WO2007051660A1 - Entrainement d'un composant rotatif d'une machine d'impression - Google Patents

Entrainement d'un composant rotatif d'une machine d'impression Download PDF

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Publication number
WO2007051660A1
WO2007051660A1 PCT/EP2006/063400 EP2006063400W WO2007051660A1 WO 2007051660 A1 WO2007051660 A1 WO 2007051660A1 EP 2006063400 W EP2006063400 W EP 2006063400W WO 2007051660 A1 WO2007051660 A1 WO 2007051660A1
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WO
WIPO (PCT)
Prior art keywords
cylinder
drive
bearing
stator
drive motor
Prior art date
Application number
PCT/EP2006/063400
Other languages
German (de)
English (en)
Inventor
Karl Robert SCHÄFER
Bernd Kurt Masuch
Georg Schneider
Original Assignee
Koenig & Bauer Aktiengesellschaft
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Koenig & Bauer Aktiengesellschaft filed Critical Koenig & Bauer Aktiengesellschaft
Priority to EP06777397A priority Critical patent/EP1943099A1/fr
Publication of WO2007051660A1 publication Critical patent/WO2007051660A1/fr

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/004—Electric or hydraulic features of drives
    • B41F13/0045—Electric driving devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/70—Driving devices associated with particular installations or situations
    • B41P2213/73—Driving devices for multicolour presses
    • B41P2213/734—Driving devices for multicolour presses each printing unit being driven by its own electric motor, i.e. electric shaft

Definitions

  • the invention relates to drives of a rotating component of a printing press according to the preamble of claim 1 or 10.
  • EP 0 699 524 B1 drive trains of printing units are disclosed, wherein in one embodiment, a single drive of the printing cylinder is effected by a single motor.
  • the rotor carrying the windings is axially movable relative to a stator fixed to the stator.
  • DE 195 34 651 A1 discloses a printing unit with lying in a plane cylinders, wherein three of four cylinders along the cylinder plane to the pressure-on or pressure-off position are mounted linearly movable.
  • the storage takes place in arranged on the frame inner wall guide elements.
  • the cylinders are mounted on the common guide elements in carriers, by pressure medium-operated working cylinder to each other on / off and rotatable by drive motors.
  • WO 03/025406 A1 discloses a bearing arrangement for cylinders, in which a carriage encompassing a linear guide can be moved by an actuator arranged on the frame.
  • EP 1 175 300 B1 shows a flexographic printing machine with a forme cylinder driven directly on the pin, wherein the motor is mounted on a slider which is arranged on a supporting shoulder of the machine frame.
  • the invention has for its object to provide simply constructed yet powerful drives a movably mounted rotating component of a printing press.
  • the achievable with the present invention consist in particular in that a particularly simple drive of a single driven, axially movably mounted rotary body of the printing machine is created.
  • the special, a relative axial direction enabling coupling of the stator and / or rotor allows a direct drive, despite the possible axial movements of the component inside the motor allows an advantageous relative position between the rotor and stator.
  • a particularly strong drive of the rotating body is created in small dimensions by small diameter motors in a special design by permanent magnet motors.
  • the motor in which can be dispensed with an internal motor bearing between the stator and rotor, the motor is particularly simple and / or is particularly low maintenance in terms of wearing parts.
  • the motor is designed with a particularly high drive power at the same time small size. Furthermore accounts for this electrical transmission means, for. B. sliding contacts on a rotating component, eg. As the rotor when the rotor for forming the magnetic field instead of electromagnetically excited coils permanent magnets.
  • the stator in the axial direction is not steep or camp-proof, but - at least in a certain order of magnitude - arranged axially movable, but he viggegesichtert with respect to torques occurring, z. B. relative to the side frame and / or a storage unit may be formed.
  • stator can be axially guided by magnetic interaction in such a way that the magnets of the stator and rotor can remain at the optimum operating point relative to one another, ie the stator is considered in an extreme case relative to the rotor can remain stationary.
  • the stator may be arranged in the axial direction staid or fixed bearing, wherein the rotor body carrying the magnets - at least in a certain order - relative to a cylinder-fixed shaft axially movable, but with respect to torque to be transmitted the cylinder or the shaft is formed nadorehgesichtert. If, for example, the cylinder is moved axially, then the rotor is not necessarily moved axially, but can remain in axial fashion - in extreme cases stationary via magnetic interaction with the stator - so that the magnets of stator and rotor can remain at the optimum operating point.
  • the storage inside of the side frames allows in addition to the simple installation and the reduction of cylinder pin, which is vibration-reducing and also space-saving effect.
  • Fig. 1 is a schematic representation of a printing unit
  • FIG. 2 shows a first operating position of a first embodiment of a printing unit
  • FIG. 3 shows a second operating position of a first embodiment of a printing unit
  • Fig. 5 is a plan view of a double printing
  • Fig. 6 is a schematic longitudinal section through a storage unit
  • FIG. 7 shows a schematic cross section through a storage unit
  • Fig. 8 is an enlarged view of the linear bearing of Fig. 6; 9 shows a coupling of a cylinder to a side register drive;
  • FIG. 10 shows a first embodiment for the coupling of a drive motor to a cylinder.
  • FIG. 11 shows an embodiment for driving a printing unit
  • FIG. 12 shows a second embodiment for the coupling of a drive motor to a cylinder.
  • Fig. 13 is a schematic 3-D representation of a rotor
  • FIG. 14 shows a further schematic representation of a stator
  • Fig. 15 shows a variant of the drive motor of Fig. 12;
  • FIG. 16 shows an embodiment variant of the drive motor from FIG. 12;
  • FIG. 17 shows an embodiment variant of the drive motor from FIG. 12;
  • FIG. 18 shows an embodiment variant of the drive motor from FIG. 12; FIG.
  • FIG. 19 shows a third embodiment of the drive of a rotary body, in particular cylinder
  • FIG. 20 shows a variant of the third embodiment of the drive of a rotary body, in particular cylinder;
  • FIG. 21 shows an axially staggered arrangement of adjacent drive motors;
  • FIG. 21 shows an axially staggered arrangement of adjacent drive motors;
  • FIG. 22 shows a segmented embodiment of the drive of a rotation body, in particular a cylinder
  • Fig. 23 variants of a segmented drive motor with axis-parallel arrangement
  • Fig. 24 variants of a segmented drive motor with achsvertikaler arrangement
  • Fig. 25 variants of a segmented drive motor with achsvertikaler arrangement
  • Fig. 26 variants of a segmented drive motor with achsvertikaler arrangement
  • FIG. 27 shows arrangements of stator segments of adjacent drive motors
  • FIG. 28 shows an embodiment of a stator segment for a movable component
  • FIG. 30 shows a further embodiment for the coupling of the drive motor to a rotating component with integrated axial drive
  • Fig. 31 is a schematic diagram of a printing machine
  • Fig. 32 is a front view of a roll changer
  • Fig. 34 is a schematic view of a folder
  • Fig. 35 shows a second embodiment of a folding apparatus
  • Fig. 36 shows a third embodiment of a folding apparatus
  • Fig. 37 shows an embodiment of a drive of a printing press.
  • a printing machine, z. B. web-fed rotary printing press, in particular a multi-color web-fed rotary printing press, has a printing unit 01, in which a substrate 02, z. B. a web of material 02, short web 02 on both sides simply or in particular successively on both sides repeatedly, z. B. here four times, or multiple webs simultaneously one or more times by printing units 04 are printable. It can also be provided one or more printing units 01 or printing units 04, in which a web 02 at the printing point 05 is only one-sided printable.
  • the printing units 04 have printing cylinder 06; 07, which are to be set in pairs in print-on.
  • one or more of the printing cylinder 06; 07 and / or other rotating components - have their own, at least from other printing units 04 or other units mechanically independent - drive motor (see below).
  • This is preferably substantially coaxial with the printing cylinder 06; 07 arranged and in an advantageous embodiment without intermediate gear to the printing cylinder 06; 07 docked.
  • the printing unit 01 has a plurality of (in the present case four) vertically stacked double printing units 03 for double-sided printing in rubber-against-rubber operation.
  • the double printing units 03 - shown here in the form of bridge or n-printing units - are each formed by two printing units 04, which each have a cylinder 06 formed as a transfer cylinder 06 and cylinder 07 as a forme cylinder; 07, z. B. printing cylinder 06; 07, and in each case have an inking unit 08 and in the case of wet offset printing additionally a dampening unit 09.
  • a (double) pressure point 05 is formed in Anstelllage.
  • the aforementioned components are designated only at the top double printing unit 03 of Figure 1, wherein the stacked (double) printing units 03; 04, however, essentially - are executed identically - in particular in the embodiment of the relevant features of the invention.
  • the double printing units 03 can - as well as the advantageous feature of the linear arrangement described below - just as well be embodied contrary to the illustration in FIG. 1 as an upwardly opening U unit.
  • the printing unit 01 in an advantageous embodiments, for. B. in the middle, d. H. in the region of the double pressure point (s) 05, or as shown in Fig. 4, between form cylinder (s) 07 and inking unit (s) 08 operatively designed to be divisible.
  • exemplary bearing assemblies 14 are shown, which -. B. for the purpose of on / off - a movement of the respective Cylinder 06; 07 in a direction perpendicular to its axis of rotation allows.
  • This can in principle an eccentric bearing arrangement, a lever arrangement or in an advantageous embodiment (see below) a linear bearing assembly 14, for. B. be a storage unit 14.
  • the inking units 08 can be designed as modules already having a plurality of rollers with their own frame 16 or a frame construction 16 and can be used as preassemblable modules in the printing unit 01.
  • the cylinder 06; 07 associated with them bearing units 14 may be formed as preassembled or preassembled cylinder units 17.
  • the axes of rotation of the printing cylinder 06; 07 of a printing unit 04 in pressure-An be substantially lying in a common plane E lying.
  • the plane E takes z. B. an angle between 76 ° and 87 °, in particular between 80 ° and 85 ° to the plane of the incoming web 02 a.
  • FIGS. 2 and 3 an advantageous embodiment of the printing unit 01 is shown, wherein in the region of its double pressure point (s) 05, operationally, d. H. for setup and maintenance purposes (as opposed to disassembly or disassembly), is divisible executed.
  • the two separable parts are referred to here with partial pressure units 01.1 and 01.2.
  • the printing cylinder 06; 07 more, in particular all the web 02 on the same side printing printing 04 on the same frame or wall section 11; 12 stored.
  • the Printing cylinder 06; 07 can in principle only be mounted on one side, ie flying on only one end frame frame sections 11.
  • each partial pressure unit 01.1; 01 .2 two front side to the cylinders 06; 07 arranged frame sections 11; 12 provided.
  • the two separable partial pressure units 01.1 and 01.2 have the respective frame sections 11; 12 and printing units 04 (printing cylinder 06, 07 and inking units 08 and possibly dampening unit 09) on.
  • the partial printing units 01 .1; 01.2 are along a direction perpendicular to the axis of rotation of the cylinder 06; 07 toward each other or away from each other by preferably one of both spatially fixed (here partial pressure unit 01 .1), d. H.
  • the outer frame sections 12 in mutually corresponding, in non-illustrated bearing elements of the frame portion 12 and the carrier 13, z. B. together a linear guide 15 forming, stored.
  • These can be designed as running in rails rollers or as a sliding or rolling body mounted mutually associated linear guide elements.
  • the wall sections 1 1; 12 are formed so that they are formed in their operating position A (Fig. 2) on its side facing each other in pairs substantially complementary to each other form and together at their dividing lines or lines of attack nevertheless form a substantially closed side front.
  • FIG. 3 shows a maintenance position B of the printing unit 01 (without the bearing units 14 indicated in FIG. 2), the relative position of the partial printing units 01 .1; 01.2 each other by moving the frame sections 12 is effected.
  • the relative position can in principle be achieved in another embodiment by both partial pressure units 01.1; 01 .2 or their frame sections 11; 12 are movably mounted.
  • FIG. 4 In a variant (FIG. 4) of a divisible pressure unit 01, the side frame 11; 12 not divisible in the manner that the printing cylinder 06; 07 are separated at the pressure point 05, but it is the printing cylinder 06; 07 in or on a common side frame 11; 12 stored undivided, while on both sides of the inking units 08 receiving wall sections 18 in an operating position A (not shown) or a maintenance position B (shown) can be brought.
  • the division takes place here between form cylinder 07 and dyeing and possibly dampening unit 08; 09th
  • Shaping and transfer cylinder 07; 06 can in an advantageous format design with a bale width of at least four, z. B. four or for particularly high product output six, juxtaposed standing printed pages in newspaper format, especially in broadsheet format, be formed.
  • the cylinder 06; 07 has a circumference which essentially corresponds to two printed pages arranged one behind the other in a newspaper format, in particular in broadsheet format.
  • the forme cylinder 07 can then be equipped with four or six printing forms side by side and two printing plates in succession.
  • the transfer cylinder 06 has a double large format (two newspaper pages in the scope behind each other) in one embodiment z. B. only one channel for receiving one or more juxtaposed blankets, which is preferably formed continuously over the entire effective bale length.
  • the transfer cylinder 06 can then be equipped with a continuous over the bale length and extending over substantially the full extent or with two or three over substantially the full extent reaching blankets side by side.
  • this two or three blankets can have side by side, wherein the respective adjacent to each other are offset by 180 ° in the circumferential direction.
  • These staggered blankets can be kept in two or three channel sections, which are also in the longitudinal direction of the cylinder 06 side by side, the respective adjacent channel sections in the circumferential direction, however, offset from each other by 180 °.
  • the cylinder 06; 07 but also with a simple scope - a print page in particular newspaper page in the circumferential direction - be formed. It may be the transfer cylinder 06 also formed with double circumference and the forme cylinder 07 with a simple scope. In printing units 04 for commercial printing, the cylinder 06; 07 may also be formed with enclosing, which corresponds to four lying tabloid sides.
  • the inking unit 08 may be formed in different ways. So it can be exemplified as shown in Fig. 1 z. B. as fashionghiges roller inking system 08 z. B. with two Reibzylindern (eg., From the newspaper printing) or as shown by way of example in Fig. 2 and Fig. 3 as short inking units 08 using a cup or Haschuren having anilox roller may be formed. In unillustrated embodiment, it can also be used as a roller inking unit 08 with two color trains and z. B. three friction cylinders (eg., From the commercial printing) to be executed.
  • the dampening unit 09 can be configured as a dampening unit 09 with at least three rollers (shown in FIG. 1). Preferably, the dampening unit 09 as so-called. Contactless dampening unit 09, in particular spray dampening 09, executed. As also indicated in FIGS. 2 and 3, the printing units 04 can each have a handling device 19 for supporting the printing form change. In a preferred embodiment, the handling device 19 is designed as an at least semi-automatic or even fully automatic printing plate changer 19.
  • the coupling of the drive to the cylinder 06; 07 may be a pressure-on-places of printing cylinders 06; 07 or at least a pressure-on points in the context of presetting a wegbegrenzenden stop by at least one actuator 43, in particular by a force-controlled or a force defined actuator 43, by means of which for employment a defined or definable force F in pressure -An direction on the cylinder 06; 07 or its pin 21; 22 is brought.
  • the decisive for the color transfer and thus the print quality, inter alia, line force in the Nippstellen is therefore not by an indirect parameter such.
  • the actuator 43 provided in the above embodiment of the bearing units 14 is designed to provide a travel suitable for engagement or disengagement ⁇ S and therefore preferably has a stroke corresponding at least to ⁇ S.
  • the actuator 43 is provided for adjusting the Anstell horres to each other employees rollers or cylinders 06, 07 and / or to carry out the pressure on - / - down position and designed accordingly.
  • the travel ⁇ S (or stroke) is for example at least 0.5 mm, for the forme cylinder 07 in particular at least 1 mm.
  • At least one cylinder 06 (07) during a period when setting - without effective Wegbegrenzung to pressure point out - only force controlled to the adjacent cylinder 06 (07) is adjustable.
  • a cylinder 06 involved in the pressure point 05 can be fixed in a defined position, advantageously in the position of adjustment found by the equilibrium of forces, or at least delimited in the direction of the pressure point 05.
  • Fig. 5 shows in plan view of the side frames in bearing units 14 rotatably mounted cylinder 06; 07.
  • modules see below to Fig. 6 and Fig. 7
  • Bearing unit 14 and cylinder 06; 07 get before their insertion into the printing unit 01 their firmly defined position to each other and are collectively in the printing unit 01 introduced.
  • the cylinder 06; 07 in storage units 14 on the side frames 1 1; 12 rotatably store, which the escape of the side frames 1 1; 12 do not penetrate and / or the cylinder 06; 07 with her bale 26; 27 including their pin 21; 22 a length L06; L07, which is less than or equal to a clear width L between the printing cylinder 06; 07 to both end faces supporting side frames 11; 12 ( Figure 5).
  • all four printing cylinder 06; 07 (but at least three) has its own storage unit 14, in which the on / off mechanism is already integrated. It can also for three of the four cylinders 06; 07 the bearing / Abstellmechanismus having bearing units 14 and be provided for the fourth bearing units 14 without on / off mechanism.
  • FIGS. 6 and 7 show a bearing unit 14, preferably based on linear travel paths, in schematic longitudinal and cross-section.
  • the on / off mechanism integrating bearing unit 14 has in addition to a bearing 31, for. B. radial bearing 31, for example, a cylindrical roller bearing 31, for rotatably supporting the cylinder 06; 07, storage means 32; 33 or bearing elements 32; 33 for a radial movement of the cylinder 06; 07 - for pressure on or pressure off - on.
  • the bearing unit 14 (after mounting the bearing unit 14 frame-fixed) carrier-resistant bearing elements 32 and the movable against these bearing elements 33.
  • the carrier-fixed and movable bearing elements 32; 33 are as co-operating linear elements 32; 33 and together with corresponding sliding surfaces or rolling elements between them formed as a total of 29 linear bearings.
  • the linear elements 32; 33 take in pairs a radial bearing 31 receiving bearing block 34, z. B. slide 34 between them.
  • Bearing block 34 and the movable bearing elements 33 may also be made in one piece.
  • the carrier-fixed bearing elements 32 are arranged on a carrier 37, which in total with the side frame 11; 12 is connected or is.
  • the carrier 37 is designed for example as a support plate 37, which, for example, at least on a drive side, a recess 38 for the passage of a shaft 39, z. B. drive shaft 39 of a pin 21, not shown in Fig.
  • the side frame 1 1; 12 on the drive side preferably has a recess or an opening for a drive shaft 39.
  • the opposite side of the drive side does not necessarily have a recess 38 or a recess in the side frame 12; 11 may be provided.
  • the advantageous arrangement of the two bearing block 34 encompassing linear bearing 29 allows a backlash-free setting, since the two linear bearings 29 are opposed in such a way that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 06; 07 learn or record.
  • the linear bearings 29 are thus adjustable in the direction to which it is at play-free positions of the cylinder 06; 07 also arrives.
  • the arrangement of the linear bearings 29 also has particular advantages in terms of stiffness and stability. This is particularly necessary in connection with an embodiment of a coupling of a stator (86, see below) to the bearing block 34.
  • the linear bearings 29 (32, 33) which can be seen in FIGS. 6 and 7 thus each have pairs of corresponding cooperating bearing means 32 and 33 or their guide or effective surface areas, designed as sliding surfaces (not shown) or with rolling bodies 23 arranged therebetween.
  • at least one of the two advantageous two linear bearings 29 of a bearing unit 14 is designed such that the two corresponding bearing means 32 and 33 each have at least two guide surfaces 32.1; 32.2; 33.1; 33.2, which in two mutually inclined planes E1; E2 are lying.
  • the two guide surfaces 32.1; 32.2; 33.1; 33.2 (or their planes E1, E2) of the same bearing means 32; 33 are z.
  • the two guide surfaces 33.1; 33.2; 32.1; 32.2 of the cooperating bearing means 33; 32 are inclined to complementary shape. At least one of the two pairings of cooperating guide surfaces 32.1; 32.2; 33.1; 33.2 is parallel to a plane E1, which has a component not equal to zero in the radial direction of the cylinder axis and thereby the degree of freedom of movement in a purely axial direction of the cylinder 06; 07 stops.
  • both pairings lie to planes E1; E2, which both have a component not equal to zero in the radial direction of the cylinder axis, but in reverse tilt against the cylinder axis and thereby the degree of freedom of movement in both axial directions of the cylinder 06; 07 stop.
  • a section line of the two planes E1; E2 is parallel to the direction S
  • the inclined active or guide surfaces 32.1; 32.2; 33.1; 33.2 are arranged so that they a relative movement of the bearing parts of the linear bearing 29 in the axial direction of the cylinder 06; Counteract 07, d. H. the bearing is "tied off" in the axial direction.
  • the linear bearings 29 both a cylinder 06; 07 frontally associated bearing units 14 two mutually arranged pairs of cooperating guide surfaces 32.1; 32.2; 33.1; 33.2.
  • at least one of the two radial bearings 31 of the two bearing units 14 has a slight bearing clearance ⁇ 31 in the axial direction.
  • assembly aids 51, z. B. dowel pins 51 in the side frame 11; 12 may be provided, to which the bearing unit 14 of the fully assembled cylinder unit 17 is aligned, before they by releasable holding means 53, z. B. screws 53, or even cohesively by welding to the side frame 1 1; 12 are connected.
  • corresponding means 54 e.g. B. Clamping screws 54 may be provided (Fig. 6).
  • the bearing unit 14 - at least to the cylinder side - by a cover 57 largely protected against contamination or even encapsulated executed as a unit.
  • Fig. 6 is schematically the cylinder 06; 07 with pin 21; 22 and a preassembled storage unit 14.
  • This module can thus be preassembled between the side frames 1 1; 12 of the printing unit 01 used for easy installation and attached to designated locations.
  • the effective inner surface of the radial bearing 31 and the outer effective lateral surface of the pin 21; 22 be cylindrical instead of tapered, since both the mounting of the bearing unit 14 on the pin 21; 22 as well as the setting of the bearing clearance outside of the printing unit 01 can be done.
  • the storage unit 14 can be shrunk, for example.
  • the mountable as a whole unit is advantageous in the manner of an optionally partially open housing of z. B. the carrier 37, and / or z. B. a frame (in Fig. 7, for example, the four the storage unit 14 to all four sides outwardly bounding side supports 61, 62, 63, 64, eg side plates 61, 62, 63, 64 and / or
  • the cover 57 (FIG. 6) is housed within this housing or this frame, the bearing block 34 having the radial bearing 31, the linear bearings 29 and, in an advantageous embodiment, the actuator 43 or the actuators 43, for example.
  • the frame-fixed bearing elements 32 are arranged substantially parallel to one another and define a positioning direction S (FIG. 7).
  • Pressure is applied by moving the bearing block 34 in the direction of the pressure point 05 by means of a by at least one actuator 43 applied to the bearing block 34 Force F, in particular by a force-controlled or a force defined actuator 43, by means of which for employment a defined or definable force F in pressure-on direction to the bearing block 34 can be brought (Fig. 7).
  • the decisive for the color transfer and thus the print quality, among other line force in the Nippstellen is therefore not by a travel, but by the balance of power between the force F and between the cylinders 06; 07 resulting line force F L and the resulting equilibrium defined.
  • cylinder 06; 07 employed in pairs by the bearing block 34 is acted upon by the correspondingly set force F on the / the actuator (s) 43.
  • F the correspondingly set force
  • At least the two middle of the four cylinders 06 - or in other words, at least all of the two outer cylinders 07 different cylinder 06 at least during a period of time Setting in a defined position, advantageously in the Anstelllage found by the equilibrium of forces, can be fixed or at least wegbegrenzbar.
  • bearing block 34 even during operation - at least in one direction away from the pressure point 05 against a force, for. B. spring force, in particular a definable force, is movably mounted. This is - in contrast to the pure travel limit - on the one hand, a maximum line force when working together cylinder 06; 07 defined, and on the other hand a yielding, for example, in a web break with subsequent winder on the cylinder 06; 07, allows.
  • the bearing unit 14 - at least during the setting process - a location-adjustable stop 41, which limits the travel to the pressure point 05 out.
  • the stop 41 can be moved in such a way that the stop surface 44, which acts as a stop, can be varied along the direction of adjustment S at least in one region. It is thus an adjustment device (adjustable stop 41) provided in an advantageous embodiment, by means of which the position of a pressure near the end position of the bearing block 34 is adjustable. For Wegbegrenzung / adjustment serves z. B. a wedge drive described below.
  • the placement of the stop 41 can in principle be done manually or via a 46 designed as an actuator 46.
  • a holding or clamping means (not shown in FIGS. 6 and 7) is provided by means of which the stop 41 can be fixed in the desired position.
  • at least one resilient element 42 for. B. spring element 42, is provided, which applies a force F R from the stop 41 in a direction away from the bearing block 34.
  • the spring element 42 causes a pressure-off in the event that the bearing block 34 is not prevented from moving in any other way.
  • Pressure is applied by moving the bearing block 34 in the direction of the stop 41 by at least one actuator 43, in particular a force-controlled actuator 43, by means of which for employment either a defined or definable force F in pressure-on direction on the bearing block 34th can be brought. If this force F is greater than the restoring force F R of the spring elements 42, the cylinder 06 is set at a corresponding spatial configuration; 07 to the adjacent cylinder 06; 07 and / or a hire of the bearing block 34 to the stop 41st
  • the applied force F, the restoring force F R and the position of the stop 41 is selected such that between abutment 41 and the stop surface of the bearing block 34 in Anstelllage no significant force .DELTA.F is transmitted for example,
  • the contact force between the cylinders 06; 07 substantially determined by the voltage applied by the actuator 43 force F.
  • the decisive for the color transfer and thus the print quality, among other decisive line force in the Nippstellen is therefore not primarily by a travel, but at quasi-free stop 41 by the force F and the resulting balance defined. In principle, after finding the basic setting with the appropriate forces F, it would be conceivable to remove the stop 41 or a corresponding fixation which is effective only during the basic setting.
  • the actuator 43 can be embodied as any desired actuator 43 applying a defined force F.
  • the actuator 43 is designed as actuatable by pressure means actuating means 43, in particular as a movable piston 43 by a fluid.
  • the arrangement of a plurality of, in this case two, such actuators 43 is advantageous with regard to possible tilting.
  • the actuator or actuators 43 can either be integrated in the side supports 63 or the carriages 34, or they can, as shown, be mounted in a separate component, eg. B. an actuator element 59, and be inserted into the storage unit 14.
  • As fluid preferably comes because of their incompressibility a liquid, for. As oil or water, used.
  • the actuator 43 as a piezo (piezoelectric force application) or as a magnet (magnetic force application), in particular electromagnet, be formed.
  • a controllable valve 56 is provided either inside or outside of the bearing unit 14. This is performed, for example, electronically controlled and provides the hydraulic piston 43 in a position without pressure or at least to a lower pressure level, while in another position of the force F conditional pressure P is applied.
  • a non-designated leakage line is provided here for safety.
  • 34 can be used as an overload protection 49, z. B.
  • spring element 49 may be provided, which in the operational pressure-Ab, ie the piston 43 are relieved and / or retracted, although serve as a stop 49 for the bearing block 34 in pressure-off position, in the case of a railway winder or other excessive forces but gives way from the point of pressure 05 and releases a larger path.
  • a spring force of this overload protection 49 is therefore chosen to be greater than the sum of the forces from the spring elements 42.
  • the stop 41 in the illustrated embodiment is designed as a wedge 41 movable transversely to the direction of adjustment S, the position of the respectively effective stop face 44 varying along the direction of adjustment S when the latter is moved.
  • the wedge 41 is supported for example on a carrier-fixed stop 58.
  • the carrier-fixed stop 58 is here z. B. formed by a side support 61 of the bearing unit 14.
  • a wedge 41 stop 41 is by an actuator 46, for example, a pressure medium actuatable actuating means 46 such as a pressure medium-actuated piston 46 in a working cylinder with (double-acting) piston via a z. B. designed as a piston rod 47 transfer member 47 or by an electric motor via a designed as a threaded spindle transfer member 47, movable.
  • This actuator 46 can either be effective in both directions or, as shown here, be designed as a one-way actuator, which operates against a return spring 48 when activated.
  • the force of the return spring 48 is made of o. G. Reasons (largely force-free stop 41) chosen so weak that the wedge 41 is held only against gravity or vibration forces in its correct position.
  • the stop 41 can also be of another type (for example, as the direction of adjustment adjustable and fixable plunger, etc.) be executed in such a way that it forms a variable in the adjustment direction S, and - at least during the adjustment process - fixable stop surface 44 for the movement of the bearing block 34 in the direction of pressure point 05.
  • a location of the stop 41 is carried out, for example, directly parallel to the direction of adjustment S by a drive means, for example, a pressure medium actuated cylinder with (double-acting) piston or an electric motor.
  • Fig. 2 is executed as a double printing unit 03 printing unit 03 schematically per cylinder 06; 07 a arranged on the side frame 1 1 bearing unit 14 indicated.
  • the centers of rotation of the cylinder 06; 07 is an imaginary connecting line or plane E (hereinafter referred to as "linear double printing unit").
  • the plane E and the incoming or outgoing web 02 close a 90 ° deviating inner angle between 75 and 88 °, in particular from 80 to
  • the bearing unit 14 of the transfer cylinder 06, in particular of all cylinders 06, 07, are arranged in the mounted state in the embodiment shown in Fig.
  • a maximum angle of 15 ° includes, for example, an acute angle of about 2 ° to 15 °, in particular form 4 to 10 ° with each other.
  • this arrangement when the adjustment direction S is horizontal and the web 02 is substantially vertical.
  • Figure 1 of an angular (n- or u-printing) arranged double printing 03 should under the plane E ', the connection plane of the pressure point 05 forming cylinder 06 and the plane E between the forming and transfer cylinders 07; 06 are understood, and the above to the angle to the direction of adjustment S at least one of the pressure point 05 forming cylinders 06 and the forme cylinder 07 and the plane E 'and E "are related.
  • One of the pressure point 05 forming cylinder 06 can also be stationary and operationally not adjustable (but possibly adjustable) in the side frame 11; 12 may be arranged, while the other along the adjustment direction S, is movably mounted.
  • An on / off-setting operational travel along the direction of adjustment S between pressure-off and pressure-on position is z. B. in the transfer cylinder 06 at 0.5 to 3 mm, in particular at 0.5 to 1, 5 mm, and the forme cylinder 07 at 1 to 5 mm, in particular at 1 to 3 mm.
  • the bearing units 14 of the transfer cylinder 06 in particular all cylinder 06; 07, arranged in the mounted state on the side frame 11 such that their adjusting directions S coincide with the connecting plane E. All adjustment directions S of the printing unit 04 coincide with it and are not spaced from each other.
  • the actuator 43 can also be integrated on the position block 34 and repel on the side plate 63.
  • at least one further actuator which acts away from the pressure point 05 when activated, may additionally be provided. This can replace or support the spring element 42.
  • Fig. 9 shows an embodiment for the coupling of an axial drive for side register setting, z. B. on the drive side opposite side of Cylinder 06;
  • the pin 21 is preferably provided with a device for axially moving the cylinder 07, ie with a side register drive 66, z. B. a drive motor 66, coupled (Fig. 37).
  • the example connected in the manner of Fig. 9 with the pin 21 shaft 39 is connected via a bearing 67, z. B. thrust bearing 67 with an axial drive 68, 69, 72, 73 connected.
  • the axial drive 68, 69, 72, 73 comprises a spindle 68, in particular with at least one threaded portion 71, a non-rotatably connected to the spindle 68 spur gear 69, a pinion 72 and a pinion 72 driving motor 73.
  • the threaded portion 71 acts with a bearing block fixed Internal thread 74, z.
  • the thrust bearing 67 allows relative rotation between shaft 39 and spindle 68, however, is formed with respect to an axial direction of the cylinder 07 pressure and zugsteif.
  • a first embodiment for the drive coupling takes place, as shown in Fig. 6 i.V.m. Fig. 10 and 1 1 shown, the coupling of the cylinder 06; 07 and the pin 21; 22 on a drive side of the printing unit 01 to a drive, for. B. directly to a rotor of a drive motor 81 and / or a drive train, via at least one angular and / or offset-compensating coupling 82.
  • the drive motor 81 in particular its rotor, can then be arranged fixed to the frame and the arrival / Abstellieri of the cylinder 06 ; 07 do not follow.
  • the drive motor 81 to be coupled in this first embodiment for the drive of the cylinder 06; 07 (or rotating component) as a synchronous motor 81 and / or permanent magnet excited electric motor 81, in particular as a permanent magnet synchronous motor 81 is formed.
  • This drive motor 81 is a directly driven round motor and has a stator with three-phase winding and a rotor with permanent magnets.
  • This design of the drive motor 81, in particular the permanent magnets a high power density is achieved and therefore makes the use of gear ratios unnecessary. This eliminates imprecision in the drive train and wear of mechanical elements such as gearbox.
  • the coupling of the rotary drive to the rotating component, here the cylinder 06, 07; takes place as shown in Figure 6 by way of example for the first embodiment shown on the shaft 39, which at its end near the cylinder end of the pin 21; 22 includes and for example via a clamping device 24 with the pin 21; 22 is torsionally rigid connected.
  • the clamping device 24 is here for example as z. T. slotted hollow shaft end formed, which comprises the journal end (pin 21, 22) and is to be pulled together by means of a screw in such a way that a frictional rotationally fixed connection between the journal end (pin 21, 22) and Hollow shaft inner surface can be produced.
  • the coupling can also in other ways, for. B. in the circumferential direction having a positive connection, be executed.
  • the shaft 39 is through a recess in the side frame 11; 12 out, which is sufficiently large for the movement of the shaft 39 is dimensioned together with the bearing block 34 and which z. B. is formed in the manner of a slot.
  • a cover 28 may be provided with a slot overlapping the collar, which z. B. with the bearing block 34, but not connected to the shaft 39.
  • Fig. 10 is a schematically designed as a permanent magnet drive motor 81, in particular synchronous motor 81 formed drive motor 81, whose rotor 84 z. B. via a rotor 84 rotatably supporting motor shaft 85 and another, rotationally fixed coupling 83, z. B. a dog clutch 83 is coupled to the shaft 39.
  • the stator 86 of the drive motor 81 is fixed to the frame via a holder 87 with the side frame 11; 12 connected.
  • the rotor 84 is mounted in the stator 86 via bearings 88, in particular radial bearings 88 and optionally additionally secured against axial movement.
  • the axial movement in the case of the cylinder 07 designed as a forme cylinder 07 is received by the clutches 82.
  • the rotor 84 or rotor of the synchronous motor 81 has poles of permanent magnets 89 on its circumference (in particular circumferentially alternating).
  • the stator 86 has windings 91 opposite to the permanent magnets 89 for generating magnetic fields by electric energy.
  • the drive motor (for example drive motor 81) designed as a permanent-magnet-excited synchronous motor 81 is, for example, B. formed as field weakenable synchronous motor.
  • the field weakening of the synchronous motor is provided, for example, up to a ratio of 1:10.
  • He has at least six pairs of poles, preferably at least 12 pole pairs.
  • the permanent magnets 89 preferably comprise rare earth materials. Particularly advantageous is the formation of the permanent magnet 89 with neodymium-iron-boron.
  • the drive motor embodied as a permanent-magnet-excited synchronous motor 81 has z. B. a steady state torque in the range of 50 Nm to 200 Nm, in particular for the drive of printing cylinders 06; 07 from 50 to 150 Nm or for reel changer or folder drive from 100 to 200 Nm.
  • the drive motor (eg drive motor 81) embodied as a permanent magnet-excited synchronous motor 81 has a maximum torque in the range of 200 to 800 Nm, 200 to 400 Nm for the drive of printing unit cylinders 06; 07 or for Rollenwechsler- or folder drive from 600 to 800 Nm.
  • the drive motor (for example drive motor 81) designed as a synchronous motor 81 and / or permanently excited motor 81 has, for example, B. a theoretical idling speed in the range of 500 U / min to 600 U / min.
  • the drive motor designed as a synchronous motor 81 and / or a permanently excited motor (eg drive motor 81) is, for. B. upstream a frequency converter for speed control.
  • the stator 86 is advantageously designed with a three-phase three-phase winding, whereby sinusoidal commutation of the current takes place.
  • the drive motor (eg drive motor 81) designed as a synchronous motor 81 and / or a permanently excited motor is a sensor 106 mentioned below, z. B. rotation angle sensor 106 is provided.
  • An axis of rotation of the rotation angle sensor 106 can advantageously be arranged coaxially with the axis of rotation of the rotor 84 of the motor (eg drive motor 81).
  • a cooling device in particular a fan wheel or a liquid coolant circuit, is provided on the drive motor (eg drive motor 81) designed as a synchronous motor 81 and / or a permanently excited motor.
  • a braking device may be provided on the motor (for example drive motor 81) designed as a synchronous motor 81 and / or a permanently excited motor.
  • the engine can also be used in generator mode as a braking device.
  • fitting mechanisms for positionally correct fixing between stator 86 and rotor 84 may be provided.
  • the one mentioned for the formation of the permanently excited synchronous motor 81 may be partially or totally connected to corresponding drive motors (138; 139; 140; 141; 142; 143; 152; 162; 163 s.u.) of other printing cylinder 06; 07 different rotating components (133; 135; 136; 144; 145; 146; 147; 148; 153; 164 s.u.).
  • the impression cylinders 06; 07 in an advantageous embodiment in each case individually driven by a drive motor 81.
  • the necessary offset when turning on / off the nipples is made possible by the clutches 82 here.
  • FIG. 11 shows the drive of the printing unit 04 on the left side for the ratios of the dry offset (without dampening unit), on the right side for the wet offset (with dampening unit).
  • the two printing units 04 of a real double printing unit 03 are of the same type.
  • the roller diagram was omitted in the front view and only the drive trains with motors were shown.
  • the drive concept is the example of an inking unit 08 with two rotatably driven changeable rollers 92, z. B. Reibzylindern 92, and - in the case of wet offset - exemplified a dampening 09 with a rotationally driven, not shown, rubbing cylinder set forth.
  • the inking unit 08 each has its own, from the printing cylinder 06; 07 mechanically independent drive motor 93 for the rotary drive on.
  • gear 94 rotationally.
  • Per distribution cylinder 92 of the inking unit 08 and each friction cylinder of the dampening 09 can be arranged a the axial traversing friction generating gear. However, this can in principle be driven by an additional drive motor, or, as illustrated, be designed as a transmission that converts the rotational movement into an axial movement.
  • the bearings are in an advantageous embodiment, the bearing units 14 in the above-mentioned embodiment for the storage of the four cylinders 06; 07 indicated.
  • the shafts 39 are, for example, by corresponding recesses / openings in the side frame 11; 12 led.
  • the coupling between frame-fixed drive motor 81 and forme cylinder 07 is preferably such as to enable side register control executed that it also receives an axial relative movement between the form cylinder 07 and drive motor 81. This can also be done by the above-mentioned multi-plate clutch 82, which allows an axial length change by deformation in the region of the slats.
  • An illustrated in the manner of FIG. 9 or otherwise executed axial drive may be provided on the other frame side as the rotary drive.
  • the driven distribution cylinders 92 of the inking unit 09 can be coupled to the drive motor 93 via at least one angular deviation compensating coupling.
  • the drive motors 93 in the inking unit 08 and / or dampening unit 09 may be formed in the manner of the above-described permanent-magnet-excited drive motors 93, in particular synchronous motor 93. Dimensioning and design may, however, be too o. G. differ.
  • the coupling between the rotational body is effected. B. cylinder 06; 07, and drive motor 81 directly - d. H. without an axial relative movement enabling clutch and / or without an angle and / or offset compensating coupling - to the shaft 39.
  • This coupling can be rigid, but detachable.
  • the drive motor 81 z. B. not fixed to the frame, but arranged cylinder-tight and is when you turn on / off - and possibly in veryregisterverschiebung - with the cylinder 06; 07 moved.
  • Fig. 12 shows an embodiment of the drive of a rotating component, in particular of the bearing on the bearing unit 14 cylinder 06; 07 with a designed as a synchronous motor 81 and / or permanent-magnet motor drive motor 81, ie with a Section of permanent magnets 89 formed on the rotor 84.
  • the stator 86 is in this case, for example, directly or indirectly on the movable part of the storage unit 14, z. B. rigidly attached to the movable bearing block 34 and movable together with this.
  • the stator 86 is mounted, for example, on the inner eccentric bush or the lever.
  • the parts relating to the bearing unit 14 are not again provided with reference numerals in FIG. 12 and can be taken from FIG.
  • the stator 91 having the windings 91 is detachably connected to a holding means 98, for. B. a socket
  • the motor shaft 85 of the drive motor 81 supporting the permanent magnets 89 and the rotor 84 is formed by the shaft 39 and vice versa, the shaft 39 through the motor shaft 85.
  • Motor shaft 85 and rotor 84 may also be integrally formed, so that in this Case, the motor shaft 85 carries the permanent magnet 89 at its periphery.
  • motor shaft 85 and rotor 84 are formed as two components and z. B. by a clamping element 101 or clamping set 101 rotatably connected to each other.
  • the rotationally fixed connection between the shaft 39 and motor shaft 85 and pin 21; 22 is here by a frictional connection, z. B. by a clamping element 102 and clamping set 102, manufactured.
  • rotor 84 and cylinder 06; 07 rigidly and non-rotatably connected to each other in the axial and radial directions.
  • connection can be made detachable at different locations.
  • the rotor 84 thus moves with when the cylinder 06; 07, in particular the forme cylinder 07, is moved axially or radially.
  • the stator 86 is with respect to a movement perpendicular to the cylinder longitudinal axis arranged cylinder-fixed and moves with arrival / Abstellierien.
  • no radial bearings 88 are preferably arranged between the stator 86 and the rotor 84 for mutual support.
  • a guide 103 may be provided, on which the motor slides.
  • the guide 103 is adapted to the curve shape of the adjustment path of the bearing assembly 14 ("similarity") and is here designed as a linear guide 103.
  • the degree of freedom of the linear guide 103 must be only a few millimeters 29, sufficiently stiff and resilient designed to both the torque between the stator 86 and rotor 84 and the tilting moment by the weight of the stator 86 (with bushing 98, etc.) to record.
  • the drive motor 81 in particular as a drive for rotating components with requirement for registration in the circumferential direction as it Druckwerkszylinder 06; 07 or cylinder of a folder (see below), the drive motor 81 is formed as an angular position-controlled drive motor 81.
  • angular position control is a with the component (cylinder 06; 07) or the drive motor 81 rotatably connected sensor 106, z. B. an angular position detecting sensor 106, in particular an angular position sensor 106, required via which the control loop, the actual angular position is confirmed.
  • the sensor 106 may also be designed only as the speed detecting sensor 106, in particular as a speed sensor.
  • the sensor 106 can basically arbitrarily on one with the cylinder 06; 07 rotatably connected component, z. B. also on the drive motor 81 opposite pin 21; 22, be arranged.
  • the sensor 106 in particular its rotor, is arranged coaxially to the axis of rotation at the cylinder-distal end of the motor shaft 85.
  • the stator of the sensor 106 is secured against rotation via an anti-rotation device 107 on the stator 86 of the drive motor 81.
  • the anti-rotation device 107 has a degree of freedom in the radial direction, so that the stator of the sensor 106 can follow a possibly present non-circular running of the motor shaft 85 and thus of the sensor rotor.
  • the attachment of the anti-rotation device 107 takes place for this purpose, for example via a radially extending slot in which a pin engages.
  • the anti-rotation device 107 is designed as a long lever with respect to the radial direction.
  • the length L107 from the sensor stator to the fixed point of the rotation 107 corresponds to z.
  • the drive motor 81 (also in application to printing cylinders 06, 07 different rotating components of the printing press) on a cooling.
  • the cooling is done by a fan.
  • a liquid coolant circuit is provided in which tempered coolant, for.
  • 81 is feasible by the drive motor.
  • connecting bores 108 are provided in the housing of the stator 86, through which the coolant can be guided in coolant channels 109 between the housing and a carrier carrying the windings 91.
  • the drive motor 81 and its connection and periphery are designed both for the cylinder 06, which is in the form of a cylinder 06 and the cylinder 06; 07 predictable.
  • the cylinder 06; 07, in particular cylinder 07 this, however, holding and / or solvent for attachment of elevators, z. B. printing forms (especially ends of finite pressure plates), which are actuated by pressure medium executes.
  • the holding and / or solvent are self-locking, so that a holding without activation of pressure medium and an opening or releasing takes place by applying pressure medium.
  • the cylinder 07 has z. B. in the axial direction more, z. B. four or even six independently operable holding and / or solvent for attachment or to solve as many juxtaposed printing forms, z. B. printing plates, on.
  • z. B. printing plates In the case of finite pressure plates, the ends of the pressure plates stuck in slots on the cylinder surface and are held by the pressure medium-actuated retaining means, preferably self-locking.
  • z. B. printing sleeves, z. B. provided on the cylinder jacket outlet openings for the pressure medium wherein the cylinder 07 encompassing printing forms z. B. be solved by applying pressure medium.
  • the cylinder 07 can in the circumferential direction one behind the other several, z. B. two independently operable holding and / or solvent for attachment or release as many circumferentially successively arranged printing plates, z. B. printing plates have. Overall, then z. B. two groups of four or six printing plates on the cylinder 07 to be arranged. However, the change of printing plates is done in groups, so that in a certain cylinder position at most the holding means of a group of printing plates, for. four or six, must be operable.
  • the drive train on a rotary transformer through which a plurality of supply channels in the cylinder 07 are independently acted upon optionally with pressure medium.
  • the rotary feedthrough is formed with an interface between the rotating and non-rotatable component, on which runs the pressure medium flow to be transmitted in the axial direction.
  • the openings 1 18 are connected to the individual holding means leading lines 117 (dashed lines) in combination.
  • the number of spatially on the rotor 11 1 separated openings 118 corresponds at least to the number of total independently operable holding means.
  • the rotor 1 11 acts on an axially directed, frontal contact surface with an opposing axially directed frontal contact surface of a rotationally fixed stator 112 (FIG. 14) together, which in its frontal contact surface outlet openings 1 19 in such a way that they depending on the relative angular position between stator 112 and rotor 11 1 optionally in registration with an inlet opening of a breakthrough 118 or depending on the position optionally in registration with inlet openings of different apertures 119 can be brought.
  • the number of outlet openings 119 corresponds at least to the number of holding means or printing plates of a group of juxtaposed printing plates, here z. Four.
  • stator 112 and rotor 11 are movable relative to one another and can be pressed against each other.
  • stator 1 12 mounted axially movable on the shaft 39 and an annular punch 1 16 to the rotor 11 1 pressed.
  • the pressing is done z. B. by applying an annular space with a pressure medium, which by a corresponding terminal 114 can be acted upon.
  • cylinder 06; 07, z. B. as a transfer cylinder 06 without the requirement of a pressure medium supply can account for the rotary transformer with the components described and possibly the drive motor 81 closer to the cylinder 06; 07 are built.
  • the stator 86 is not rigidly connected to the bearing block 34, but is supported on the motor shaft 85 via radial bearings 88 (comparable to FIG. 10).
  • radial bearings 88 (comparable to FIG. 10).
  • This can in the axial direction of the cylinder 06; 07 be stiff when the radial bearings 88 between rotor 84 and motor shaft 85 and stator 86 allow axial relative movement.
  • the rotor 84 moves in the frame-fixed stator 86 axially when the cylinder 06; 07 is moved axially.
  • the device for preventing rotation 103, 104 must also have a degree of freedom in the axial direction of cylinder 06; 07 be executed enabling.
  • the rotor 84 moves together with the stator 86 axially when the cylinder 06; 07 is moved axially. Since it is only a few millimeters, this can be done in a simple embodiment, for example, by a long lever arm, ie. With respect to the distance to the guide 103 long support 104, wherein the small axial movement is absorbed by deformation of the support 104.
  • either the guide 103 or the connection of the support 104 to the stator 86, a further linear guide, but with a degree of freedom in the axial direction of the cylinder 06; 07 have.
  • This can be done for example by bolts, z. B. on the side frame 1 1; 12, on the movable part of the guide 103 or on the stator 86, and a corresponding bore or eyelet on the corresponding component, for. B. the frame-fixed part of the guide 103, the support 104 in the region of the guide 103 or the support 104 in the region of the stator 86 take place.
  • a part 181 of the stator 86 carrying the windings 91 was rigid in the axial and radial directions and non-rotatable, but detachable - e.g. B. on the illustrated, but not in Fig. 12 not designated screw - connected to the movable part of the bearing assembly 14 and, for example, with a housing 182 of the drive motor 81.
  • This rigid connection 184 (shown in FIG. 12 as a whole with a dashed arrow) represents there a connection which is in particular rigid with respect to an axial direction and can also be rigid in the radial direction with respect to the side frame 11 for non-movable cylinders. 12 be formed.
  • a permanent magnet 89 carrying part 183 of the rotor 84 was there with respect to.
  • An axial relative movement rigid with the cylinder 06; 07 connected so that with an axial movement of the cylinder 06; 07 - z. B. to adjust the page register - inevitably an axial relative movement between windings 91 and permanent magnets 89 could occur.
  • FIGS. 15 to 18 particularly advantageous embodiment variants of the drive motor 81 are set forth, which ensure an optimum operating point between the stator 86 and the rotor 84 relative to each other with regard to an axial positioning.
  • FIGS. 15 to 18 are simplified in comparison to FIG. 12 and may additionally also have a rotary transformer described above and / or a support and / or anti-twist device for the drive motor 81 described above.
  • the stator 86 although rotatably, but not in the axial direction of stock or storage, but (at least in a certain order of magnitude for the pages register) arranged axially movable. Relative to the side frame 11; 12 and / or one for arrival / Abstallens movable Part of a bearing assembly 14, however, it is formed against rotation with respect to occurring torques.
  • a coupling between the stator 86 and the rotor 84 with respect to the axial movement takes place here not mechanically, but for example via magnetic forces.
  • an axially together with the cylinder 06; 07 movable rotor moves axially, it is at least partially carried along on the magnetic interaction of the stator.
  • this can be axially carried along in such a way that the magnets of the stator and the rotor can remain at the optimum operating point relative to one another, that is to say that the stator can remain stationary relative to the rotor in an extreme case.
  • stator 86 with respect to the side frame 1 1; 12 and / or bearing assembly 14 together with a rotationally fixed connection with the side frame 1 1; 12 and / or the bearing assembly 14 on the other hand (anti-rotation) can be realized in many different ways. Without limiting the generalization, three first advantageous embodiments are set forth in FIGS. 15, 16 and 17. Here there is between stator windings and side frame 1 1; 12 and / or bearing assembly 14 or holding means 98) in the axial direction not rigid, but within certain limits (eg, an axial relative movement in the range of at least 1 mm, ie at least ⁇ 0.5 mm from a central position considered) in the axial direction "Soft" connection.
  • FIG. 15 there is no rigid connection (184) between the stator 86 (or the part carrying the windings 91) and the housing 182.
  • the part of the stator 181 carrying the windings 91 is axial in the housing 182 movably mounted.
  • housing 182 and the windings 91 supporting part of the stator 181 z. B. formed with co-operating sliding surfaces 186.
  • the guarantee of the radial relative position to be maintained while at the same time enabling an axial relative movement can in principle also take place in a different way than with a sliding surface 186 having sliding guide.
  • the housing 182 (as in Fig.
  • stator 86 and its part 181 rotatably with the bearing assembly and the side frame 11; 12 connected.
  • This is done, for example, via one or more with respect to a direction of rotation form-locking anti-rotation 187 (eg, clutch 187) between the stator 86 and its part 181 and a stock or fixed bearing part as it is z.
  • B. represents the housing 182.
  • the rotationally fixed connection by one or more arranged on the stator 86 stops 188, z. B.
  • the sensor 106 may be either as shown in Fig. 12 or as shown in Fig. 15 via a holding means 191, z.
  • a holding means 191, z As a holder or so-called. Can be connected to the housing 182. 16, the sensor 106 is connected via the holding means 191 substantially rigidly connected to the housing 181, an axial relative movement between the shaft 39; 85 and the rotor of the sensor via a non-rotatable or torsionally stiff, but an axial relative movement receiving coupling 192, z.
  • a jaw clutch but preferably via a so-called. Lamellar or all-metal coupling.
  • the housing 182 is not connected to the bearing arrangement 14 or the side frame in a pressure / tension-stable manner, but is itself axially movable, but guided in a rotationally fixed manner.
  • the windings 91 supporting part 181 of the stator is connected to the housing 182 z. B. rigidly connected so that housing 182 and the stator 86 and the part 181 move together axially.
  • the housing is opposite the bearing assembly 14 and the side frame 11; 12 rotatably, but axially (at least within certain limits) arranged to be movable. This is done, for. B. again via a form-locking anti-rotation 187.
  • the guide 194 may be formed as a bore in a fixed to the housing 182 strap 196. This can also be carried out in the reverse manner.
  • the tab may be formed as a collar-shaped circular ring in which a plurality of these guides 194 (or vice versa bolts) may be arranged.
  • a seal 197 or other type of cover Between the axially relative to each other movable parts, here the housing 182 and the tab 196 and the holding means 98 may advantageously be arranged a seal 197 or other type of cover.
  • the rotationally positive locking anti-rotation 187 within its axial range of motion no positive connection in the axial direction, but z. B. only one end stop (see, for example, thickening
  • the anti-rotation 187 as based on deformation of individual disks 201 and disk packs coupling 187, z. B. formed in the manner of a lamella or all-metal coupling.
  • the windings 91 supporting part 181 of the stator or the housing 182 is connected via a group of at least two circumferentially spaced spring elements 202 with the holding means 98 and the bearing block 34.
  • the spring elements 202 each have at least two lamellae 201 or disk packs connected to one end, eg via a spacer 203, whose other ends are connected to the part 181 of the stator or the housing 182 carrying the windings 91 on the one hand and to the holding means 98 or are connected to the bearing block 34 on the other.
  • the housing 182 or the stator 1 12 can now be moved axially relative to the holding means 98 or the bearing block, the relative movement being absorbed by the deformation of the spring elements 202.
  • the group of spring elements has at least two of these spring elements 202, which are preferably offset by 150 ° to 210 ° in the circumferential direction to each other. As a result, a radial displacement is prevented during axial movement.
  • Embodiment is - as shown in Fig. 17 - a second, arranged in the axial direction to the first spaced group of spring elements 202, wherein again one end of the spring element 202 is "stator fixed" and the other "bearing block fixed” is arranged. As a result, tilting of the stator 1 12 or of the stator 1 12 having the housing 182 is prevented.
  • the windings 91 are therefore non-rotatable with the bearing block 34, but in the axial direction of the associated cylinder 06; 07 is movably connected (within certain limits (eg at least 1 mm, in particular at least 2 mm) relative to the positional block 34.
  • the rotation relative to an axial relative movement 187 between the winding 91 carrying part 181 of the stator and the bearing block 34 provides a rotatable, but an axial relative movement receiving coupling 187, which with corresponding stops (eg., With guided stops of Fig. 15 and 16) or as shown in Fig. 17 via a non-rotatable or torsionally stiff, but an axial relative movement receiving so-called .
  • Lamella or all-metal coupling 187 with corresponding spring assemblies may be formed.
  • the stator 86 may be arranged in the axial direction stagnant or fixed in storage, wherein the magnet supporting part 183 of the rotor 84, z. B. rotor body, at least in a certain order relative to a cylinder-fixed shaft, ie in the result relative to the cylinder 06; 07, is axially movable (Fig. 18).
  • the part carrying the magnets 183 of the rotor 84 is with respect to torque to be transmitted to the cylinder 06; 07 or the shaft 39; 85 rotationally fixed, z. B. via an anti-rotation device 199, is formed.
  • the magnet-carrying part 183 of the rotor 84 and the shaft 39; 85 can z. B. be moved over sliding surfaces or similar acting means in the axial direction relative to each other.
  • the axial relative movement enabling rotation 199 between shaft 39; 85 and rotor body 183 can either over corresponding stops (eg in the tongue and groove principle or with comparable to Fig. 15 and 16 attacks) or as shown by a non-rotatable or torsionally stiff, but an axial relative movement receiving coupling 199, z.
  • a jaw clutch but preferably via a so-called. Lamella or all-metal clutch coupling, be formed.
  • FIGS 15 to 18 and its principle is applicable to subsequent embodiments of the drive motor 81 (or other drive motors (see below 139; 140; 141; 142; 143; 162; 163).)
  • the drive motor 81 in this case is preferably designed as a permanent magnet synchronous motor, it may also have 91 corresponding windings for the electrical formation of the magnetic fields instead of the permanent magnet.
  • the rotor 84 is now z. B. with the jacket body of the cylinder 06; 07 connected or formed by this.
  • the windings 91 of the stator 86 are supplied with energy, for example, by electrical leads 121.
  • the sensor 106 can in principle at different points rotationally fixed to the cylinder 06; 07 and / or the rotor 84 may be connected, for. B. also on the other end face of the cylinder 06; 07, and has z. B.
  • a signal line 121 for drive control In the example it is connected to the rotor 84. Stator 86 and rotor 84 are supported by bearings 88, here radial bearings 88, each other. For this purpose, the radial bearings 31 omitted in the bearing block 34 of FIG. 6 and 7.
  • the stator 86 is rotatably connected to the Bearing block 34 connected and together with this, in particular linear, movable. In the case of non-moving rotating components, such. B. cylinder of a folder or draw rollers, the principle can be transmitted without the use of the storage unit 14.
  • FIG. 20 shows an advantageous variant, whereby, in particular in the case of a cylinder 07 designed as a forme cylinder 07, an axial movement by the drive motor 81 should also take place.
  • the rotor 84 has a section covered in a different way with permanent magnets 123.
  • the poles of the permanent magnets 123 alternate here, for example, in the axial direction.
  • z. B the poles in the provided for the rotary drive portion of permanent magnets 89 z. B. in the circumferential direction (also in Fig. 10, 12 and 15).
  • the section of permanent magnets 123 provided for the axial movement are arranged opposite to the windings 91 different windings 126, which are controllable via their own signal lines 124 from a machine controller for the purpose of side register adjustment.
  • the bearings 88 are formed here, for example, as an axial relative movement enabling roller bearing 88.
  • a first possible solution is, as shown schematically in Fig. 21, the adjacent drive motors 81, z. B. in the embodiment of FIG. 10 or 12, but axially to each other so that they are not perpendicular to the direction of rotation overlap lying plane.
  • the shafts 39 can be made longer or intermediate shafts can be provided.
  • the stator 86 may be segmented, i. H. be formed of one or more segments, which does not surround the full circle circumference or which in several segments in total do not enclose the entire circumference.
  • One or more stator segments 86 'thus only enclose a circumferential angle which is smaller than 360 °, z. B. less than 300 °, in particular less than 240 °, is. If two segments are provided, they may be distributed as desired around the circumference of the circumference and each enclosing a circumferential angle smaller than 150 °, in particular smaller than 120 °.
  • stator 86 formed from the at least one stator segment 86 'or the stator segments 86', or the assembly with windings 91, does not extend completely but only partially around the circumference. In an advantageous embodiment, however, in the case of two stator segments 86 ', these are located opposite each other, ie. H. uniformly distributed in the circumferential direction, arranged.
  • FIG. 22 A first of several subsequent embodiments of this third embodiment for the formation of the drive is shown in FIG. 22 in detail.
  • an active surface between the stator 86 and rotor 84, or an active surface between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86 extends parallel and z. B. coaxial with the axis of rotation of the cylinder 06; 07 or rotating component.
  • the cylinder 06; 07 has z. B. in the region of its lateral surface or a frontal mounting the permanent magnets 89 in the circumferential direction.
  • the windings 91 having stator 86 is fixed to the frame outside of the cylinder 06; 07 (or a roller), but between the two side frames 1 1; 12 arranged.
  • the stator 86 supporting the windings 91 only extends over an angular segment (see FIGS. 23 to 26). But the permanent magnets 89 can also on a pin 21; 22 or a frontal taper of the cylinder 06; 07 or the component can be arranged. Since the Stator 86 is arranged here on the side frame 12 (11) is in the case of an optionally movable cylinder 06; 07 to take into account the shape of the stator 86 and / or its distance from the rotor 84 (see, for example, Fig. 28).
  • stator 86 and rotor 84 there are arrangements of stator 86 and rotor 84, wherein an effective area between stator 86 and rotor 84, or an effective area between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86 in parallel and z.
  • 25 and 26 are arrangements of stator 86 and rotor 84, wherein an effective area between stator 86 and rotor 84, or an effective area between the permanent magnet 89 of the rotor 84 and the windings 91 of the stator 86 perpendicular to the axis of rotation the cylinder 06; 07 or rotating component is located (in short: achsvertikale arrangement).
  • FIG. 23 and 25 are variants, wherein rotor 84 and stator 86 on the cylinder 06; 07 or rotating component facing side of the side frame 12; 1 1, and in Figures 24 and 26 to variants, wherein rotor 84 and stator 86 from the cylinder 06; 07 or rotating component facing away from the outside of the side frame 12; 11 lie.
  • Figures 23a, 23c and 25a represent variants taking into account a bearing assembly 14 for moving the cylinder 06; 07 and a movable component
  • the Fig. 23b, 23d, 24a, 24b, 25b, 26a and 26b illustrate the variants for a conventional side wall mounting of the rotating components.
  • bearing arrangements 14 On the figurative representation of Fig. 24a and 24b, taking into account bearing arrangements 14 has been omitted here.
  • Figures 23a, 23b and 24a illustrate drive motors 81 in the construction of an internal rotor motor, while Figures 23c, 23d and 24b illustrate external rotor motors.
  • stator 86 is in each case arranged on the movable part of the bearing arrangement 14, in particular on the bearing block 34.
  • the segmented design of the stators 86 offers a variety of possibilities for space-saving arrangement, of which in Fig. 27 with reference to a double printing unit 03 four variants are shown using the example of the axis-parallel arrangement. The teaching is correspondingly to differently executed o. G. Transfer variants. While in Fig. 27a, the drives of the cylinder 06; 07 each two segment-like stators 86, z. B. Statorsegmente 86 ', is assigned to each drive only a stator 86' in Figs. 27b to 27d.
  • stator segment 86 ' is designed so that a movement of the cylinder 06; 07 is ensured within limits (FIG. 28).
  • the radius of the effective stator is chosen so that the air gap in the end position of the cylinder 06; 07 is not closed. This is advantageous, for example, in arrangements according to FIGS. 23b, 23d, 24a and 24b, when the bearing between side frame 12; 11 and pin 22; 21 is designed as an eccentric.
  • the windings 91 can be connected either in parallel or in series and operated by a control unit 127.
  • a separate control of the windings 91 from different control devices 127 is conceivable (FIG. 29). It is only a sensor 106, z. B. angular position sensor 106, which supplies all the controllers 127 with the position signals of the actual position.
  • the position offset of the stator segments 86 'to each other can be parameterized accordingly in the control unit 127 or the control units 127.
  • a sufficiently accurate relative arrangement of the stator segments 86 'to each other in the circumferential direction is required so that the stator segments 86' do not operate against each other during operation.
  • stator segments 86 liquid-cooled.
  • the sensor 106 may be mounted on the rotor 84 itself, on the pin 21; 22 of the same cylinder side, or on the opposite pin 22; 21 be arranged.
  • the rotor 84 can be designed to be divisible into segments.
  • the rotor 84 is then z. B. in the circumferential direction of several (eg., Three, four six or eight) rotor segments 84 'together, which in sum cover the full circumference of 360 °, but are individually mountable / disassembled.
  • the cover is complete, ie it consists for. B. between the rotor segments 84 'no significant deviation from the spacing pattern of the alternating poles (permanent magnets or windings) or a distance between two rotor segments 84' in the circumferential direction is at most 5 °.
  • the drive motor 81 is designed in particular as a permanent magnet-excited synchronous motor 81.
  • the coupling mentioned in FIG. 12 is advantageous for a drive motor 81 embodied as a permanent-magnet-excited synchronous motor 81, but is also suitable for drive motors 81 of a different design, for example.
  • a linear drive for the axial adjustment is integrated in the drive motor 81 .
  • the components of the axial and the rotary drive can in principle be arranged one behind the other in the axial direction (as in FIG. 20). In an advantageous variant, however, these are arranged coaxially to each other and to the motor shaft or the shaft 39.
  • a sensor 106 detecting the rotational angle position, a sensor 128 detecting the axial position and a coolant channel 109 are provided.
  • the connection can either frame-fixed as shown in FIGS. 6 and 10 via couplings 82, or as indicated in an advantageous embodiment In principle, not shown variants are possible, wherein the externally arranged in Fig. 30 rotary drive inside, and the axial drive is arranged externally.
  • the permanent magnets 89; 123 and the windings 91; 126 each to swap.
  • the example of the printing cylinder 06; 07 described coupling of the drive motor 81 to the cylinder 06; 07 preferably has a releasable connection between pin 21; 22 and shaft 39 and motor shaft 85 in such a way, so that the pin 21; 22 in the assembled state of the cylinder 06; 07 the side frame 11; 12 does not penetrate.
  • the drive connection between the cylinder 06; 07 and the, in particular substantially coaxial with the axis of rotation of the cylinder 06; 07 arranged drive motor 81 is in this case a multi-part, d. H. by at least one pin 06; 07 and one rotatably but releasably connected with this shaft 39, which may also represent the motor shaft 85 at the same time.
  • the drive motor 93 may in principle be designed as an asynchronous motor or synchronous motor.
  • the drive motor 93 from FIG. 11 is designed as a synchronous motor 93, in particular as a permanent magnet synchronous motor 93.
  • the gear 94 in this case has z. B. no rotary reduction gear, but only one rotational movement in a traversing movement reshaping Gear, z. B. traversing on.
  • no own drive motors are then provided for the demonstration of the traversing movement.
  • two distribution cylinders 92 are provided in the inking unit 08, which are rotatable and iridescent, for example, via a mechanical drive connection both by the drive motor 93.
  • only the remotecylinder 92 disposed farther away from the forme cylinder 07 is rotationally driven.
  • the drive motor 93 of the inking unit drive designed as a permanent magnet synchronous motor 93, comparable to the drive motor 81 in FIG. 30, has a drive motor 93 in which both the rotary drive and the axial drive are integrated.
  • the drive motor 93 in which both the rotary drive and the axial drive are integrated.
  • a roll changer 131 a drive a material roll 144 driving motor 138 and / or a tension roller 145 of a retraction 132 a drive motor 139 and / or a pressure units 01 downstream draw roller 133 a drive motor 141 and / or a former 134 pull roller 136 a drive motor 142nd and / or a tension roller 135 downstream of a former 134, a drive motor 140 and / or at least one cylinder 146; 147; 148 of a folding apparatus 137 on a drive motor 143.
  • the material roll 144, the draw roll 145, the draw roll 133, the draw roll 135, the draw roll 136, the cylinder 146; 147; 148 are specially driven rotating components 144; 145; 133; 135; 136; 146; 147; 148 and can in the sense of the above iVm the printing cylinder 06; 07 can be driven by the drive motors 138, 139, 141, 140, 142, 143, in which case the drive motors 138; 139; 140; 141; 142; 143 in a related to the printing cylinder 06; 07 mentioned manner to the associated component 144; 145; 133; 135; 136; 146; 147; 148 may be coupled, but in each case the on / off enabling bearing assembly 14 may be omitted. Also u. U. the angular and / or offset compensating coupling 82 omitted.
  • the rotating member 144; 145; 133; 135; 136; 146; 147; 148 driving drive motor 138; 139; 141; 140; 142; 143 may in an advantageous embodiment as permanent magnet excited and / or as a synchronous motor 138; 139; 141; 140; 142; 143 trained drive motor 138; 139; 141; 140; 142; 143 be formed in the manner described above.
  • the provided in some versions axial drive can be omitted here. Differences may also arise in nominal and maximum torque.
  • drive motors 138; 139; 140; 141; 142; 143 in the manner of the drive motor 81 as a permanent magnet synchronous motor 138; 139; 140; 141; 142; 143 be formed.
  • Fig. 31 is schematically represented by one of the drive motors 81; 138; 139; 140; 141; 142; 143 connecting dash-dotted line indicated a drive control, which below to Fig. 37 is described in more detail.
  • FIG. 32 shows the front view of an exemplary embodiment of a roll changer 131 with the drive motor 138 designed as a synchronous motor 138, in particular with permanent magnet excitation 89 (see above), by means of which the most diaryachste roll of material 144 is driven and unwound.
  • At least one of two cones 149 is z. B driven by such, described above synchronous motor 138 with permanent magnets 89 on the rotor 84 and windings 91 on the stator 86.
  • the other cone 149 may be idle as shown or may also include such a drive motor 138.
  • the cone 149 is not formed Jerusalemsp Dretti here, but can also be designed to be spreadable.
  • FIG. 33 shows a folding former 151 having a plurality of folding hoppers 151 with traction rollers 153 driven by drive motors 152 as rotating components 153.
  • These drive motors 152 can also be designed as directly coupled synchronous motors, in particular permanent magnet excited as described above.
  • 153 also driven guide elements of a superstructure may have a drive motor in the manner of a synchronous motor as described above in one of the embodiments.
  • the drive motor 81 of the cylinder 06; 07 and / or the drive motor 93 of the inking unit 08 and / or the drive motor of the dampening unit 09 and / or the drive motor 143; 162 in the folding apparatus 137 and / or the drive motor 139; 140; 141; 142; 152; 163 of a draw roller 133; 135; 136; 145; 153; 164 (in the superstructure and / or in the folding structure 151 and / or at the entrance of the folding apparatus 137) and / or the drive motor 138 of the roll changer 131 may preferably be designed in the above-mentioned embodiment of the drive motor 81 as a synchronous motor 81 and / or as a drive motor 81 with permanent magnet excitation ,
  • the drive of the cylinder 06, 07 advantageous angular position control, and the drive of the draw rollers 133; 135; 136; 145; 153; 164 and the Reel changer 131 a speed control, possibly with superimposed
  • the folding apparatus 137 shown schematically in Fig. 34 has z. B. as Schneid representing. Knife cylinder 146, designed as a transport cylinder 147 and a jaw cylinder 148 cylinder 146; 147; 148 on.
  • the transfer of the folded product can then be given to a paddle wheel 154 and from there to a delivery 156.
  • At least the transport cylinder 147 designed as a folding blade cylinder 147 may be designed to be variable in format, ie. H. a distance .DELTA.U in the circumferential direction between holding means 157 and each subsequent folding blades 158 on the circumference of the transport cylinder 147 is made variable.
  • the strand 159 may consist of one or more longitudinally folded or unfolded webs 02 or partial webs.
  • Cutting, transport, jaw cylinders 146; 147; 148; and possibly paddle wheel 154 are preferably driven by at least one drive motor 143 (M), in particular at least one permanently excited (synchronous) motor 143, mechanically independent of printing units, superstructure and folding structure.
  • the drive can via a transmission, in particular a reduction gear, from the drive motor 143 to one or more of the cylinder 146; 147; 148 of the folder 137 done.
  • the drive motor 143 drives the cutting cylinder 146 (or one of a plurality of cutting cylinders) via an unillustrated transmission (eg, unspecified pinion or drive wheels). The latter is driven onto the transport cylinder 147 and from there to the jaw cylinder 148. From the jaw cylinder 148 may possibly be driven via a belt drive on the paddle wheel 154.
  • the display 156 preferably has its own, from the cylinders 146; 147; 148 and the paddle wheel 154 mechanically independent drive motor 162 (M).
  • Cutting, transport and jaw cylinders 146; 147; 148 and possibly paddle wheel 154 may also each mechanically independent of each other and from the printing units 04 by their own drive motors 143; 162 (M) (FIG. 35).
  • M drive motors 143; 162 (M)
  • FIG. 36 the three cylinders 146, 147, 148 together and paddle wheel 154 and display 156 are each driven individually.
  • cutting, transport and jaw cylinders 146; 147; 148 driven by at least one common or alternatively by each one of the printing units mechanically independent drive motor 143, while in a first variant paddle wheel 154 and delivery device 156 by a common drive motor mechanically independent of the cylinders 146; 147; 148 and the printing units 04 and in a second variant in each case by their own drive motors 143; 162 (M) are rotationally driven.
  • a possibly provided band system for guiding the product sections 161 in and through the folding apparatus 137 by its own drive motor 162 (M) mechanically independent of the cylinders 146; 147; 148 be driven.
  • the said drive motors 143; 162 (M) can, as shown above, advantageously as permanent magnet synchronous motors 143; 162 (M) may be formed.
  • inlet region of the folding apparatus 137 can also by a drive motor 163, z. B. permanentmagnet excited, driven tension roller 164 may be arranged as a rotating member 164.
  • the drive control described below is basically also independent of the specific above-described design of the drive motors 81; 138; 139; 140; 141; 142; 143; 162; 163 and special linear bearing of cylinders 06; 07 of advantage.
  • the drive control is particularly advantageous for the directly driven components in o. G. Versions.
  • FIG. 37 shows an example for the drive of a printing machine with a plurality of printing units 01, which are here by way of example two, in the form of printing towers 01, which in each case have a plurality of printing units 04, here double printing units 03.
  • the printing units 04 of a printing tower 01 together with their drive controllers 166, briefly drives 166 and the drive motors 81; 93 a group 167, z. B. drive motor 167, in particular a pressure point group 167, which is connected via a subordinate drive control 168 of this group 167 with a signals of a respective Leitachsposition ⁇ a virtual leading axis leading first signal line 171.
  • the slave drive controller 168 may also manage subgroups of printing units 01 or other divisions.
  • own subordinate drive control 168 having units, for. B. one or more guide elements (eg pull roller 133, 153, Fig. 31, 33) of a superstructure and / or Falz inconveniences 151 and / or one or more folders 137 connected. Not shown here is the possible in the same way connection to the reel splitter 131 and the retraction mechanism 132.
  • the signal line 171 is advantageously here as a first network 171 in ring topology, in particular as Sercos ring executed, which the Leitachsposition ⁇ by one with the network 171 associated higher-level drive control 172 receives.
  • a section computer receives.
  • the computing and / or data processing unit 173, receives the specification of the production speed from a control station 174 or control center computer 174 connected to it.
  • z. B. depending on a web guide, are in the correct angular position to each other.
  • 166 offset values ⁇ which define the correct relative angular position for the production relative to the common lead axis and / or relative to one of the aggregates, are provided for the individual actuators requiring registration.
  • At least these units (printing units 04 and folding unit 137) and their drives 166 are subject to angular position control.
  • Other train 02 leading aggregates such as pull rollers 133; 135; 136 and / or roll changer 131 need not necessarily be operated angular position controlled, but may be subject to a speed control.
  • the transmission of the offset values ⁇ , to the subordinate drive controls 168 takes place for. B. either via corresponding signal lines from the second network 176 directly to the drive control 168 (not shown), or advantageously via a control system 177, which is associated with the respective group 167 or its own subordinate drive control 168 having unit.
  • the control system 177 is connected to the second network 176 (or to the computing and data processing unit 173).
  • the control system 177 controls and / or regulates, for example, those of the drive motors 81; 93 different actuators and drives of the printing units 04 and folders 137, z. B. ink supply, positioning movements of rollers and / or cylinders, dampening, positions, etc.
  • the control system 177 has one or more (in particular programmable logic) control units 178 on.
  • This control unit 178 is connected to the subordinate drive control 168 via a signal line 179. In the case of a plurality of control units 178 these are through the signal line 179, z. B. a bus system 179, also interconnected.
  • the drives 166 Via the first network 171, the drives 166 thus receive the absolute and dynamic information for circulating a common control axis position .phi., And via a second signal path, in particular via at least one second network 176, the information required for register-specific processing, in particular offset values .DELTA..PHI the register-oriented relative position of the mechanically independent drives 166 or aggregates transmitted.
  • bearing assembly 14 bearing assembly 14, drive coupling, motor design as a permanent magnet synchronous motor
  • I- Printing units ie substantially rotated by 90 ° double printing units 03
  • the feature of the bearing assembly 14 and / or the linear travel and / or drive coupling, engine design are also applicable to nine- or ten-cylinder satellite printing units individually or in combinations.
  • bearing means bearing element, linear element
  • bearing means bearing element, linear element

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)

Abstract

L'invention concerne un entraînement pour un composant rotatif (06; 07) d'une machine d'impression monté à rotation sur des bâtis latéraux (11; 12). Le composant (06; 07) est entraîné en rotation par son propre moteur d'entraînement (81) et le rotor (84) du moteur d'entraînement (81) est monté à déplacement axial par rapport au bâti latéral. Le stator (86) est monté de manière à pouvoir se déplacer dans la direction axiale du cylindre (06; 07) par rapport au bâti latéral (11; 12).
PCT/EP2006/063400 2005-10-31 2006-06-21 Entrainement d'un composant rotatif d'une machine d'impression WO2007051660A1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP06777397A EP1943099A1 (fr) 2005-10-31 2006-06-21 Entrainement d'un composant rotatif d'une machine d'impression

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE200510052497 DE102005052497B4 (de) 2005-10-31 2005-10-31 Antrieb eines Zylinders einer Druckmaschine
DE102005052497.7 2005-10-31

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WO2007051660A1 true WO2007051660A1 (fr) 2007-05-10

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US11130331B2 (en) 2014-12-04 2021-09-28 Ball Beverage Packaging Europe Limited Printing apparatus
US11999178B2 (en) 2019-01-11 2024-06-04 Ball Coporation Closed-loop feedback printing system

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DE102007053596A1 (de) * 2007-11-09 2009-05-14 Manroland Ag Positionierantriebsanordnung einer Druckmaschine
WO2024110011A1 (fr) * 2022-11-22 2024-05-30 Andritz Küsters Gmbh Tête d'étanchéité d'un ensemble rouleau, ensemble de rouleau et procédé de fonctionnement d'un ensemble rouleau

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US6684775B2 (en) * 2001-06-07 2004-02-03 Heidelberger Druckmaschinen Ag Printing unit with roll-away inkers
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EP0689277A2 (fr) * 1994-06-24 1995-12-27 M.A.N.-ROLAND Druckmaschinen Aktiengesellschaft Moteur électrique pour entraîner un corps rotatif
EP0699524A2 (fr) * 1994-08-30 1996-03-06 M.A.N.-ROLAND Druckmaschinen Aktiengesellschaft Machine d'impression offset
EP0699524B1 (fr) 1994-08-30 2001-10-31 M.A.N.-ROLAND Druckmaschinen Aktiengesellschaft Machine rotative d'impression offset à bobines
DE19534651A1 (de) 1995-09-19 1997-03-20 Roland Man Druckmasch Druckwerk für indirekten Druck
EP0878302A1 (fr) * 1997-05-17 1998-11-18 MAN Roland Druckmaschinen AG Cylindre déplaçable avec entraínement électrique individuel
EP1175300B1 (fr) 2000-02-18 2004-05-26 Uteco Holding S.P.A. Machine d'impression flexographique rotative a plusieurs couleurs
WO2002081218A2 (fr) 2001-04-09 2002-10-17 Koenig & Bauer Aktiengesellschaft Groupe d'impression d'une machine d'imprimerie comportant un cylindre de transfert pouvant etre deplace lineairement
WO2003025406A1 (fr) 2001-09-14 2003-03-27 Ina-Schaeffler Kg Systeme de palier pour cylindres, rouleaux ou tambours

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US11130331B2 (en) 2014-12-04 2021-09-28 Ball Beverage Packaging Europe Limited Printing apparatus
EP3028856B2 (fr) † 2014-12-04 2023-07-26 Ball Beverage Packaging Europe Limited Appareil d'impression
US11999178B2 (en) 2019-01-11 2024-06-04 Ball Coporation Closed-loop feedback printing system

Also Published As

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DE102005052497B4 (de) 2011-09-01
DE102005052497A1 (de) 2007-05-03
EP1943099A1 (fr) 2008-07-16

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