle around 75° to 88° or rather 92° to 105°, preferably an angle around 80 to 86 or rather 96 to 100°, on each of a path side (or rather 96 to 100° or rather a 80 to 86° on each other path sides). In an other not represented execution the bearing units 14 of the transmission cylinder 06, in particular of all cylinders 06, 07 are assembled in erected condition on the side rack 11 in such way that their positioning directions S coincide with connecting plane. All positioning direction S of the printer 04 coincide with it and are not distanced from each other. In an execution variant the actuator 03 can be assembled integrated on the bearing block 34 and push it self off at the side plate 6.. In a further execution version, additionally at least one further, in activation acting away from the print position 05, actuator can be planned. This can replace or support the spring item 42. Figure 9 shows an execution example for the coupling of an axial drive for page recording equipment as for example on the side lying opposite to the drive side of the cylinders 06, 07; in particular of the cylinder 07 executed as plate cylinder. For this the neck 21 is coupled preferably with a device for axial movement of the cylinder 07, that means with a page recording drive 66 as for example a drive motor 66 (Figure 37). The shaft 39 combined, with the neck 21 as example in the type of Figure 9 is combined via a bearing 67 as for example axial bearing with an axial drive 68,69, 72, 73. The axial drive 68, 69, 72, 73 covers a spindle 68, in particular with at least one thread section 71, one spur gear 69 combined rotation fixed with the spindle 68 a pinion 72 as well as a motor 73 driving the pinion 72. The threading section 71 acts together with a bearing block fixed internal thread 74, as for example an internal thread 74 of a pot 76 combined with the bearing block 34, and causes, in case of twisting of spindle 68 an axial movement of the same together with shaft 39 (via the axial bearing 67) and neck 21. 16 The axial bearing 67 permits a relative rotation between shaft 39 and spindle 68, is designed pressure - and tension rigid however with regard to an axial direction of the cylinder 07. This takes place via a disk 78 assembled on the shaft 39 which as for example via rolling element 79 supported both side wise is path limited in both directions through spindle fixed stops 77. A shifting of the page recorder takes place now through the motor 73 via a not represented control equipment Herein the motor 73 can either have at their disposal a - as for example previously calibrated correspondingly - motor internal position feed back or else a position feed back takes place at the control via a not represented sensor as for example a correspondingly calibrated rotary potentiometer which is coupled to a rotating component of the axial drive. Independent of the special design of the bearing and/or alignment of actuators travel to the plane E or rather E' or E" (small inclination or yet not) and/or of divisibility of the printing unit 01 and/or the coupling of an axial drive, followingly specially advantageous executions for coupling of a drive motor 66 to the rotation body designed here as cylinder 06; 07 and/or specially advantageous designs of the drive motor 66 driving the rotation body are shown. In an example not belonging to the invention, for the drive coupling, as represented in Figure 6 i.v.m Fig 10 or rather 11, the coupling of the cylinder 06,07 or rather of the neck 21; 22 takes place on a drive side of the print unit 01 to a drive as for example directly to a rotor of a drive motor 81 and/or a drive pulling, via at least one angle - and/or off-set balancing coupling 82. The drive motor 81, in particular it's rotor, can then be assembled rack fixed and must not follow the on-/off setting movement of the cylinder 06,07. Preferably the drive motor 81 to be coupled in this first execution for the drive of the cylinder 06; 07 (or rather rotating component) is designed as synchronous motor 81 and/or permanent magnet excited electromotor, in particular as permanent magnet excited synchronous motor 81. This drive motor 81 is a directly driven circular motor and shows a stator with 3-phase current winding as well as a rotor with permanent magnets. Through this design of the drive motor 81, in particular the permanent magnets a high power density is achieved and makes therefore use of the gear ratio unnecessary. Thus the inaccuracies in drive strand as well as wear mechanical items like gear are dispensed with. The coupling of rotatory drive to the rotating component, here the cylinder 06, 07 takes place herein as represented in Figure 6 as example for the first execution via the shaft 39, which covers on their cylinder near end one end of the neck 21, 22 and is combined rotation stiff as example via a clamping equipment 24 with the neck 21; 22. The clamping equipment 24 is here as for example designed as partly slit hollow shaft end which covers the neck ends (neck 21,22) and by means of a screw combination is to be pulled together in the way that a frictional locking rotation fixed combination between neck ends (necks 21; 22) and hollow shaft internal area is generated. The coupling can also in other way, as for example in circumference direction showing a form fitting, be executed. Also it is possible in an advantageous variant to manufacture the rotation fixed combination with tension elements in friction locking 17 condition. The shaft 39 is guided through a cut out in side rack 11; 12 which is dimensioned sufficiently large for the movement of the shaft 39 together with the bearing block 34 and which as for example is designed in the type of an elongated hole. As pollution safety a cover 28 with a collar covering the elongated hole can be planned, which as for example with bearing block 34, however is not combined with the shaft 39. At the cylinder distant end of the shaft 39 as represented in Figure 6, one of, if required, more in number serially assembled angle- and/or off-set balancing coupling 82, in particular clutch disk coupling 82, may be coupled through a rotation fixed combination 36 as for example a tension item 36. In the Figure 10 not belonging to the invention with regard to the drive coupling schematically a drive motor 81, designed as permanent magnet excited drive motor 81, in particular synchronous motor 81, is represented whose rotor 84 as for example via a motor shaft 85, carrying the rotor 84 rotation fixed and a further, rotation fixed coupling 83 as for example a jaw coupling 83 is coupled on the shaft 39. The stator 86 of the drive motor 81 is combined rack fixed via a holding item 87 with the side rack 11; 12. The rotor 84 is rested in the stator 86 via bearing 88 in particular radial bearing 88 and if required is additionally secured against an axial movement. The axial movement in case of the cylinder 07 designed as plate cylinder 07 is taken up through the couplings 82. The rotor 84 or rather rotor of the synchronous motor 81 shows on it's circumference (in particular in circumference direction alternatively) pole out of permanent magnets 89. The stator 86 shows windings 91 lying opposite to the permanent magnet 89 for generation of magnetic fields through electric energy. The drive motor (as for example drive motor 81) designed as permanent magnet excited synchronous motor 81 is as example designed as field weakening synchronous motor. The field weakening of the synchronous motor is as for example planned up to a ratio 1:10. It shows at least six pole pairs, advantageously at least 12 pole pairs. The permanent magnets 89 has preferably rare-earth-material. In particular advantageously the design of the permanent magnet 89 is with neodymium-iron-boron. The drive motor (as for example drive motor 81) designed as permanent magnet excited synchronous motor 81 shows as for example a sustained stall moment in the range of 50Nm to 200Nm, in particular for the drive of printer cylinders 06; 07 from 50 to 150 Nm or rather for roller changer-or folding machine device drive of 100 to 200 Nm. Advantageously the drive motor designed as permanent magnet excited synchronous motor 81 (as for example drive motor 81) has a maximum torque in range of 200 to 800 Nm, 200 to 400 Nm for the drive of printer cylinders 06; 07 or rather for roller changer or folding machine drive of 600 to 800 Nm. The drive motor (as for example drive motor 81) designed as synchronous motor 81 and/or permanent excited motor 81 has a for example a theoretical no-load speed in the area of 500 rotation / min to 600 rotations / min. 18 To the drive motor (as for example drive motor 81) designed as synchronous motor 81 and/or permanent excited motor as for example a frequency converter is pre- connected for control of number of rotation. The stator 86 is advantageously executed with 3-phase current winding, in doing so sinusoidal commutation of the current takes place. Preferably on the drive motor (as for example drive motor 81) designed as synchronous motor 81 and/or permanent excited motor, a sensor 106 mentioned below as for example angle of rotation sensor 106 is planned. A rotation axle of the angle of rotation sensor 106 can be assembled advantageously coaxially to the rotation axle of the rotor 84 of the motor (as for example drive motor 81). Advantageously at the drive motor (as for example drive motor 81) designed as synchronous motor 81 and/or permanent excited motor, a cooling equipment in particular a fan wheel or a liquid cooling medium circuit, is planned. Additionally on the motor (as for exampled drive motor 81) designed as synchronous motor 81 or permanent excited motor a brake equipment can be planned. The motor can also be in put in generator operation on brake equipment. Further fitting mechanism for position correct fixing between stator 86 and rotor 84 may be planned. That mentioned standard for design of permanent excited synchronous motor 81 can be partly or a together transmitted to corresponding drive motors (138; 139; 140; 141; 142; 143; 152; 162; 163; see below) of other rotating components (133; 135; 136; 144; 145; 146; 147; 148; 153; 164; see below) different from printer cylinders 06; 07. As represented in Figure 11 not belonging to the invention as regard to the drive coupling, the print cylinders 06; 07 in advantageous execution in each case are driven through a drive motor 81. The necessary off-set in case of on- / off-setting of the nipping position is made possible herein through the coupling 82. In the execution as per Figure 11 an ink unit gear with internal drive motor (for rotation and changing movement) and in case of the moist off set, a damping unit gear with internal drive motor (rotation and changing movement) work out a variability and accuracy. As for example in Figure 11 the drive of the printer 04 on the left side is represented for the proportion of the dry off-set (with out damping unit), on the right side for the wet off-set (with damping unit). Obviously both the printers 04 however are of same type of a real double printer 03. In the front sided view due to outline reasons roller diagrams are dispensed with and only the drive pullings with motors are represented. In the plan view the drive concept on the example of an ink unit 08 with two rotationally driven changeable rollers 92 as for example friction cylinder 92 and- in case of moist off-set-as example of a damping unit 09 with a rotationally driven, not represented friction cylinder is represented. The ink unit 018 shows in each case an internal, drive motor 93 mechanically independent from tne printer cylinders 06; 07 for the rotational drive. Through this in 19 particular both the friction cylinders 92 of the ink unit 08 are driven rotationally as for example via a gear not explained here further. In the case of moist off-set (right) mainly the same is valid for the drive of damping unit 09 with a drive motor 96 and a gear 97. Per friction cylinder 92 of the ink unit 08 and per friction cylinder of the damping unit 09 a friction gear generating axially changing movement can be assembled. This can however be driven basically through an additional drive motor or else as represented can be designed as a gear converting the rotation movement to an axial movement. In Figure 11 in advantageous design the bearings are indicated as bearing unit 14 in above mentioned execution for the bearing of four cylinders 06; 07. The shafts 39 are as for example guided through corresponding cutouts / breakouts in side rack 11, 12. The coupling between rack fixed drive motor 81 and plate cylinder 07, not belonging to the invention is preferably executed for making possible a page record control/- regulation in such way that it admits also an axially relative movement between plate cylinder 07 and drive motor 81. This can likewise take place through above mentioned clutch plate coupling 82 which makes possible through deformation in the area of clutch plate an axial length change. An axial drive executed in the way represented in Figure 9 or otherwise can be planned on the other rack side, as the rotational drive. Also the driven friction cylinder 92 of the ink unit 09 can be coupled via at least one coupling balancing angle deviations, with the drive motor 93. The drive motors 93 in the ink unit 08 and/or damping unit can be designed in the way of above described permanent magnet excited drive motor 93, in particular synchronous motor 93. Dimensioning and designing however if required can differ from above. In an execution example for the drive coupling (Figure 12) as per the invention the coupling between rotation body as for example cylinder 06, 07 and drive motor 81 directly takes place-that means without one coupling making possible one axial relative movement and/or without an angle-and/or coupling balancing off-set at the shaft 39. This coupling can be solid, but detachably executed. In this execution the drive motor 81 as for example is not rack fixed, rather assembled cylinder fixed and is moved along in case on-/off setting - and if required in page recording shifting - with the cylinder 06, 07. In the case of cylinders 06; 07 movable by means of a bearing assembly 14 the drive motors 81 per printer cylinder 06, 07 are not combined on the side rack 11; 12 but directly with the movable bearing block 34 solidly as for example screwed and are moved along during the position movement, Figure 12shows a design of the drive of a rotating component, in particular of the cylinders 06; 07 supported on the bearing unit 14 with a drive motor 81 designed as synchronous motor 81 and/or permanent excited motor that means designed with a section of permanent magnet 89 on the rotor 84. The stator 86 is herein as for example directly or indirectly fixed on the moving part of the bearing unit 14 as for example on movable bearing block 34 solidly and together with this is movable. In case of other type of bearing assembly 14 the stator 86 as for example is rested in the interior eccentric bush or rather the lever. The parts 20 corresponding to the bearing unit 14 are not provided once more in Figure 12 with reference symbols and can be taken from Figure 6. In the example of Figure 12 the stator 86 showing the windings 91 is bolted detachably with a holding medium 98 as for example a bush 98 in particular collar bush 98 which is detachably combined as for example through bolts 99, with bearing block 34. In the present execution the motor shaft 85 carrying the permanent magnets 89 or rather the rotor 84, of the drive motor 81 is built through the shaft 39 or rather in reverse the shaft 39 through the motor shaft 85. Motor shaft 85 and rotor 84 can be designed as single piece, so that in this case the motor shaft 85 carrier the permanent magnet 89 on it's circumference. In the example, motor shaft 85 and rotor 84 are designed as two components and as for example through a tension item 101 or rather locking assembly 101 are combined rotation fixed with each other. The rotation fixed combination between shaft 39 or rather motor shaft 85 and necks 21, 22 is generated here through a friction lock as for example a tensioning element 102 or rather locking assembly 102. In the result rotor 84 and cylinders 06; 07 (or rather neck 21; 22) are combined with each other in axial and radial direction solidly and rotation fixed. The combination can be designed however detachable on different positions. The rotor 84 moves thus along when the cylinder 06; 07 in particular the plate cylinder 07 is moved axially or radially. The stator 86 with regard to a movement vertical to the cylinder longitudinal axle is assembled cylinder fixed and moves along in on-/ off setting movements. In contrast to the execution of the drive motor 81 out of Figure 10, here preferably between stator 86 and rotor 84 no radial bearing for opposite support is assembled. For additional support and/or anti-rotation device of the permanent excited synchronous motor 81, in particular it's stator 86, a guide 103 can be planned on which the motor slides. The guide 103 is matched to the curve shape of adjustment path of the bearing assembly 14 ("similarity") and is designed here as linear guide 103. For this a rack fixed part of the guide 103 with the side rack 11, 12 and the stator 86 as for example via a support 104 as for example a support plate 104 is combined with the corresponding movable part of the guide 103. The degree of freedom of linear guide must only amount to few millimeters. In the represented execution the support and/or anti-rotation device can also be dispensed with, when the bearing assembly 14 in particular the linear bearing 29 is designed sufficiently stiff and load bearing in order to take up the torque between stator 86 and rotor 84 as well as tilting torque through the weight of the stator 86 (with bush 98 etc). In preferred execution of the drive motor 81, in particular as drive for rotating component with requirement on record holding capacity in circumference direction as printer cylinders 06; 07 or cylinder of a folding machine represent (see below) the drive motor 81 is designed as angular position regulated drive motor 81. For control or rather angular position regulation a sensor 106 combined rotation fixed with the component (cylinder 06; 07) or rather the drive motor 81 as for example a sensor 106 detecting the angular position, in particular an angular position provider 106 is required, over which the actual angular position, is reported back to feed back control 21 circuit. In case of a component without requirement on record maintaining (as for example ink unit 08, in taking unit, or a draw roller) however with requirement on a selectable number of rotation the sensor 106 can be executed also only as the number of rotation detecting sensor 106, in particular revolution speed transmitter. In the case lying in Figure 12 of a cylinder 06; 07, the sensor 106 can basically be assembled optionally to one component combined rotation fixed with the cylinder 06; 07 as for example also on the neck 21, 22 lying opposite to the drive motor 81. In the advantageously represented execution, the sensor 106, in particular it's rotor is assembled however co-axially to the rotation axle on the cylinder distant end of the motor shaft 85. The stator of the sensor 106 is secure via an anti rotation device 107 on the stator 86 of the drive motor 81 against twisting. The anti-rotation device 107 shows in radial direction a degree of freedom, thus the stator of the sensor 106 can follow a, if required, present untrue running of the motor shaft 85 and with it of the sensor rotor. The fixing of anti-rotation device 107 takes place for this as for example via a radially running elongated hole in which a pin engages. In order to maintain angle fault resulting from an untrue running smallest possible, the anti-rotation device 107 is executed as longer lever with regard to the radial direction. The length 107 from the sensor stator to the fixing point of the anti- rotation device 107 corresponds as for example at least to one external diameter, advantageously at least the double external diameter of the sensor rotor in order to maintain small the angle if required, of a swing movement present in case of out-of- balance. In advantageous execution the drive motor 81 shows a cooling (also in application on rotating components of the printing machine different from printer cylinders 06; 07). In simple not represented execution the cooling takes place through a fan wheel. Advantageously however a liquid cooling medium circuit is planned, in which tempered cooling medium, as for example water may be guided through the drive motor 81. In Figure 12 for this connecting bores 108 in the housing of the stator 86 is planned, through which the cooling medium may be guided in cooling medium channels 109 between the housing and a carrier carrying the windings 91. In the execution represented so far for Figure 12 the drive motor 81 and it's binding and periphery (sensor 106 and/or cooling and/or anti-rotation device 107) may be planned for the cylinders 06, 07 designed as plate cylinder 07 as well as transmission cylinder 06. In a special execution of the cylinder 06, 07 in particular plate cylinder 07, this shows however holding - and/or detaching medium for fixing of fittings as for example printing blocks (in particular ends of end thrust plates) which are executed workable through pressure medium. Preferably the holding - and/or detaching medium are designed self secure, so that a holding without activation of pressure medium and an opening or rather detaching takes place through charging with pressure medium. The cylinder 07 shows as for example in axial direction more number as for example four or even six holding and/or detaching media workable independent of each other for fixing or rather detaching, likewise many adjacently assembled printing blocks as for example thrust plates. In the case of endwise thrust plates, the ends of thrust plates slip in slit on the cylinder casing area and are held preferably self secure through the 22 pressure medium workable holding medium. In the design of end less printing blocks as for example printing block sleeves, as for example on the cylinder casing out let openings for the pressure medium are planned, in doing so the printing blocks 07 engaging the cylinders 07 as for example are detached through charging with pressure medium. The cylinder 07 can show in circumference direction in series more number as for example two holding - and/or detaching media workable, independent of each other, for fixing or rather for detaching like wise of many printing blocks as for example pressure plates assembled serially in circumference direction. Altogether then as for example two groups to each four or six pressure plates are to be assembled on the cylinder 07. The change of pressure plates takes place however group wise, so that in a definite cylinder position in all cases the holding medium of a group of pressure plates as for example four or six must be in position to be operated. For definite supply of multiple number of holding media in the cylinder 07 with pressure medium the drive strand shows a rotation transmitter through which multiple number of supply channels may be charged with pressure medium in the cylinder 07 selectively independent of each other. In an advantageous execution the rotation carrying is designed with an interface between rotating and rotation fixed component to which the pressure medium flow to be transferred runs in axial direction. For this a rotor III designed in the type of circular ring is combined rotation fixed with the cylinder 07 or rather it's neck 21; 22 which shows (Fig 13) break outs 118 going through axially through the rotor 111. The break outs 118 remain in combination with the lines 117 (dash lined) leading to the individual holding medium. The number of spatial break outs 118 separated from each other on the rotor corresponds at least to the number of total holding media to be operated independent of each other. The rotor 111 works together on an axially aligned, front sided contact area with an oppositely lying axially aligned, front sided contact area of a rotation fixed stator 112 (Fig 114) which in it's front sided contact area shows out let openings 119 in the way that they may be passed depending on relative angle position between stator 112 and rotor 111, selectively in coverage with an inlet opening of a break out 118 or also depending on the position selectively in cover with inlet openings of different break outs 119. The number of out let openings 119 corresponds at least to the number of holding medium or rather pressure plates of a group of serially assembled pressure plates here as for example four. These four out let openings 119 as for example are fed via four supplies 113 out of lines separated from each other, not represented which in each case selectively are chargeable with pressure. In order to seal inter faces in the selected relative position of the cylinder 07 during the charging, in advantageous execution stator 112 and rotor 111 are relatively movable to each other and are designed pressable to each other. In the present execution the stator 112 is supported axially movable on the shaft 39 and is pressable via a ring shaped punch 116 on the rotor 111. The pressing takes place as for example through charging of a ring shaped intermediate space with a pressure medium, which is charged through a corresponding connection 114. In an execution of the cylinder 06, 07 as for example as transmission cylinder 06, without the requirement of a pressure medium supply, the rotation transmitter with the described components can 23 be dispensed with and if required the drive motor 81 can be designed narrower to the cylinder 06; 07. In a variant not belonging to the invention for the second execution represented in Figure 12 the stator 86 is not solidly combined with the bearing block 34 but is carried via radial bearing 88 (comparable to Figure 10) on the motor shaft 85. Here at least one anti-rotation device 103, 104 as for example in the way represented in Figure 12 is required. This can be designed stiff in axial direction of the cylinder 06, 07 when the radial bearing 88 between rotor 84 or rather motor shaft 85 and stator 86 make possible an axial relative movement. In this case the rotor 84 moves in rack fixed stator 86 axially, when the cylinder 06; 07 is moved axially. In case rotor 84 or rather motor shaft 85 and stator 86 are secure against an axial relative movement, then the device must be executed for anti-rotation device 103, 104 also making possible a degree of freedom in axial direction of the cylinder 06; 07. In this case the rotor 84 moves jointly with the stator 86 axially when the cylinder 06; 07 is moved axially. Since it deals only with few millimeters this can take place in a simple execution as for example through a long lever arm that means through a long support 104 with regard to the distance to the guide 103, in doing so the small axial movement is picked up through the deformation of the support 104. In a second execution either the guide 103 or the binding of the support 104 at the stator 86 can show a further linear guide, however with a degree of freedom in axial direction of the cylinder 06; 07. This can as for example take place through bolts as for example on side rack 11; 12 on movable part of the guide 103 or on stator 86 and corresponding bore or rather suspension eye on the corresponding component as for example the rack fixed part of the guide 103, the support 104 in the area of the guide 103 or the support 104 in the area of the stator 86. In the execution represented in Figure 12 a part 181 carrying the winding 91, of the stator 86 is combined in axial and radial direction solidly and rotation fixed but detachable - as for example via the represented, screw connection however not described in Figure 12 - with the movable part of the bearing assembly 14 and as for example with a housing 182 of the drive motor 81. This solid combination 184 (in Figure 12 altogether represented with dashlined arrow) represents there one solid combination in particular with regard to an axial direction and can be designed solid for not movable cylinder also in radial direction with regard to the side rack 11; 12. One part 183 carrying the permanent magnet 89, of the rotor 84 is combined there with regard to an axial relative movement solidly with the cylinders 06; 07, so that with an axial movement of the cylinder 06; 07 - as for example for adjustment of the page recorder compulsorily an axial relative movement between windings 91 and permanent magnets 89 can appear. In the following (Figure 15 to Fig 18), special advantageous execution variant of the drive motor 81 is represented which with regard to an axial positioning guarantee to each other an optimal workpoint between stator 86 and rotor 84. The Figures 15 to 18 are represented simplified in contrast to Figure 12 and can additionally show a rotation transmitter described above and/or a support described above and/or anti- rotation device for the drive motor 81. 24 In a design not belonging to the invention, of the drive motor 81, the stator 86 is assembled in fact rotation fixed, in axial direction however not rack - or bearing fixed, but (at least in a definite order of magnitude for the page recorder) axially movable. Relative to the side rack 11; 12 and/or to a purpose of an-/off position moving parts of a bearing assembly 14 it however designed with anti-rotation device with regard to appearing torque. A coupling between stator 86 and rotor 84 which concerns the axial movement does not take place here mechanically but as for example via magnet force. In case now as for example a rotor movable axially jointly with the cylinder 06; 07 moves axially, then via the magnetic interaction the stator may be at least partly guided along. In ideal case, this may be carried along axially in the way, that the magnets of stator and rotor can remain in the optimal working point to each other that means the stator considered relative to the rotor can remain stationary in extreme case. The axial degree of freedom of the stator 86 with regard to the side rack 11; 12 and/or the bearing assembly 14 besides the rotation fixed combination with the side rack 11; 12 and/or bearing assembly 14 on the other hand (anti - rotation device) can be realized in different way. Without restriction of the generalization, in Figure 15, 16 and 17 three first advantageous execution shapes are represented. Herein there exists between stator windings and side racks 11; 12 and/or bearing assembly 14 or rather holding medium 98) in axial direction to solid, but in certain limits (as for example an axial relative movement in the area of at least 1 mm that means at least ± 0.5 mm out of a medium position considered) a "soft" combination in axial direction. In contrast to Figure 12 there exists in the example of Figure 15 not belonging to the invention, no solid combination (184) between the stator 86 (or rather of the part carrying the windings 91) and the housing 182. The part of the stator 181 carrying the windings 91 is supported in the housing 182 movable axially. For this housing 182 and part carrying the windings 91, of the stator 181 as for example are designed with together working slide areas 186. The guarantee of maintaining radially relative position in simultaneously making possible an axial relative movement can in principle also take place in other way than with a slide guide showing slide area 186. In this execution the housing 182 (as in Figure 12) is combined pressure -/ tension stiff and rotation fixed with the holding medium 98 that means lastly with the bearing assembly 14 and/or the side rack 11, 12. With it however the motor torque is held, the stator 86 or rather it's part 181 is combined rotation fixed with bearing assembly or rather the side rack 11, 12. This takes place as for example via one or more number anti-rotation devices 187 (as for example coupling 187) form fitting with regard to a direction of rotation, between the stator 86 or rather it's part 181 and a rack - or bearing fixed part like it represents as for example the housing 182. In Figure 15 the rotation fixed combination through one or more number stops 188 as for example bolts assembled on the stator 86, is formed which is led in guide 189 as for example bore in the housing. This can also be executed in the reverse way. The anti-rotation device 187 form fitting in rotation direction shows inside their axial movement clearance in this execution no form fitting in axial direction but as for example only one end stop. 25 The sensor 106 can be represented either as in Figure 12 or else as in Figure 15 via a holding item 191 as for example a holding device or so called box combined with the housing 182. In Figure 16 the sensor 106 is combined via the holding medium 191 mainly solidly with the housing 181, an axial relative movement between the shaft 39, 85 and the rotor of the sensor takes place via a rotation fixed or rather rotation stiff, coupling 192 as for example a jaw coupling admitting however an axial movement preferably via a so called clutch - disk - or all-metal coupling. In the variant to the execution not belonging to the invention, of the axially movable stator as per Figure 16 the housing 182 is not combined pressure -/ tension stiff with the bearing assembly 14 or rather the side rack, but is movable it self axially, however is guided rotation fixed. The part 181 carrying the windings 91, of the stator is combined with the housing 182 as for example solidly so that housing 182 and the stator 86 or rather the part 181 move jointly axially. The housing is assembled opposite to the bearing assembly 14 or rather to the side rack 11; 12 rotation fixed, however axially (at least in certain limits) movable. This takes place as for example again via a form fitting anti-rotation device 187. In the Figure 16 not belonging to the invention the rotation fixed combination (anti-rotation device or rather coupling 187) assembled through one or multiple number of holding media 98 is formed in stop 193. In the Figure 16 not belonging to the invention the rotation fixed combination (anti- rotation device or rather coupling 187) is formed through one or more number stops 193 or rather bolts 193 acting in rotation direction, assembled on holding medium 98, which is guided in a housing fixed guide 194 as for example bore 194. The guide 194 can be designed as bore in a connecting bar 196 combined firmly with the housing 182. This can also be designed in reverse way. The connecting bar can be designed as collar shaped annulus, in which more number of these guides 194 (or in reverse way bolts) can be assembled. Between the parts movable axially relative to each other here a sealing 197 or other type covering can be advantageously assembled to the housing 182 or rather the connecting bar 196 and the holding medium 98. Also here the form fitting anti-rotation devices 187 in direction of rotation, do not show within their axial movement clearence any form fitting in axial direction but as for example only one end stop (see as for example thickening on end of bolts 193). In the Figure 17 not belonging to the invention, the anti-rotation device 187 is designed as coupling 187 basing on deformation of individual multiple-disk 201 or clutch - disk pack, as for example in the type of a multiple disk - or whole metal coupling. The part 181 carrying the windings 91, of the stator or rather the housing 182 is combined via a group of at least two spring items 202 distanced in circumference direction, with the holding medium 98 or rather the bearing block 34. The spring items 202 show in each case at least two multiple disks 201 or clutch-disk pack combined at one and with each other - as for example via a spacer piece 203 - it's other ends are combined with the part 181 carrying the windings 91, of the stator or rather the housing 182 at one side and with the holding medium 97 or rather the bearing block 34 on the other side. The housing 182 or rather the stator 112 can now be relatively moved axially to the holding medium 98 or rather to the bearing block, in doing so the relative movement of the deformation of the spring item 202 is admitted. The group of spring items shows at least two of these spring items 202, which are shifted preferably around 150° to 210° in circumference direction to each other. Through here a radial shifting in axial movement is opposed. In advantageous execution - as represented in Figure 17 - a 26 second, one is assembled in axial direction to the first distanced group spring items 202, in doing so again one end of spring item 202 is assembled "stator fixed" and the, other "bearing block fixed". Through here a tilting of the stator 112 or rather of the housing 182 showing the stator 112 is prevented. In the executions as per the Figures 14 to 17 the windings 91 thus infact are combined rotation fixed with the bearing block 34, however movable in axial direction of the allocated cylinder 06, 07 considered relative to the bearing block 34 (in certain limits as for example at least 1 mm, in particular at least 2 mm). The anti-rotation device 187 making possible an axial relative movement between the part 181 of the stator carrying the windings 91 and the bearing block 34 represents a rotation fixed, coupling 187 admitting however an axial relative movement which with corresponding stops (as for example guide stops out of Figure 15 and 16) or as represented in Figure 17, can be designed via a rotation fixed or rather rotation stiff, however socalled multi-disk-or all-metal coupling 187 admitting an axial relative movement, with corresponding spring packs. In a likewise execution not belonging to the invention, of the drive motor 81 the stator 86 is assembled in axial direction rack-or bearing fixed in doing so the part 183 of the rotor 84 as for example rotor body, carrying the magnet, at least in a definite order of magnitude relative to a cylinder fixed shaft, that means in the result is movable axially relative to the cylinder 06, 07 (Figure 18). The part 183 of the rotor 84 carrying the magnet is however with regard to transmitting torque opposite to the cylinder 06; 07 or rather the shaft 34; 85 is designed rotation fixed via an anti-rotation device 199. The part 183 of the rotor 84 carrying the magnets and the shaft 39; 85 can be moved to each other as for example via slide areas or similarly working media in axial direction. The anti-rotation device 199 making possible an axial relative movement, between shafts 39; 85 and rotor body 183 can be designed either via corresponding stops (as for example in tongue and groove principle or with stops comparable to Figure 15 and 16) or as represented via a rotation fixed or rather rotation stiff, coupling 199 as for example a jib coupling, admitting however an axial relative movement preferably however via a so called multi-disk-or all-metal coupling. In case now as for example the cylinder 06; 07 moves axially then the rotor 84 or rather rotor body 183 is not moved compulsorily along axially, but can remain via magnetic interaction with the stator 86 axially - in the extreme case stationary, in the way that the magnets from stator 86 and rotor 84 can remain in optimal work point to each other. The represented execution variants out of Figure 15 and 18 or rather their principle is so far transferable also on following execution example of the drive motor 81 (or rather other drive motors see below 139; 140; 141; 142; 143; 162; 163) for application. Through the drive motor 81 (or rather other) herein preferably is designed as permanent magnet excited synchronous motor, it can also have in place of permanent magnets 91 corresponding windings for electrical structure of magnet fields. In an execution not belonging to the invention for the drive of the rotating component, as for example a cylinder 06; 07 or a roller, the drive motor 81 to its rotational drive can be designed 60 as external rotor motor 81 in particular like wise with permanent 27 magnet 89 on now out side lying rotor 84 (Figure 19). The rotor 84 is now as for example combined with the casing body of the cylinder 06; 07 or structured through this. The windings 91 of the stator 86 are provided with energy as for example through electric lines 121. The sensor 106 in principle can be combined on different positions rotation fixed with the cylinders 06, 07 and/or to the rotor 84, as for example also on the other front sides of the cylinder 06; 07 and shows as for example a signal line 121 for drive control. In the example it is combined with rotor 84. Stator 86 and rotor 84 are supported on each other over bearing 88, here radial bearing 88. For this the radial bearing 31 in bearing block 34 of the Figure 6 or rather 7 are dispensed with. The stator 86 is combined with the bearing block 34 and together with this, in particular linear movable in the case of not movable rotating components like as for example cylinder of a folding machine or draw roller, this principle without the application of bearing unit 14 can be transmitted. Figure 20 shows likewise a variant not belonging to the invention, in doing so in particular in the case of a cylinder 07 designed as plate cylinder 07, also an axial movement will follow through the drive motor 81. For this the rotor 84 shows a section 121 fixed with permanent magnet 123 in another way. The pole of the permanent magnet 123 alternate here as example in axial direction. In contrast for this as for example the pole alternate in the section of permanent magnet 89 as for example in circumference direction (also in Figure 10, 12 and 15) planned for the rotational drive. Windings 126 different from the windings 91 are lying opposite to the section of permanent magnet 123 planned for the axial movement, which are controllable via internal signal lines 124 from a machine control for the purpose of page recording adjustment. The bearing 88 are designed here as for example as an axial relative movement making possible roller bearing 88. As it is in the case of printer cylinders 06, 07 more number of adjacently assembled rotating components in each case are to be driven through drive motor 81, and the structure size of the drive motor 81 is limited through the distances of rotation axles of the adjacent rotation body, when these overlap in relation to the distances to the allocated component. The motor size rather in particular in the design of drive motors 81 as direct drive without intermediate connection of gears can be possibly greater than the component diameter as for example cylinder diameter. A first possible solution is, as schematically represented in Fig 21, the adjacent drive motor 81 as for example in the execution as per Figure 12 however are to be shifted axially such that they do not overlap in any plane lying vertical to rotation direction. For this the shafts 39 (see Fig 9) can be designed longer or intermediate shafts may be planned. In an advantageous execution, in particular in limited construction space as for example in drive of printer cylinders 06, 07 the stator 86 can be built segmented, that means out of one or more number of segments, which does not surround the full circle circumference or rather which in multiple segments in sum do not surrounded the entire circle circumference. One or more number stator segments 86', surrounded thus purely a circumference angle, which is smaller than 360°, as for example smaller than 28 300°, in particular smaller than 240 . In case two segments are planned then these can be of any advantage depending on design space in circular circumference and surround in each case a circumference angle less than 150° in particular less than 120°. The stator 86 built out of at least one stator segment 86' or rather stator segments 86' or rather the fitting with windings 91, does not reach full circumferentially but only partly around circular circumference. In advantageous design in case of two stator segments 86' these are however assembled oppositely lying that means in circumference direction equally distributed. A first execution variant not belonging to the invention of this execution to the design of the drive is shown in Figure 22 in details. Herein a working area runs between stator 86 and rotor 84 or rather a work area between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86, parallel and as for example co-axially to the rotation axle of the cylinder 06; 07 or the rotating component. The cylinder 06, 07 shows as for example in area of it's casing surface or a front sided structure the permanent magnet 89 in circumference direction. The stator 86 showing the windings 91 is assembled rack fixed out side of the cylinder 06, 07 (or rather a roller), however between the both side racks 11; 12. The stator 86 carrying the windings 91 reaches only over an angle segment (see Figure 23 to 26). The permanent magnets 89 can also be assembled on a neck 21, 22 or a front sided taper of the cylinder 06; 07 or rather of the component. Since the stator 86 here is assembled on the side rack 12 (11) in case of a, if required, movable cylinder 06, 07 the shaping of the stator 86 and/or it's distance to the rotor 84 are to be considered correspondingly (see for this as for example Fig 28). The detailed principle explained in Figure 22 for the segmented stator 86 is represented with the help of Figures 23 to 26 schematically in different variants. Reference symbols for the main components are provided only in Figure 23 a and on ground of shaping and filler sample can be transmitted on remaining variants in simple way. In a first, series of variants represented in the Figures 23 and 24, it deals with assemblies of stator 86 and rotor 84, in doing so one working area lies between stator 86 and rotor 84 or rather one working area between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86 parallel and as for example co-axially to the rotation axle of the cylinder 06; 07 or rather rotating component (short: axle parallel assembly). In the Figure 25 and 26 it deals with assemblies of stator 86 and rotor 84, in doing so one working area between stator 86 and rotor 84 or rather one working area between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86 lies vertical to the rotation axle of the cylinder 06; 07 or rather rotating component (short: axle vertical assembly). Therein in the Figures 23 and 25 it deals with variants, wherein rotor 84 and stator 86 lie on the side of the side rack 12; 11 turned to the cylinders 06; 07 or rather rotating components and in Figure 24 and 26 it deals with variants wherein rotor 84 and stator 86 lie on external side of the side rack 12; 11 turned away from the cylinder 06; 07 or rather rotating components. The Figures 23a, 23c and 25a represent variants belonging to the invention, under consideration of a bearing assembly 14 for the movement of 29 the cylinder 06; 07 or rather a movable component, while the Figures 23b, 23d, 24a, 24b, 25b, 26a and 26b represent variants not belonging to the invention for a usual side wall bearing of the rotating component. Figure wise representation of the Figures 24a and 24b under consideration of bearing assemblies 14 are dispensed with. The Figures 23a, 23b and 24a represent drive motors 81 in the design of an internal rotor motor, while Figure 23c, 23d and 24b represent external rotor motors. In the executions as per the invention, as per Figure 23a, 23c and 25a the stator 86 is assembled in each case on movable part of the bearing assembly 14, in particular on the bearing block 34. The segmented execution of the stators 86 offers various possibilities for space saving assembly, from which in Figure 27 with the help of a double printer 03 four variants on the example of the axle parallel assembly are represented. The theory is to be transmitted correspondingly to other wise executed above mentioned variants. While in Figure 27a the drives of the cylinder 06, 07 in each case have two segment type stator 86 as for example stator segments 86', in the Figures 27b to 27d to each drive only one stator segment 86' is allocated. For the case not belonging to the invention, that the stators 86 or rather stator segment 86' is designed rack fixed and the rotating component, in particular the cylinder 06; 07 is designed movable in a direction vertical to the rotation axle, the stator segment 86' is so executed, that one movement of the cylinder 06; 07 in the border is guaranteed (Figure 28). For this the radius of effective stator area is so selected that the air gap also in the end position of the cylinders 06; 07 is not closed. This is advantageous as for example in assemblies as per Figure 23b, 23d 24a and 24b when the bearing is designed between side rack 12; 11 and neck 22; 21 as eccentric bearing. In the input of more number of stator segments 86' per drive the windings 91 can be connected either parallel or serially and can be operated by a control equipment 127. Also a separate activation of the windings 91 out of different control equipments 127 is conceivable (Fig 29). Only one sensor 106 as for example angular position provider is required which provides all control equipments 127 with the position signals of the actual - signal. The position off set of the stator segment 86' to each other can be correspondingly in parameter in the control equipment 127 or rather to the control equipment 127. A sufficiently exact relative assembly of the stator segment 86' to each other in circumference direction is required, with it the stator segments 86' do not work against each other in operation. For this, maintaining of an exactness of less than one tenth of an angle-distance of the same side of a pair of same named pole following one after the other is of advantage. As for example in case of a pole pair number of 12 in over the angle of as for example 120° reaching segment 24, poles lie with respective distance of the same side of 5°. The distance of same named poles runs up then to 10° and the maximum permissible angle error to 0.1 . Also in this execution, it is advantageous, to design the stator segments 86' liquid cooled. The sensor 106 can be assembled on the rotor 84 it self, on the necks 21, 22 of the same cylinder side or on oppositely lying necks 22, 21. The design with a large pole pair number per drive, as for example 12 pole pairs is of advantage. 30 As indicated in the Figures 27, 28 and 29, in an advantageous execution the rotor 84 can be designed divisible in segments. The rotor 84 is made together out then as for example in circumference direction, of multiple number (as for example three, four, six or eight) rotor segments 84' which in sum cover the full circular circumference of 360° however individually can be assembled / disassembled. The covering is without gap that means there exists as for example between rotor segments 84' no significant deviation from distance pattern of the alternating pole (permanent magnets or also windings) but also a distance of a pair of rotor segments 84' amount to highest 5° in circumference direction. Through here it is specially possible, to assemble or disassemble the rotor 84, without like wise to remove the cylinders 06; 07 or rather the allocated rotating components. For the case of the design of the rotating component as roller or else, in case no construction space problem exists between adjacent cylinders 06; 07, in a fourth not represented execution shape the stator 86 carrying the windings 91, of the Figure 22 to 26, can be designed not segment type rather reaching around the entire circumference of the roller or rather of the cylinder 06, 07. In the execution named to the Figure 6 and 10 for the drive of a cylinder 06; 07, the drive motor 81 is designed in particular as permanent magnet excited synchronous motor 81. The coupling mentioned in Figure 12 is advantageously for a drive motor 81 designed as permanent magnet excited synchronous motor 81, is however advantageously applicable also for other wise designed drive motor 81 as for example asynchronous motor in particular with a resolution gear reducing the speed. In a further execution example for the coupling of rotating component in particular of the component executed as plate cylinder 07, as represented in Figure 30 schematically, in contrast to the execution as per Figure 20 a linear drive for the axial adjustment (page recorder) is integrated in the drive motor 81. The components of the axial and the rotational drive can in principle be assembled in axial direction one after the other (as in Figure 20). In an advantageous variant these are however assembled co-axially to each other and to the motor shaft or rather the shaft 39. In Figure 30 the windings 91; 126 for the radial and the axial drive, the permanent magnet 89; 123 for the radial and the axial drive, the rotor 84 carrying permanent magnet 89; 123 as well as the stator 86 carrying the windings 91; 126 are represented. Further to this, a sensor 106 detecting the position of angle rotation, a sensor 128 detecting the axial position as well as a cooling medium channel is planned. The binding can either be rack fixed via coupling 82 as represented in Figure 6 and 10 or also as indicated in an advantageous execution on bush 98 corresponding to Figure 12. In principle not represented variants are possible, in doing so the rotational drive assembled in Figure 30 externally is assembled inside and the axial drive is assembled outside. Herein the permanent magnets 89; 123 and the windings are to be exchanged. The coupling of the drive motor 81 on the cylinders 06; 07 described on the example of the printer cylinder 06; 07 shows preferably a detachable connection between necks 21; 22 and shaft 39 and motor shaft 85 in such way, that the neck 21; 22 in erected 31 condition of the cylinder 06; 07 does not penetrate the side rack 11; 12. The drive connection between the cylinder 06; 07 and the, drive motor 81 assembled in particular mainly co-axially to the rotation axle of the cylinder 06; 07 is here multi part wise, that means through at least one neck 06; 07 and a shaft 39 combined with this rotation fixed but detachably, which at the same time can represent the motor shaft 85. In addition to the drives for the printer cylinders 06; 07 the printer 04 or rather double printer 03 shows as indicated in Figure 11 at least one drive for a roller 92, in particular changeable roller 92 like as for example friction cylinder 92 of the ink unit 08 and/or of the damping unit 09. The drive of at least one roller 92 can as represented in Figure 11, take place through a front sided drive motor 93 via a gear 94. The drive motor 93 can be designed in principle here as asynchronous motor or synchronous motor. In an advantageous execution of the ink unit drive with regard to a direct coupling without reducing gear the drive motor 93 from Fig. 11 however can be designed as synchronous motor 93, in particular as permanent magnet excited synchronous motor 93. The gear 94 shows herein as for example no rotational reducing gear, rather only one gear converting a rotation movement to a changing movement as for example changing gear. In this first execution for the ink unit drive no internal driving motor for the generation of changing movement is planned. In Figure 11 two friction cylinders 92 in ink unit 08 are planned which as for example may be driven both rotationally and changing via a mechanical drive connection through the drive motor. In a variant only the friction cylinder 92 assembled distanced to plate cylinder 07 is driven rotationally. In a specially advantageous execution the drive motor 93 of the ink unit drive designed as permanent magnet excited synchronous motor 93, however comparable with the drive motor 81 in Figure 30 has a drive motor 93, in which rotational drive as well as axial drive are integrated. To an execution, it is referred to the schematic representation and description to the Figure 30. In Figure 31 base items of the print machine are put together, in doing so in the print units 01 the above represented drive motors 81 for the rotating components 06, 07 designed as print cylinder 06, 07 are planned. Further as for example a roller changer 131 has a drive motor 138 driving a material roller 144 and/or a tension roller 145 of an insertion unit 132 has a drive motor 139 and/or a tension roller 133 post assembled to the printing unit 01 has a drive motor 141 and/or a tensioning roller 136 pre assembled to a folding funnel 134 has a drive motor 142 and/or a tension roller 135 post assembled to a folding funnel 134 has a drive motor 140, and/or at least one cylinder 146; 147; 148 of a folding machine 137 has a drive motor 143. The material roller 144, the tension roller 145, the tension roller 133, the tension roller 135, the tension roller 136, the cylinder 146, 147, 148 represent internally driven rotating components 144; 145; 133; 135; 136; 146; 147; 148 and can be driven in the meaning of above i.v.m rotating components called print cylinder 06; 07 through the drive motors 138,139,141,140,142,143. Herein the drive motors 138; 139, 140, 32 141, 142, 143 in a mentioned way in connection with the print cylinders 06; 07 can be coupled to the allocated component 144, 145, 133, 135, 136, 146, 147, 148, in doing so however in each case the bearing assembly 14 making possible on-/off position can be dispensed with. Also possibly the angle - and/or off set balancing couple can be dispensed with. The drive motor 138, 139, 141, 140, 142, 143 driving the rotating component 144; 145; 133; 135; 136; 146; 147 in advantageous execution as permanent magnet excited and/or as synchronous motor 138, 139, 141, 140, 142; 143 designed drive motor 138; 139; 141; 140; 142; 143 can be designed in above described way. The axial drive planned in a few executions can herein however be dispeused with. Differences can result in nominal and in maximum torque. One or more or all these drive motors 138, 139, 140, 141, 142, 143 can be designed in the type of the drive motor 81 as permanent magnet excited synchronous motor 138, 139, 140, 141, 142, 143. In the print units 01 and in the folding machines 137 and/or in a tension roller 145 (in the fold structure 151 or in insertion unit 132) and/or on the roller changer 138, internal drive motors 81, 138, 139, 141, 140, 142; 143 in particular can be planned as permanent magnet excited and/or as synchronous motor 81; 138; 139; 14; 140; 142; 143 designed drive motors 81; 138; 139; 141; 142; 143. With regard to coupling of synchronous motor 81 iv. m Figure 19 to 26 the mentioned one - however without the bearing assembly 14 - is also transmittable on the rotating component 144, 145, 133, 135, 136; 146; 147; 148, which does not require any axial movement and/or position movement vertical to rotation axle. In the Figure 31, schematically, through a dash pointed line connecting the drive motors 81; 138; 139; 140; 141; 142; 143 a drive control is indicated, which is described closer in Fig 37 below. Figure 32 shows the front view of an execution example a roller changer 131 with the motor 138 designed as synchronous motor 138, in particular with permanent magnet exciting 89 (see above) by means of which the materials roller 144 is driven and wound up. At least one of two cones 149 as for example, is driven through a such type, above described synchronous motor 138 with permanent magnets 89 on rotor 84 and windings 91 on stator 86. The other cone 149, as represented, can be non-driven or like wise can show a that type drive motor 138. The cone 149 is not designed here as expandable, however can also be designed expandable. Figure 33 shows a multiple number folding funnel 134 showing a folding structure 151 with tension rollers 153 driven through drive motors 152, as rotating components 153. Also these drive motors 152 can be designed as described above as directly coupled synchronous motors, in particular permanent magnet excited. In addition to the tension rollers 133, 153 represented in Figure 31 and 29 also driven guide items of a super structure can have a driving motor in the type of a synchronous motor as above described in one of the executions. The drive motor 81 of the cylinder 06; 07 and/or driving motor 93 of the ink unit 08 and/or driving motor 93 of the ink unit 08 and/or the drive motor of the damping unit 33 09 and/or the driving motor 143, 162 in the folding machine 137 and/or the drive motor 139,140,141,142,152,163 of a tension roller 133; 135; 136; 145; 153; 164 (in the super structure and/or in the folding structure 151 and/or at the entry of the folding machine 137) and/or the driving motor 138 of the roller changer 131 can preferably be executed in the above mentioned design of the drive motor 81 as synchronous motor 81 and/or as drive motor 81 permanent magnet exciting. Herein the drive of the cylinders 06; 07 can be subjected advantageously to an angle bearing control and the drive of the tension roller 133, 135, 136, 145, 153, 164 and of roller changer 131 can be subjected to a speed regulation if required with super imposed path tension control. An activation of the drive motor 139; 140; 141; 142; 152; 163 takes place as for example advantageously over an electronic guide axle as mentioned to Figure 37. The folding machine 137 represented schematically in Figure 34 shows as for example cylinder 146, 147, 148 designed one as cutting or rather knife cylinder 146, one as transport cylinder 147 and one as folding gate cylinder 148. The transfer of the folded products can be connectingly given to an impeller 154 and from there to a delivery section 156. At least transport cylinder 147 designed as folding knife cylinder 147 can be executed format variably that means a distance AU in circumference direction between holding medium 157 and respectively post assembled folding knives 158 in circumference of the transport cylinder 147 is executed changeably. For this the holding medium 157, as for example can be executed as punctured ledge or gripper at one side and the folding knife 158 on the other side can be assembled on two different co-axially assembled drums which twist to each in circumference direction. In case the distance A U between holding medium 157 and post assembled folding knife 158 reduces then a product section 161 sectioned by a strand 159 through the knife cylinder transversely in extending of the folding knife 158 to a shorter section length is transversely folded and reversed. The strand 159 can comprise one or more number long folded or unfolded paths 02 or rather part paths. Cutting, transport, fold cylinders 146; 147; 148 and if required impeller 154 are driven preferably through at least one drive motor 143 (M), in particular at least one permanent excited (synchronous) motor 143, mechanically independent of printing units, super structure as well as fold structure. The drive can take place via a gear, in particular a reducing gear, from drive motor 143 to one or more number of cylinders 146, 147, 148 of the folding machine 137. In the execution represented in Figure 34 it is driven from the drive motor 143 via a not represented gear (as for example not indicated pinion or rather drive wheels) on the cutting cylinder 146 (or rather on a multiple number of cutting cylinders). From the last one it is driven on the transport cylinder 147 and from this on fold gate cylinder 148. From the fold gate cylinder 148 if required, it can be driven via a belt drive on the impeller 154. In a not represented variant it is driven from the drive motor 143 via a pinion or drive wheel on the transport cylinder 147. It is driven from the last one on the cutting cylinder 146 and fold gate cylinder 148. It is driven on the impeller 154 from the fold gate cylinder 148 as for example again via the belt drive. In both the described cases 34 the delivery 156 has preferably an internal drive motor 162 (M) mechanically independent from the cylinders 146,147,148 and the impeller 154. Cutting, - transport, and fold gate cylinder 146, 147, 148 and if required impeller 154 can also be driven mechanically independent of each other and from the printers 04 through internal drive motors 143, 162 (M) (Figure 35). In a variant (Figure 36) the three cylinders 146, 147, 148 are jointly and impeller 154 as well as delivery 156 individually driven. In another drive execution, cutting, - transport and fold gate cylinder 146, 147, 148 are driven at least through one joint or alternatively through each one drive motor 143 mechanically independent from the printer, while in a first variant impeller 154 and delivery device 156 are driven rotationally through a joint drive motor mechanically independent of the cylinders 146, 147, 148 and of the print 04 and in a second variant in each case through internal drive motors 143, 162 (M). Also one, if required planned tape system for guiding to the product section 161 in which and through which folding machine 137 can be driven through an internal drive motor 162 (M) mechanically independent of the cylinders 146; 147; 148. The mentioned drive motors 143; 162 (M) as represented above can be designed advantageously as permanent magnet excited synchronous motors 143; 162 (M). In the entry area of the folding machine 137 a like wise tension roller 164 driven through a drive motor 163, as for example a permanent magnet excited, can be assembled as rotating component 164. In fact the drive controls described in the following basically also independent of the specially above described design of the drive motors 81, 138, 139, 140, 141, 142, 143, 162, 163 and of special linear bearing of the cylinders 06, 07 is of advantage. Specially the drive control; however is of advantage for the directly driven component in above mentioned executions. Figure 37 shows an example for the drive of a printing machine with multiple number, here as example two, printing units 01 executed as printing column 01 which show in each case multiple number of printers 04, here double printer 03. The printers 04 of a printing column 01 form together with their drive regulators 166, shortly drives 166 and the drive motors 81, 93 a group 167, as for example drive motor 167 in particular a print position group 167 which via a sub assembled drive control 168 of this group 167 is combined with a signal of a respective guide axle position 0 of virtually a guide axle guiding first signal line 171. The sub assembled drive control 168 can however also control sub groups of printing units 01 or other divisions. With this signal line 171 also further, units, showing an internally sub assembled drive control 168 as for example one or more number control items (as for example tension roller 133, 153, Figure 31, 33) of a super structure and/or folding structure 151 and/or of one or more number folding machinery 137 are combined. In the same way possible combinations to the roller changer 131 and to the insertion unit 132 are not represented here. The signal line 171 is here executed advantageously as a first 35 network 171 in ring topology, in particular as sercos-ring which the guide axle position 0 receives through the coordinated control 172 combined with the network 171. This generates the circulating guide axle position 0 on the basis of preset values with regard to a preset production speed, which it receives from a computer and/or data processing unit 173 as for example a section computer. The computer and data processing unit 173 receives from their side the preset value of the production speed from a control position 174 or rather guide position computer 174 combined with it. In order to guarantee record holding prints and/or longitudinal cutting the mechanically independent from each other driven aggregates (printer 04 as well as folding machine 137), as for example depending on path guiding must stand to each other in correct angle position. Further for the drives 166 requiring individual record holding, off set values A 0 are reserved, which for the production define the correct relative angle position for joint guide axle and/or relative to one of the aggregates. At least this aggregate (print unit 04, as well as folding machinery 137) or rather their drives 166 are subjected to an angle bearing position. Other aggregates leading the path 02 like tension rollers 183, 135, 136 and/or roller changers 131 must not in any case be operated angle position regulated rather can be subjected to a control of number of rotations. The off set values A0 relevant for the individual for the individual drives 166 (at least for drive 166 with record requirement) for the respective production from the computer - and data processing item 173 via a second, signal line 176 different from first signal line 171, in particular a second network 176 are transmitted to sub assembled drive control 168 allocated to the respective drive 166 and in advantageous execution are stored there and processed with the guide axle position 0 to corrected control axle positions 0'. The communication of the offset value A0 on the sub assembled drive controls 168 takes place as for example either via corresponding signal lines from the second network 176 directly for the drive control 168 (not represented) or advantageously via a control system 177 which is allocated to the respective group 167 or rather the unit showing an internal sub assembled drive control 168. The control system 177 is for this combined with the second network 176 (or rather with the computer and data processing unit 173). The control system 177 controls and/or regulates as for example the positioning elements different from the drive motor 81, 93 and drives of printer 04 or rather folding machine 137 as for example ink supply, position movement from rollers and/or cylinders, damping units, positions etc. The control system 177 shows one or more number of (in particular store programmable) control units 178. This control unit 178 is combined via a signal line 179 with the sub assembled drive control 168. In case of multiple number control units 178 these are combined among each other through the signal line 179 as for example a Bus system 179. Via the first network 171 the drives 166 receive thus the absolute and dynamic information for circulation of a joint guide axle position 0 lying at the base and via a second signal path, in particular via at least one second network 176, the informations required for record meeting processing, in particular off set values A 0 are communicated for the record meeting relative position of the drives 166 or rather aggregates independent of each other mechanically. 36 The advantageous features as for example of a printing machine with existing double printers 03 (bearing assembly 14, drive coupling, motor execution as permanent magnet excited synchronous motor) are individually or in combination like wise are to be applied on printing units, that means mainly around 90° rotated double printers 03. Also the features of bearing assembly 14 and/or of the linear actuator travel and/or drive coupling, motor execution are to be applied also on nine-or ten cylinder satellite printing units individually or in combination. 37 Reference number list 01. Printing unit, printing column. 01.1 Part printing unit 01.2 Part printing unit 2. Print material, material path, path 3. Double printer 4. Printer 5. Printing position, double printing position 6. Cylinder, transmission cylinder, printer cylinder, component, rotating 7. Cylinder, plate cylinder, printer cylinder, component, rotating 8. Inking system, roller inking system, short inking system 9. Damping unit, spray damping unit 10. 11. Rack section, wall section, side rack 12. Rack section, wall section, side rack 13. Base, carrier, erection plate, erection frame 14. Bearing assembly, linear bearing assembly, bearing unit 15. Linear guide 16. Rack, frame design (08) 17. Cylinder unit 18. Wall section 19. Handling device, printing block changer 20. 21. Neck (06) 38 22. Neck (07) 23. Rolling element 24. Clamp equipment 25. 26. Barrel (06) 27. Barrel (07) 28. Cover 29. Linear bearing 30. 31. Bearing, radial bearing, cylinder roller bearing 32. Bearing medium, Bearing element, linear element 32.1 Guide area 32.2 Guide area 33. Bearing medium, bearing element, linear element 33.1 Guiding area 33.2 Guiding area 34. Bearing block, slide 35. 36. Combination, clamping item 37. Carrier, carrier plate 38. Recess 39. Shaft, drive shaft 40. 41. Stop, wedge 39 42. Item, spring item 43. Actuator, power controlled, positioning medium pressure medium applicable, piston, hydraulic, piston 44. Stop area (41) 45. 46. Positioning medium, actuator, pressure medium applicable piston 47. Transmission item, piston rod 48. Reset spring 49. Stop, over load safety, spring element 50. 51. Erection help, dowel pin 52. 53. Holding medium, screw 54. Medium, clamping screw 55. 56. Valve, controllable 57. Cover 58. Stop 59. Actuator element 60. 61. Side carrier, side plate 62. Side carrier, side plate 63. Side carrier, side plate 64. Side carrier, side plate 40 65. 66. Page record drive, drive motor 67. Bearing, axial bearing 68. Spindle 69. Spur gear 70. 71. Thread section 72. Pinion 73. Motor 74. Internal thread 75. 76. Pot 77. Stop 78. Disk 79. Rolling element 80. 81. Driving motor, synchronous motor, electro motor, external rotor motor, permanent magnet excited. 82. Coupling, clutch-disk coupling 83. Coupling, jaw coupling 84. Rotor 85. Motor shaft 86. Stator 87. Holding device 88. Bearing, radial bearing, Roller bearing 41 89. Permanent magnet 90. 91. Winding 92. Roller, friction cylinder 93. Driving motor, synchronous motor, permanent magnet excited motor 94. Gear 95. 96. Driving motor 97. Gear 98. Holding medium, bush, collar bush 99. Screws 100. 101. Clamping item, clamping set 102. Clamping item, clamping set 103. Guide, linear guide 104. Support, support plate 105. 106. Sensor, detecting, angle of rotation sensor, angular position provider 107. Anti rotation device 108. Connection port 109. Cooling medium channel 110. 111. Rotor 112. Stator 42 113. Supply 114. Connection 115. 116. Punch 117. Line 118. Breakout 119. Outlet opening 120. 121. Line, electrical 122. Signal line 123. Permanent magnet 124. Signal line 125. 126. Winding 127. Control equipment 128. Sensor 129. 130. 131. Roller changer 132. Insertion device 133. Tension roller, component, rotating 134. Folding funnel 135. Tension roller, component, rotating 136. Tension roller, component, rotating 43 137. Folding machine 138. Driving motor, synchronous motor, permanent magnet excited component, rotating. 139. Driving motor synchronous motor, permanent magnet excited component, rotating. 140. Driving motor, synchronous motor, permanent magnet excited component, rotating. 141. Driving motor, synchronous motor, permanent magnet excited, component rotating. 142. Driving motor, synchronous motor permanent magnet excited, component, rotating. 143. Driving motor, synchronous motor, permanent magnet excited component, rotating. 144. Material roller 145. Tension roller, component, rotating 146. Cylinder, component, rotating, cutting cylinder knife cylinder 147. Cylinder, component, rotating, transport cylinder 148. Cylinder, component, rotating, folding gate cylinder 149. Cones 150. 151. Folding structure 152. Driving motor synchronous motor, permanent magnet exciting, component, rotating. 153. Tension roller, component rotating 154. Impeller 155. 156. Delivery 44 157. Holding medium 158. Folding knife 159. Strand 160. 161. Product section 162. Driving motor, synchronous motor, permanent magnet exciting, component, rotating 163. Driving motor, synchronous motor, permanent magnet exciting, component, rotating 164. Intake roller component, rotating 165. 166. Drive regulator, drive 167. Group, drive motor, print position group 168. Drive control 169. 170. 171. Signal line, network 172. Drive control 173. Computer - and/or data processing unit 174. Control pulpit, control pulpit computer 175. 176. Signal line, network 177. Control system 178. Control unit 179. Signal line, Bus system 45 180. 181. Partofstator 182. Housing 183. Part of the rotor 184. Combination 185. 186. Slide area 187. Anti-rotation - device 188. Stop 189. Guide 190. 191. Holding medium 192. Coupling 193. Stop 194. Guide M Number of rotations P Pressure S Position direction  Guide axle position A 31 Bearing end play A U Distance 46 Claims 1. Rotating cylinder (06) of a printing machine with end sided necks (21; 22) with a drive and a bearing, in doing so the cylinder (06) is designed as transmission cylinder (06) of a linear or angularly designed double printer (03) and is movably assembled at side racks (11; 12) by means of a bearing assembly (14) in a positioning direction (S) vertical to rotation axle of the rotating cylinder (06; 07) and in doing so the end sided necks (21; 22) of the transmission cylinder (06) do not penetrate in erected condition the respective side racks (11; 12), in doing so the transmission cylinder (06) is driven rotationally through an internal drive motor (81) and in doing so the bearing assembly (14) has a movable bearing block (34) for admission of the necks (21; 22) of the transmission cylinder (06, 07), which with regard to the alignment of the side rack (11; 12) is assembled lying on it's internal side, marked through it, that the transmission cylinder (06) with it's barrel (26; 27) and it's neck (21; 22) has a length (L 06) which is smaller or equal to a clear span (L) between the side racks (11; 12) carrying the transmission cylinder (06) to both front sides, that the bearing assembly (14) making possible the movement of transmission cylinder (06) is assembled in such way on the side rack (11) that it's positioning direction (S) for the case of the linear double printer (03) with the plane (E) combining the rotation axles of four cylinders (06; 07) in print-on and for the case of angular double printer (03) with the plane E' combining the rotation axle of the cylinders (06) forming the print position (05), includes maximum angle of 15°, that a rotor (84) of the drive motor (81) is combined firmly but detachably with the neck (21; 22) of the rotating cylinder (06; 07), that a stator (86) of the drive motor (81) is combined firmly but detachably with the movable bearing block (34) in such way that it moves along during position movement and that the drive motor (81) is designed as a synchronous motor (81) with permanent magnet excitement. 2. Rotating cylinder (06; 07) of a printing machine with end sided neck (21; 22) with a drive and a bearing, in doing so the cylinder (06; 07) is designed as plate cylinder (07) of an angularly designed double printer (03) and is assembled movably on a side rack (11; 12) by means of a bearing assembly (14) in position direction (S) vertical to the rotation axle of the plate cylinder (07) and in doing so the front sided necks (21; 22) of the plate cylinder (07) do not penetrate in erected condition the respective side racks (11; 12), in doing so the plate cylinder (07) is driven through an internal drive motor (81) rotationally and in doing so the bearing assembly (14) has a movable bearing block (34) for admission of neck (21; 22) of the plate cylinder (07) which with regard to the alignment of the side rack (11; 12) is assembled lying on it's internal side, marked through it, that the plate cylinder (07) with it's barrel (26, 27) and it's necks (21; 22) has a length (L 07) which is smaller or equal to a clear span (L) between the side racks (11; 12) carrying the plate cylinders (07) to both front sides, that the bearing assembly (14) making possible the movement of the plate cylinder is assembled in such way to side rack (11) that it's positioning direction (S) for the case of linear double printers (03) with the plane (E") combining the rotation axle from plate - and transmission cylinder 47 (07, 06) of the printer includes maximum an angle of 15°, that a rotor (84) of the drive motor (81) is combined firmly but detachably with the neck (21; 22) of the plate cylinder (07), that a stator (86) of the drive motor (81) is combined firmly but detachably with the movable bearing block (34) in such way that it moves along during the position movement and that the drive motor (81) is designed as synchronous motor (81) with permanent magnet excitement. 3. Rotating cylinder (06; 07) as per claim 1 or 2, marked through it, that the rotor (84) of the drive motor (81) is combined rotation fixed but detachable with a shaft (85) and this is combined rotation fixed but detachably with the necks (21; 22) of the rotating cylinder (06; 07). 4. Rotating cylinder as per claim 1 or 2, marked through it, that a holding medium (98) engaging the side rack (11; 12) is combined firmly but detachably with the bearing block (34) and that the stator (86) of the drive motor (81) lying on the external side of the side rack (11; 12) is assembled firmly or detachably on the holding medium (98). 5. Rotating cylinder as per claim 1 or 2, marked through it, that the bearing assembly (14) has rack fixed bearing medium (32) and the movable bearing block (34) admitting the necks (21; 22). 6. Rotating cylinder as per claim 1 or 2, marked through it, that the drive motor (81) is designed without motor internal bearing between stator (86) and rotor (84). 7. Rotating cylinder as per claim 1 or 2, marked through it, that only in the bearing assembly (14) a radial bearing (31) admitting the radial forces between stator (86) and the rotor (84) is planned. 8. Rotating cylinder as per claim 1 or 2, marked through it, that on side rack (11, 12) a medium for support and/or anti rotation device of the drive motor (81), in particular of the stator (86) or rather of it's housing (182) is planned. 9. Rotating cylinder as per claim 8, marked through it, that for support and/or anti-rotation device a guide (103) is planned. 10. Rotating cylinder as per claim 1 or 2, marked through it, that with the rotating cylinder (06; 07) permanent magnets (89) are combined rotation fixed. 11. Rotating cylinder as per claim 1 or 2, marked through it, that the drive motor (81) is designed with motor internal bearing between stator (86) and rotor (84). 12. Rotating cylinder as per claim 1 or 2, marked through it, that the drive motor (81), in particular at least it's rotor (84) is assembled mainly co-axial to the rotation axle of the cylinder (06; 07). 48 13. Rotating cylinder as per claim 1 or 2, marked through it, that the rotor (84) of the drive motor 81 is combined rotation fixed but detachably with a motor shaft (85). 14. Rotating cylinder as per claim 3 or 13, marked through it, a clamp item (102) is planned as combination between rotor (84) and neck (21; 22). 15. Rotating cylinder as per claim 3 or 13, marked through it, that as combination between rotor (84) and motor shaft (85) a clamp items (101) is planned. 16. Rotating cylinder as per claim 4, marked through it, that the holding medium (98) is designed as bush (98). 17. Rotating cylinder as per claim 1 or 2, marked through it, that with the rotor (84) a rotor of a number of revolution-and/or angle of rotation position detecting sensor (106) is combined rotation fixed. 18. Rotating cylinder as per claim 17, marked through it, that a stator of the sensor (106) is assembled over an anti-rotation device (107) on the drive motor (81) in such way that the stator shows a radial degree of freedom, in particular of at least 2 mm. 19. Rotating cylinder as per claim 1 or 2, marked through it, that the rotor (84) of the drive motor (81) has pole out of permanent magnets (89). 20. Rotating cylinder as per claim 1 or 2, marked through it, that on the drive motor (81) a cooling equipment, in particular a liquid circuit is planned. 21. Rotating cylinder as per claim 1 or 2, marked through it, that on the drive motor (81) a rotation transmitter (111, 112) is planned. 22. Rotating cylinder as per claim 1 or 2, marked through it, that the bearing assembly (14) has a bearing block (34) and two linear bearings (29) engaging the bearing block (34). 23. Rotating cylinder as per claim 1 or 2, marked through it, that the bearing assembly (14) encloses an actuator (43) integrated in the bearing assembly (14) for managing the actuator travel. 24. Rotating cylinder as per claim 23, marked through it, that both the linear bearings (29) lie opposite to each other in the way and engage the bearing block (34) that the bearing pre-stress and the bearing forces, experience or rather admit a main component in a direction perpendicular to the rotation axle of the cylinder (06, 07). 25. Rotating cylinder as per claim 1,2 or 3, marked through it, that the bearing assembly (14) has linear bearing (29), by means of which the rotation body is movable linear. 49 26. Rotating cylinder as per claim 25, marked through it, that the rotation body together with bearing unit (14) is designed pre erectable. 27. Rotating cylinder as per claim 1 or 2, marked through it, that the drive motor (81) receives from a signal line (171) guiding a virtual guide axle, signals for pre-set angle position and/or angle speed and/or guide axle position (0). . 28. Rotating cylinder as per claim 19, marked through it, that the permanent magnets (89) have rare-earth-materials. 29. Rotating cylinder as per claim 1 or 2, marked through it, that the rotor (84) of the drive motor (81) is supported movable axially relative to the side rack (11; 12) and that the rotor (84) and the stator (86) of the drive motor (81) working with this together are supported movably relative to each other in axial direction. 30. Rotating cylinder as per claim 29, marked through it, that the stator (86) is supported movable with regard to an axial direction of the cylinder (06; 07) relative to the side rack (11; 12). 31. Rotating cylinder as per claim 30, marked through it, that the stator (86) is combined at least in directly rotation fixed with the side rack (11; 12). 32. Rotating cylinder as per claim 31, marked through it, that a housing (182) of the drive motor (81) is at least indirectly combined in axial direction of the cylinder (06, 07) pressure - and pulling stiff with the side rack.(l 1; 12). 33. Rotating cylinder as per claim 32, marked through it, that the housing (182) is combined at least indirectly with a part of a bearing assembly (14) which from it's side is combined in axial direction of the cylinder (06, 07) pressure - and pulling stiff with the side rack (11, 12). 34. Rotating cylinder as per claim 30, marked through it, that the rotor (84) is combined at least in directly in axial direction pressure - and pulling stiff, with the cylinder (06, 07). 35. Rotating cylinder as per claim 29, marked through it, that the stator (86) with regard to an axial direction of the cylinder (06, 07) is assembled rack fixed. 36. Rotating cylinder as per claim 1 or 2, marked through it, that the stator (86) has at least one stator segment (86'), which with regard to it's working area in circumference direction working together with the rotor (86) reaches only via an angle segment less than 360°. 37. Rotating cylinder as per claim 36, marked through it, that only one stator segment (86') working together with the rotor (84) is planned. 50 33. Rotating cylinder as per claim 36, marked through it, that in circumference direction, distanced from each other, multiple number, in particular two, stator segments (86') working together with the rotor (84) are planned. 51 39. Rotating cylinder as per claim 36, marked through it, that the stator segments (86'), in sum less than 300°, in particular less than 240° cover the full circumference. 40. Rotating cylinder as per claim 1, 2 or 36, marked through it, that the rotor (84) is designed in circumference direction considered out of multiple number of individual rotor segments (86') erectable on a shaft. 41. Rotating cylinder as per claim 40, marked through it, that the rotor segments (86') in sum cover the full circle circumference of 360°. 42. Rotating cylinder as per claim 40, marked through it, that the rotor segments (86') have permanent magnets (89). 43. Rotating cylinder as per claim 40, marked through it, that the rotor segments (86') have windings for electrical magnetic field generation. 44. Rotating cylinder as per claim 1, 2 or 6, marked through it, that the drive motor (81) is designed as external rotor motor with internally lying stator (86). 45. Rotating cylinder as per claim 1, 2 or 6, marked through it, that the drive motor (81) is designed as internal rotor motor with externally lying stator (86). 46. Rotating cylinder as per claim 1, 2, 3 or 13, marked through it, that as detachable combination a detachable shape-or force fitting combination is planned. The invention relates to a drive unit of a rotating component (06; 07) of a printing press, said component (06; 07) being disposed on lateral frames (11; 12) by means of a bearing assembly (14) so as to be movable in one direction, perpendicular to the axis of rotation of the component (06; 07). The component (06; 07) is rotatably driven by an independent driving motor (81) while a journal (21; 22) of the component (06; 07) does not penetrate an alignment of the lateral frame (11; 12) in the mounted state. A rotor (84) of the driving motor (81) is joined to the journal (21; 22) of the component (06; 07) in a torsion-proof, detachable manner. The bearing assembly (14) is provided with a movable bearing block (34) for accommodating the journal (21; 22) of the component (06; 07), which is located on the inside of the bearing assembly relative to the alignment of the lateral frame (11; 12). A stator (86) of the driving motor (81) is rigidly and removably connected to the movable bearing block (34).

Documents:

04333-kolnp-2007-abstract.pdf

04333-kolnp-2007-claims.pdf

04333-kolnp-2007-correspondence others.pdf

04333-kolnp-2007-description complete.pdf

04333-kolnp-2007-drawings.pdf

04333-kolnp-2007-form 1.pdf

04333-kolnp-2007-form 2.pdf

04333-kolnp-2007-form 3.pdf

04333-kolnp-2007-form 5.pdf

04333-kolnp-2007-international publication.pdf

04333-kolnp-2007-international search report.pdf

04333-kolnp-2007-others pct form.pdf

04333-kolnp-2007-others.pdf

04333-kolnp-2007-pct priority document notification.pdf

04333-kolnp-2007-pct request form.pdf

04333-kolnp-2007-translated copy of priority document.pdf

4333-KOLNP-2007-(13-08-2012)-CORRESPONDENCE.pdf

4333-KOLNP-2007-(29-03-2012)-CORRESPONDENCE.pdf

4333-KOLNP-2007-(29-03-2012)-ENGLISH TRANSLATION.pdf

4333-KOLNP-2007-(29-03-2012)-PETITION UNDER RULE 137.pdf

4333-KOLNP-2007-ABSTRACT.pdf

4333-KOLNP-2007-CORRESPONDENCE 1.5.pdf

4333-KOLNP-2007-CORRESPONDENCE OTHERS 1.1.pdf

4333-kolnp-2007-CORRESPONDENCE OTHERS 1.2.pdf

4333-KOLNP-2007-CORRESPONDENCE OTHERS 1.3.pdf

4333-KOLNP-2007-CORRESPONDENCE-1.3.pdf

4333-KOLNP-2007-CORRESPONDENCE-1.4.pdf

4333-KOLNP-2007-DESCRIPTION (COMPLETE).pdf

4333-KOLNP-2007-DRAWINGS.pdf

4333-KOLNP-2007-EXAMINATION REPORT REPLY RECIEVED.pdf

4333-KOLNP-2007-EXAMINATION REPORT.pdf

4333-KOLNP-2007-FORM 1.pdf

4333-kolnp-2007-FORM 18.pdf

4333-KOLNP-2007-FORM 2.pdf

4333-KOLNP-2007-FORM 26.pdf

4333-KOLNP-2007-FORM 3 1.1.pdf

4333-KOLNP-2007-FORM 3.pdf

4333-KOLNP-2007-FORM 5.pdf

4333-KOLNP-2007-GRANTED-ABSTRACT.pdf

4333-KOLNP-2007-GRANTED-CLAIMS.pdf

4333-KOLNP-2007-GRANTED-DESCRIPTION (COMPLETE).pdf

4333-KOLNP-2007-GRANTED-DRAWINGS.pdf

4333-KOLNP-2007-GRANTED-FORM 1.pdf

4333-KOLNP-2007-GRANTED-FORM 2.pdf

4333-KOLNP-2007-GRANTED-LETTER PATENT.pdf

4333-KOLNP-2007-GRANTED-SPECIFICATION.pdf

4333-KOLNP-2007-OTHERS 1.3.pdf

4333-KOLNP-2007-OTHERS-1.1.pdf

4333-KOLNP-2007-OTHERS-1.2.pdf

4333-KOLNP-2007-PA.pdf

4333-KOLNP-2007-PETITION UNDER RULE 137.pdf

4333-KOLNP-2007-PRIORITY DOCUMENT-1.1.pdf

4333-KOLNP-2007-PRIORITY DOCUMENT.pdf

4333-KOLNP-2007-REPLY TO EXAMINATION REPORT.pdf

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