EP2490894B1 - Devices in a printing unit of a printing machine - Google Patents

Description

The invention relates to a printing unit of a printing press with a device according to the preamble of claim 1.

The WO 03/039873 A1 discloses an inking unit with two Reibzylindern, which are rotatably in one embodiment on a same machine side by a drive motor via a belt drive together, and driven by another drive motor via a crank mechanism with respect to a traversing movement. The belt drives on a pulley, which receives the lifting movement by a correspondingly widened running surface or by a guided on bolt movement.

From the WO 2005/097505 A2 a printing unit with an inking unit is known, wherein two distribution cylinders are rotatably driven and iridescent together arranged in a housing gearbox.

By the DE 10 2007 000 554 A1 a drive concept of two distribution cylinders is disclosed, wherein only one of the two distribution cylinders is operatively rotationally positively driven by a drive motor via a pinion, and the two distribution cylinders are forcibly driven by this drive motor via respective cross thrust crank drives with respect to a traversing motion.

The post-published German patent application DE 10 2008 001 848 relates to a single drive a Reibzylinders, wherein the rotary drive from a drive motor axially via a magnetic coupling on the one pin of the Reibzylinders, and the traversing drive on the pin of the other side of the machine by a drive motor via a connecting rod of a sliding crank drive.

In the EP 0 652 104 A1 an offset printing unit of an illustration printing machine is disclosed, wherein a plurality of inking cylinders of an inking unit are tempered by tempering fluid of a temperature control circuit.

The DE 101 61 889 A1 describes an inking unit of a printing machine with a Farbreibwalze, wherein the Farbreibwalze is connected with the interposition of a permanent magnet having magnetic coupling with a drive motor. The two coupling halves of the magnetic coupling are not movable relative to each other in the direction of the axis of rotation.

The DE 39 17 074 A1 and the DE 1 233 416 B1 disclose electromagnetic clutches in inking units. A compensation for a traverse stroke within the clutch is not suggested.

The DE 103 04 296 A1 discloses a drive of a printing unit, wherein at least one inking and / or dampening roller, z. B. Reibwalze, is driven by the drive of a printing cylinder ago. For this purpose, a drive wheel arranged on the printing cylinder pin drives a traction mechanism onto a drive wheel connected to the roll neck. In order to select or couple the traction mechanism optionally a coupling member, such as a magnetic coupling, is provided, through which the arranged on the printing cylinder pin drive wheel is selectively coupled to the pin. An axial drive of the friction roller can be effected by means of a drive motor by means of a piston which can be acted upon with pressure medium or by magnetic force.

By the DE 102 27 516 A1 discloses a traversing mechanism of a friction driven friction roller, wherein in the roller a rotation in a traversing motion converting worm gear is provided.

In the DE 100 03 026 A1 a drive of a friction-driven friction roller is described, wherein in one embodiment, an axial traversing movement takes place via a crank drive driven by the machine drive and in another embodiment by a linear motor. The drive of the crank mechanism from the machine drive via a torque-adjustable coupling, z. B. slip clutch or electrically switchable coupling.

The DE 10 2005 061 028 A1 discloses a printing unit of a printing press with at least one axially movably mounted roller of a inking or dampening unit, which is on a front side via an interface to the tempering a temperature control can be fed. For the rotary drive a permanent magnet excited electric motor and for the axial drive a permanent magnet comprehensive linear motor is provided. The rotor carrying the permanent magnets of the rotary drive is rigidly connected to a roll neck.

The invention has for its object to provide a printing unit with easy to maintain and / or variable devices.

The object is achieved by the features of claim 1.

The achievable with the invention advantages are in particular that - especially for a tempering cylinder to be tempered - an oil-free and easy to maintain, yet inexpensive and less susceptible to failure drive is created. It is also particularly advantageous that the drive can be driven independently of the rotation in terms of the frequency of the friction.

The arrangement of both the rotary and the axial drive on a same machine side make room for supply systems, eg. B. the potential or actual connection to a Temperiermittelkreislauf. Nevertheless, the execution is such that the accessibility is high and the maintenance requirement is as low as possible.

The rotational drive via a belt drive, an engine size can be kept small, without an additional oil chamber would be required for corresponding additional gear transmission. A belt replacement, and thus the maintenance is therefore also considerably simplified compared to gear units with oil space.

The execution of the torque acting on the friction cylinder coupling as a magnetic coupling works without contact and thus extremely low maintenance.

The design of the crank mechanism as a cross-thrust crank mechanism protects material and increases the quality, as this - in comparison to otherwise used crank drives - actually opposite phasing realized and thus a rocking of transverse movements in the printing unit are avoidable. In particular, in terms of cost, maintenance and accessibility is an embodiment of the cross-slide crank drive of advantage, wherein in a preferred embodiment, a linear guide from standard high precision produced (complementary) "round parts" (outer circumference of a shaft and inner surface of a round hole such as a hole) is made, wherein the guide member associated with the crank comprises the one associated with a guide link. As a result, a rolling bearing could be used without having to provide clearance. A required accuracy of fit can already be achieved by available on the market vendor parts. The low maintenance can advantageously be further increased by the fact that -. B. grease lubricated - find bearings between the guide elements use. For a simplified installation / removal, it may be advantageous to form the holder receiving the linear guide pivotable within certain limits, so that the crank mechanism does not have to be completely disassembled for each removal or maintenance of the roller. Thus, a tilting of the roller and a loosening at another (simpler) position is possible.

By using a separate, different from the rotary drive drive means for the axial movement is achieved on the one hand a higher flexibility in the search for the optimum frequency, and on the other hand, an entry of load torque from the traversing drive in the rotary drive and vice versa avoided.

Embodiments of the invention are illustrated in the drawings and are in Described in more detail below.

Fig. 1

ein erstes Ausführungsbeispiel für eine Druckeinheit;

Fig. 2

ein Doppeldruckwerk aus der Druckeinheit gemäß Fig. 1;

Fig. 3

ein alternatives Ausführungsbeispiel für ein Farbwerk;

Fig. 4

ein zweites Ausführungsbeispiel für eine Druckeinheit;

Fig. 5

eine schematische Darstellung zweier changierender Walzen mit Antrieb;

Fig. 6

eine perspektifische Ansicht einer Ausführung des Antriebes gemäß Fig. 5;

Fig. 7

eine Hinteransicht der Ausführung des Antriebes gemäß Fig. 6;

Fig. 8

eine Detaildarstellung einer Ausführung des rotatorischen Antriebes in Schnittansicht;

Fig. 9

eine vergrößerte Darstellung der Magnetkupplung aus Fig. 8;

Fig. 10

eine perspektifische und ausgezogene Darstellung der Magnetkupplung aus Fig. 8;

Fig. 11

eine Schnittansicht des Changierantriebes;

Fig. 12

eine Hinteransicht des Changierantriebes;

Fig. 13

eine perspektivische Darstellung eines der Changiergetriebe;

Fig. 14

eine perspektivische Darstellung einer anderen Ausführung oder des anderen der Changiergetriebes;

Fig. 15

eine Detaildarstellung einer alternativen Ausführung des rotatorischen Antriebes in Schnittansicht;

Fig. 16

eine Detaildarstellung einer weiteren Ausführungsvariante des rotatorischen Antriebes in Schnittansicht.

Show it:

Fig. 1

a first embodiment of a printing unit;

Fig. 2

a double printing unit from the printing unit according to Fig. 1 ;

Fig. 3

an alternative embodiment for an inking unit;

Fig. 4

a second embodiment of a printing unit;

Fig. 5

a schematic representation of two iridescent rollers with drive;

Fig. 6

a perspektifische view of an embodiment of the drive according to Fig. 5 ;

Fig. 7

a rear view of the embodiment of the drive according to Fig. 6 ;

Fig. 8

a detailed view of an embodiment of the rotary drive in a sectional view;

Fig. 9

an enlarged view of the magnetic coupling Fig. 8 ;

Fig. 10

a perspektifische and solid representation of the magnetic coupling Fig. 8 ;

Fig. 11

a sectional view of the traversing drive;

Fig. 12

a rear view of the traversing drive;

Fig. 13

a perspective view of one of the traversing gears;

Fig. 14

a perspective view of another embodiment or the other of the traversing gear;

Fig. 15

a detailed view of an alternative embodiment of the rotary drive in a sectional view;

Fig. 16

a detailed view of another embodiment of the rotary drive in a sectional view.

A printing machine, z. B. web-fed rotary printing press, in particular a multi-color web-fed rotary printing press, has at least one printing unit 01, in which a web of material 02, short web 02 on both sides simply or in particular successively multiple, z. B. here four times, or multiple tracks 02 at the same time one or more times are printable.

In the Fig. 1 illustrated printing unit 01 is formed in the manner of a printing tower with a substantially vertical web run and has a plurality, in the present case, four vertically stacked double printing units 03 for the two-sided printing in rubber back-to-back operation. Such formed in the manner of printing towers printing units 01 with a bottom-up the printing unit 01 continuous web run are preferably arranged in newspaper printing machines, said z. B. several towers and a plurality of printed through this, and downstream summarized to a product tracks 02 have.

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 one as
Transfer cylinder 06 and designed as a forme cylinder 07 cylinder 06; 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. In each case between the two transfer cylinders 06 a (double) pressure point 05 is formed in Anstelllage. The above components are only on the top double printing unit 03 of Fig. 1 denotes, wherein the stacked (double) printing units 03; 04 but essentially in particular in the embodiment of the relevant features of the invention - may be identical. The double printing units 03 can just as well, contrary to the illustration in FIG. 1, without the advantageous feature of the linear arrangement described below Fig. 1 as upwardly opening u-, downwardly opening n- or otherwise offset at the pressure point 05 unit, or as in Fig. 2 represented as a flat double printing unit 03, that is, wherein the axes of rotation of the printing cylinder 06; 07 in pressure on position z. B. in a common plane E, be executed.

Shaping and transfer cylinder 07; 06 are z. B. with a bale width of at least two, z. B. four or even six juxtaposed standing printed pages in newspaper format, especially in broadsheet format formed. At least the forme cylinder 07 can in one embodiment z. B. have a circumference which essentially corresponds to two consecutively arranged printed pages in a newspaper format. In another embodiment, the scope may correspond to a single such print page.

Basically, a printing tower and two satellite printing units on top of each other with z. B. four each with a satellite cylinder cooperating printing units 04 have.

The inking 08, z. B. as well as a short inking unit 08 designated, two-row roller inking unit 08 executed, has a plurality of rollers 11; 12; 13; 14; 16 on. The inking unit 08 according to Fig. 1 and 2 includes three, the color on the printing form Rolls 11, in particular application rollers 11, which convey the ink over a dampener-remotely changeable roller 12.1, in particular a friction cylinder 12.1 (eg with a hard surface), a second, near-wetable changeable roller 12.2, in particular a friction cylinder 12.2, a further color wheel Transfer roller 13 (eg, with a soft surface), a roller 14, in particular film roller 14 and a roller 16, in particular ductor or fountain roller 16 from a color box 17 receives. Dipping and film roller 16; 14, which are characterizing designed as a film inking roller inking unit 08, can also be advantageous by another Farbzuführ- or metering, z. B. by a pumping system in Pumpfarbwerk, or lift system in the elevator inking unit to be replaced. It is also conceivable that only two applicator rollers 11 or more than three applicator rollers 11, the ink from the friction cylinders 12.1; 12.2 transmitted to the form cylinder 07. The soft surfaces of the application and / or transfer rollers 11; 13, short soft rollers 11; 13, are yielding in the radial direction, z. B. with a rubber layer, formed in what Fig. 2 and 3 through the concentric circles and in Fig. 1 expressed by reinforced lines. The following remarks on the drive of the friction cylinder 12 or more of the distribution cylinders 12.1; 12.2 are particularly advantageous i. V. m. apply such a short zweizügigem inking unit 08.

In another embodiment, the inking unit 08 as a single-inking unit 08 with two in the roller train from Farbzuführ- or metering system for forme cylinder 07 serially arranged Reibzylindern 12.1; 12.2 ( Fig. 3 ) be formed. The following remarks on the drive of the friction cylinder 12 or more of the distribution cylinders 12.1; 12.2 are also advantageous to one or more of the distribution cylinder 12.1; 12.2 of printing units 04 with this inking 08 apply.

Fig. 4 shows an alternative embodiment of the printing unit 01 as I-printing unit 01, wherein the printing unit 01 is traversed by the web 02 substantially vertically. It has a double printing 03 from two printing units 04, which is not predominantly horizontally, but predominantly vertically extends, ie their pairs of cylinders are not adjacent to each other, but are arranged one above the other. Such printing units 01 are provided in as commercial or commercial printing presses and are with regard to higher quality requirements of the products, inter alia respect. The equipment of inking and dampening 08; 09 complex, z. B. with a higher number of rollers 11; 12; 13; 14; 16 designed. So the inking unit 08 here z. B. three distribution cylinders 12.1; 12.2; 12.3, wherein the compactor from Farbzuführ- or metering system for forme cylinder 07 considered after a pressure remote from the remote cylinder 12.3 divides into two trains with a damp remover cylinder 12.1 and a near-wet grate cylinder 12.2. The following remarks on the drive of the friction cylinder 12 or more of the distribution cylinders 12.1; 12.2; 12.3 are also advantageous to one or more of the distribution cylinder 12.1; 12.2; 12.3 of printing units 04 of the printing units 01 designed as I-printing units 01 apply.

In the following, the printing units 04 and their drive the example of the embodiment according to Fig. 2 - as far as transferred but representative of the printing units 04 other design - explained.

The printing cylinder 06; 07 are mechanically driven independently of other printing units 04 by at least one drive motor, not shown. As in Fig. 2 only symbolically identified, however, is preferably each printing cylinder 06; 07 driven by a separate drive motor rotationally. In this case, the drive is in each case from the drive shaft, via possibly a clutch directly, or via its own encapsulated transmission, z. B. reduction gear, and possibly a clutch on the pin of the respective printing cylinder 06; 07. This allows the drive without otherwise required oil space.

At least one of the distribution cylinders 12 of the inking unit 08 is characterized by at least one drive means 18, for. B. a drive motor 18 mechanically independent of the Printing cylinders 06; 07 rotationally forcibly driven or force-driven. In principle, a plurality of friction cylinders 12 each have their own drive motor 18, or even a plurality of friction cylinders 12 - z. B. via a coupling or coupling gear - be assigned a common drive motor 18. The drive motor 18, the distribution cylinder 12; 12.1; 12.2 basically via a gear 26, z. B. via a Zahlrad-, preferably belt transmission, drive. The drive preferably follows via a clutch on the distribution cylinder 12. In the execution of the drive via a gear 26 can be used advantageously on standard motors without a development and production of adapted to the local application special motors would be required in small quantities.

By a subsequent, for the case of an inking unit 08 with a plurality of Reibzylindern 12 described advantageous drive solution is in formzylindernahen area of the inking unit 08, in particular in the field of ink application by the rollers 11 to the printing plate, a substantially slip-free rolling, so-called "true rolling" , and coloring is achieved.

For this purpose, one of the distribution cylinder 12, z. B. the dampening remoteness distribution cylinder 12.1, at least in production, rotational only by friction with adjacent rollers 11; 13 driven and has its rotary drive in production neither an additional mechanical drive connection for driving the printing cylinder 06; 07 or another rotationally forcibly driven roller of the inking unit 08 still has its own drive motor. In this way, the first distribution cylinder 12.1 is predominantly driven in rotation via the application rollers 11 driven by friction with the forme cylinder 07 in this example, and essentially has the circumferential speed of the forme cylinder 07 independent of the indentations in the intermediate nip points.

The other or another of the distribution cylinder 12, z. B. the feuchtwerknahe distribution cylinder 12.2 points, as in Fig. 2 indicated, this driving in the direction of rotation driving motor 18. In an advantageous development, an optionally activatable and deactivatable mechanical drive coupling can be provided between the drive motor 18 or the positively driven distribution cylinder 12.2 and the non-positively driven distribution cylinder 12.1 (see below), or a mechanical drive coupling to the operationally not necessarily driven distribution cylinder 12.1 via a freewheeling device be provided that the freewheel in the production direction of rotation and the mechanical drive coupling against the production direction of rotation is effective. This makes it possible, the non-operational force-driven distribution cylinder 12.1 at least temporarily for set-up operations such. As for washing, to drive in the first alternative via the selectively closed coupling, and in the second case in the reverse direction. This is the one, z. B. feuchttwerksferne distribution cylinder 12.1 rotationally in production only via friction with adjacent rollers 11; 13 driven, but for example zwangsbarreibbar for washing. In two in the roller train in series with each other arranged Reibzylindern 12.1; 12.2 (eg 3 or 4 ) can one of these, z. B. or the druckstellennähere (s), forced in the above sense, and the other, z. As the or a druckstellenfernerer, friction-driven (and possibly coupled).

The at least one distribution cylinder 12, or at least one of a plurality of friction cylinders 12, in particular two distribution cylinders 12.1; 12.2 of the same inking unit 08, is executed with respect to its or are forcibly driven with respect to their axial traversing movement. In principle, the two axially positively driven distribution cylinders 12.1; Although 12.2 have mechanically independent traversing drives, but they are preferably coupled together, but at least coupled.

Preferably, both distribution cylinders 12.1; 12.2 a through in Fig. 2 by respective double arrows symbolized gear 19, in particular a traversing or friction gear 19, whereby the distribution cylinder 12.1; 12.2 one over that respective friction gear 19th perform forced traversing movement in the axial direction.

In a mechanically inexpensive design, one of, z. B. the dampening remote drive cylinder 12.1 own, only his (possibly in production only by friction with an adjacent roller 11, 13 generated) rotational movement in a traversing motion forming traversing 19 have. This can then z. B. be designed as a cam gear, wherein z. B. a frame-fixed axial stop cooperates with a roller-fixed curved circumferential groove or a roller-fixed axial stop in a frame-fixed circumferential groove of a cam. Basically, this could be the rotation in an iridescent Axialhub transforming gear 19 another suitable gear 19, z. B. by an eccentric exhibiting worm or crank gear, be executed.

As in Fig. 2 symbolized by a dashed line connecting the double arrows, the traversing gear 19 of the two distribution cylinders 12.1; 12.2 advantageously, z. B. via a drive connection 21, mechanically coupled to each other. The two coupled traversing gears 19 advantageously provide a common traversing drive 22 or traversing gear 22 (FIG. Fig. 5 ) and are for the traversing movement by a drive motor 18 which causes the rotational movement different drive unit 23, z. B. a drive motor 23, forcibly driven. ( Fig. 2 ). In principle, however, could in a simple embodiment of the forced drive of the traversing gear 22 by the one distribution cylinder 12, z. B. the operationally forced driven friction cylinder 12.2, rotationally driving drive motor 18 by a transforming gear.

Preferably, the drive of the distribution cylinder 12, or the distribution cylinder 12.1; 12.2 (rotational and / or axial) formed in such a way that no extensive oil space must be provided and / or there is a simple, easily accessible maintenance and / or low wear. In particular, this should preferably be in conjunction with a distribution cylinder 12 or with Reibzylindern 12.1; 12.2 take place, one end face is free of drive elements, for example, a media supply, for. B. to be able to provide a connection of a Temperiermittelkreislaufs. The roller (s) 12; 12.1; 12.2 or the / the distribution cylinder 12; 12.1; 12.2 is or are then, for example, designed such that they face an interface 24 to a media circuit, for. B. a rotary feedthrough 24 for the inflow and outflow of a tempering fluid, and in the interior corresponding cavities and / or paths for the circulation of the tempering fluid has or have ( Fig. 5 ).

Fig. 5 schematically shows an embodiment with two Reibzylindern 12.1; 12.2, the rotation and axial drive on a same machine or front side, and a media inflow, z. B. a rotary feedthrough 24, are arranged on the other side, wherein both a rotational movement transmitting gear 26 and the or the traversing gear 19 and a torque on the distribution cylinder 12 transmitting clutch 27 may be formed without oil space. Although these design features are considered individually in each case or have particular advantages in subcombinations, they in their entirety develop a preferred solution for an oil-free, maintenance-friendly and cost-effective drive of a, or in particular second temperable, distribution cylinder 12; 12.1; 12.2. In one below too Fig. 16 set forth embodiment, the rotational movement transmitting gear 26 between the drive motor 18 and the distribution cylinder 12 or at least one of the distribution cylinder 12; 12.1; 12.2 omitted, due to which this is also driven oil-free.

The two distribution cylinders 12.1; 12.2 are mounted in side frames 30 so that they can perform both a rotational movement and an axial movement. On one of the sides of the machine in each case an above-mentioned rotating union 24 may be provided. On the other side of the machine is at least one of the two distribution cylinders 12.2 (see above) by the drive motor 18 via the belt drive 26 with a belt 36, in particular toothed belt 36, trained gear 26 forcibly driven or positively driven. The other (or more other) distribution cylinder 12.1 is not operatively coupled to the drive motor 18, and may be with its pin 28 via z. B. a thrust bearing 49, tension and compression stiff (or -fest), but freely movable with respect to a relative rotational movement, and possibly additionally coupled via a rigid, but releasable coupling, not shown, to the traversing gear 19.1. The torque of the rotary drive is transmitted from the drive motor 18 to a pin 28 of the distribution cylinder 12.2 by a coupling 27 designed as a magnetic coupling 27. By training as a belt drive 26, the gear 26 may be formed oil-free. In contrast to a gearless direct drive, a smaller sized motor, z. As well as a standard motor can be used. If necessary, in setup mode, eg. B. for washing, to drive the other distribution cylinder 12.1 can (as shown in phantom) with the latter rotatably connected gear 32 may be provided, which is selectively coupled to a non-rotatably connected to the forcibly driven positive displacement cylinder 12.2 gear 33. This is done for example via a with the two gears 32; 33 selectively engageable intermediate 31, z. B. gear 31, by z. B. a (in particular remotely operated) actuator 34 ( Fig. 6 ). So that the drive can be oil-free, this intermediate wheel 31, in particular its teeth, is preferably made of plastic.

The or preferably both distribution cylinders 12.1; 12.2 is or are in terms of their axial movement via a respective traversing gear 19.1; 19.2 positively driven, which in particular each as the rotational movement in a linear motion forming cross thrust crank drives 19.1; 19.2 are formed or at least include such kind. The traversing gear 19.1; 19.2, z. B. via a gear 29, for example, a corner gear or worm gear, driven by the drive motor 18 different drive motor 23.

Fig. 6 shows the entire drive simulation in a perspective view, wherein the distribution cylinder 12.1; 12.2 themselves are not shown. Fig. 7 shows the entire drive simulation from a rear view.

Fig. 8 to 10 show in more detail an embodiment of the rotary drive of z. B. a pinion 37 of the drive motor 18, via the belt 36 of the belt drive 26 and the magnetic coupling 27 on the distribution cylinder 12.2.

Fig. 10 shows a perspective view of a magnetic coupling 27 in the extended state. In the assembled state, the clutch 27 is preferably arranged coaxially to the axis of rotation of the friction cylinder 12 and its pin. Roller The magnetic coupling 27 comprises two coaxially arranged rotors 41; 42, namely an outer rotor 41 and an inner rotor 42, wherein the outer rotor 41 on its inner side and the inner rotor 42 on its outside with (high-quality) magnet 43; 44, in particular permanent magnet 43; 44 alternating polarity are equipped, ie alternate in the circumferential direction north and south poles. At rest, the respective north and south poles of outer rotor 41 and inner rotor 42 are opposite. By twisting the magnetic field lines are deflected, whereby torques can be transmitted through the air gap. It turns a synchronous operation under a constant backlash. The outer rotor 41 has on its circumference a race 38, z. B. an external toothing 38, on which or which with the belt 36, z. B. an internal toothing of the toothed belt 36, for the purpose of driving the outer rotor 41 cooperates. So that the outer rotor 41 can rotate, it is rotatably mounted in or on the side frame 30 via a radial bearing 39. The outer rotor 41 is driven by the drive motor 18 via the belt 36. The drive motor 18 is preferably arranged fixed to the frame and, for example, via a non-designated frame, for. B. via studs, a housing or a base, connected to the side frame 30.

In the present embodiment, the storage of the outer rotor 41 z. B. between a collar 46 of the outer rotor 41 (or a composite with this collar) and a z. B. detachably connectable to the side frame 30 frame 47, in particular a housing 47 ( Fig. 8 ). The inner rotor 42 is, for. B. via a clamping connection 48 (eg., A clamping set) with the pin 28 of the Reibzylinders 12.2 torsionally rigid and tensile and pressure rigid (or -fest) connected. With an output element 51 of the cross crank drive 19.2 of the inner rotor 42, z. B. via a thrust bearing 49, tension and compression stiff (or -fest), but freely movable with respect to a relative rotational movement. The outer rotor 41 is thus frame-fixed with respect to an axial movement, and the inner rotor 42 relative to the outer rotor 41 by the maximum amplitude of the traverse stroke, z. B. by at least 10 mm, in particular by at least 20 mm, in the example about 30 mm, axially movable. For this purpose, the magnetic coupling 27 has sufficient space. The set or desired amplitude of the traverse stroke can - if not further under or translated - have a double eccentricity e of the crank mechanism (see below).

The torque transmission between the drive motor 18 and the distribution cylinder 12.2 via the magnetic force between the outer rotor 41 and inner rotor 42. The inner rotor 42 and the outer rotor 41 are, however, in the direction of the axis of rotation of the roller 12.2 relative to each other movable. Basically, either inner rotor 42 or the outer rotor 41 in the direction of the axis of rotation of the roller 12.2 immovably (ie frame fixed with respect to an axial position), wherein in the present, with respect to simple construction advantageous example of the outer rotor 41 axially immobile and coupled to the drive motor 18, and the inner rotor 42 is axially movable and coupled to the traverse drive 22. In below too Fig. 15 described variant, this fact is provided by way of example in the reverse manner.

The changeable roller 12.2; 12.1 is thus offset by a traversing drive 22 in an axial traversing movement. The traverse stroke generated in this way becomes received by the magnetic coupling 27 characterized in that the relative position of outer rotor 41 and inner rotor 42 is not fixed, but variable. In a first traversing stroke position of the roller 12; 12.1; 12.2, the outer rotor 41 and the inner rotor 42 are arranged in a first position and in a second position of the traverse stroke of the roller 12; 12.1; 12.2, the outer rotor 41 and the inner rotor 42 are arranged in a position differing from the first position with respect to their relative axial position. The traverse stroke of the roller 12; 12.1; 12.2 can thus be recorded without contact and thus wear-free by the magnetic coupling 27. If another or the other distribution cylinder 12.1 rotationally forcibly driven, so the connection is according to the positively driven distribution cylinder 12.2 with the interposition of z. B. an external toothing having magnetic coupling 27 executable. The magnetic coupling 27 is maintenance-free because of its freedom from wear and also requires no oil chamber.

The Reiberhub for the distribution cylinder 12; 12.1; 12.2 can in principle take place in different ways, but is preferably introduced via a crank mechanism, in particular via a cross-thrust crank drive 19 described below. About the drive motor 23, which is embodied for example as an electric motor, via a gear mechanism, not shown in detail of a frame fixedly arranged gear 29, z. B. a Querverreibgetriebes 29, a shaft 52, and per traversing 19.1; 19.2 a rotatably connected to the shaft 52 crank arm 53, z. B. eccentric 53, in a rotational movement about a crank axis K, which z. B. coincides with the axis of rotation of the shaft 52. The crank axis K is in this case perpendicular or orthogonal to the roller or cylinder axis Z, along which they should perform a traversing movement.

In the crank arm 53 is, for. B. via a radial bearing 54, a crank 56 rotatably supported about an axis parallel to the crank axis K, which about the perpendicular to the roll or cylinder axis Z of iridescent traction cylinder 12; 12.1; 12.2 extending crank axis K spaced by an eccentricity e, rotates. Around tilting to prevent, the crank 56 is preferably connected to the crank arm 53 in addition to the radial bearing 54 via a non-designated hinge. Radial bearing 54 and joint can also be designed as a combined component. In a further development, the crank drive can be adjustable in its effective crank arm 53 (eccentricity e) by, for example, the crank 56 being variable at a distance from the crank axis K (possibly including storage), or a plurality of crank arms 53 having different distances and being exchangeable in a simple manner ,

The traversing gear 19.1; 19.2 further includes a tension and compression stiff with the friction cylinder 12 to be alternated; 12.1; 12.2 connected guide slot 57; 57.1; 57.2. The guide slot 57; 57.1; 57.2 has a perpendicular to the cylinder axis Z and the crank axis K extending guide member 58 which cooperates with a corresponding guide member 59 of the crank 56 as a linear guide 58, 59 together.

In the advantageous embodiment shown here, the crank 56 associated with the guide element 58, z. B. in the manner of a guide ring 58, the guide slot 57; 57.1; 57.2 associated, z. B. in the manner of a guide shaft 59 (or a bolt) formed guide member 59. The guide member 59 is connected by connecting means 66, z. B. screw 66, in a holder 61, z. B. a frame 61, stored or attached, which in turn pressure and tension over z. B. the output element 51 and the thrust bearing 49 with the pin 28 of the roller 12 to be alternated; 12.1; 12.2 is connected. During the rotation of the crank 56 about the crank axis K, the guide ring 58 on the guide shaft 59 describes an oscillating linear movement. At the same time, the guide shaft 59 experiences by the revolving crank 56, and with it the holder 61, but also a force or movement component perpendicular to the degree of freedom of the linear guide 58, 59, that is perpendicular to the longitudinal extent of the guide shaft 59, and perpendicular to the crank axis K. Through the Execution of the linear guide 58; 59 as a ring running over a wave (Round parts) can be achieved without great effort, a high degree of fit.

Between the inner, the guide shaft 59 facing side of the annular guide member 59 and the guide shaft 59, a friction-reducing bearing is provided in an advantageous embodiment. Preferably, on the inner, the guide shaft 59 facing side of the annular guide member 58 is an in Fig. 11 only indicated roller bearing 62 is arranged, roll the rolling elements on the guide shaft 59. The rolling bearing 62 further increases the life and can - for example by internal grease lubrication - reduce maintenance intervals.

The said to a traversing gear 19, is on both traversing 19.1; 19.2 two jointly zwangschangierbarer distribution cylinder 12.1; 12.2, wherein here as shown on the shaft 52 both traversing 19.1; 19.2 are driven. The guide slots 57; 57.1; 57.2 of the two traversing gears 19.1; 19.2 can in the same, z. In Fig. 13 illustrated manner formed. However, it may also be one of these, or may also both guide slot 57; 57.1; 57.2 in the way of in Fig. 14 be shown guide slot 57.1 formed. For this purpose, the guide shaft 58 receiving frame 61.1 -. B. in the range of a reibzylinderferneren end - with a second, the first frame 61.1 z. B. encompassing frame 63 so by connecting means 64, z. B. a screw 64, connected, that at mitigates partially dissolved connection of the inner and the outer frame 61.1; 64 z. B. are mutually pivotable about an axis passing through the connecting means 64 axis. As a result of this design, the relevant distribution cylinder 12 can be moved perpendicular to its cylinder axis Z at least in a small area, which considerably simplifies installation and removal and / or maintenance.

In the execution of two driven by the traversing drive 22 Reibzylindern 12.1; 12.2, it is advantageous if these are opposite in phase by 180 ° out of phase Perform traversing movements. It is expedient that the two traversing gears 19.1; 19.2 are set or adjusted so that their crank movement offset by 180 ° to each other, that is exactly the same time at the opposite dead center of the movement.

The described traversing drive 22 of two changable rollers 12.1; 12.2 thus comprises a driven by a drive motor 23, side frame fixed Querverreibgetriebe 29 and in each case one of the Querverreibgetriebe 22 driven, a crank mechanism having traversing 19.1; 19.2 each with a perpendicular to the cylinder axes Z of iridescent rollers 12.1; 12.3 extending crank axis K revolving crank 56 per iridescent roller 12; 12.1; 12.2. So that the iridescent rollers 12; 12.1; 12.2 perform a 180 phase offset counter-clockwise traversing the cranks 56 are arranged offset by 180 ° to each other about the crank axis K. The cranks 56 may be adjustable with respect to the angular position relative to the crank axis K or shaft 52. The Querverreibgetriebe 29 may for example consist of a worm drive, z. B. screw, exist. However, the traversing gear 19 preferably have not simple crank mechanisms, but cross thrust crank drives 27 with linear guide (linear guide), so that in fact an exactly opposite oscillating traversing movement of the two rollers 12.1 12.2 can be reached.

The in connection with the two friction cylinders 12.1; 12.2 explained Sachverhalrte are also apply to the drive only a Reibzylinders 12.

With more than two phase-shifted traversing movements exporting, iridescent rollers 12; 12.1; 12.2; 12.3 should preferably the traversing movements of the rollers 12; 12.1; 12.2; 12.3 by one of the number of iridescent rollers 12; 12.1; 12.2; 12.3 corresponding fraction of a full circle corresponding angle to each other out of phase. This then also corresponds to the angle by which the cranks 56 in In such a case around the crank axis K around are spaced apart or arranged. Are of a traverse drive 22 more than two iridescent rollers 12; 12.1; 12.2; 12.3 driven, the cranks 56 may also be designed as crank portions of a crankshaft.

In one of the above-mentioned embodiment Fig. The Fig. 8 with respect to the axial mobility inverted design is in Fig. 15 the inner rotor 42 axially immovable and coupled to the drive motor 18, and the outer rotor 41 axially movable and coupled to the traversing drive 22. The storage of the inner rotor 42 is z. B. via a radial bearing 39 on an advantageously releasably connectable to the side frame 30 frame 47, in particular a housing 47 (FIG. Fig. 15 ). The outer rotor 41 is, for. B. via a clamping connection 48 (eg., A clamping set) with the pin 28 of the Reibzylinders 12; 12.1; 12.2 torsionally rigid as well as tension and compression stiff (or fixed) connected. With an output element 51 of the cross crank drive 19; 19.2; 19.2 is the outer rotor 41, z. B. on the thrust bearing 49, tension and compression stiff (or -fest), but freely movable in terms of a relative rotational movement. Here, the inner rotor 42 by the Abntriebsmotor 18, z. B. via the gear 26, rotationally driven. The inner rotor 42 is frame-fixed with respect to an axial movement, and the outer rotor 41 relative to the outer rotor 41 by the maximum amplitude of the traverse stroke, z. B. by at least 10 mm, in particular by at least 20 mm, in the example about 30 mm, axially movable. For this purpose, the magnetic coupling 27 has sufficient space. The set or desired amplitude of the traverse stroke can - if not further under or translated - have a double eccentricity e of the crank mechanism (see above).

In a - advantageous also oil-free - drive variant ( Fig. 16 ), the rotatably positively driven distribution cylinder 12; 12.1; 12.2 be formed without the interposition of a transmission between the drive motor 18 and clutch 27. Here, the drive motor 18, in particular a stator 62 and a rotor 63 of the drive motor 18, coaxial with the clutch 27 and its axis of rotation is arranged. Basically, the Coaxially arranged drive motor 18 may be disposed on the reibzylinderfernen side of the clutch 27, wherein the rotor 63 of the motor 18 rotatably with the axially stationary rotor 41; 42 of the magnetic coupling 27 is connected. In connection with an attacking on the same pin 28 traverse drive 22, however, an embodiment of the drive motor 18 is advantageous, wherein the axially stationary rotor 41; 42 of the magnetic coupling 27, the magnets 66 or coil windings 66 of the rotor 63 of the drive motor 18 -. B. on its circumference - carries or at least connected to these. The on its inside magnet 64 or coil windings 64 bearing stator 62 of the drive motor 18 is then fixed to the frame, z. B. on the side frame 30 connected to the frame 47, rotatably and coaxially with the rotor 62 is arranged.

In a starting from Fig. 16 further simplified, but not shown embodiment, the clutch 27 can be omitted if the stator 62 and rotor 63 are mounted axially movable relative to each other. In this case, in the representation of the rotor 42 coincides with the rotor 63, the rotor 63 thus rotatably connected to the pin 28.

In conjunction with the o. G. rotational drive via the magnetic coupling 27 and / or the belt drive 26 and / or on the same machine side to the traverse drive 22 also other traverse drives come into consideration, such as traversing gears that convert a rotational movement of the roller in an axial traversing movement.

The device in a printing unit 04 of a printing press of the rotary drive with a magnetic coupling 27 and / or the belt drive 26 is not limited to one or more distribution cylinders 12; 12.1; Restricted 12.2 of an inking unit 08, but may alternatively or additionally for other rollers, for example, for changeable rollers of the dampening 09 come into consideration. The device is in further development in terms of the design of the rotary drive via the magnetic coupling 27 and axially to be moved printing cylinder 06; 07, in particular to a respect to the side register adjustable form cylinder 07 to transfer, in which case to the Place a traversing drive 22 a side register drive occurs by means of which the respective printing cylinder 06; 07 in view of its axial position, z. B. can be positioned as a result of a coming from a page register control or regulation command.

LIST OF REFERENCE NUMBERS

01

Printing unit, I-printing unit

02

Material web, train

03

Double printing

04

printing unit

05

(Double) Druckstelle

06

Cylinder, printing cylinder, transfer cylinder

07

Cylinder, printing cylinder, form cylinder

08

Inking unit, roller inking unit

09

dampening

10

-

11

Roller, applicator roller

12

Roller, changeable, distribution cylinder

13

Roller, ink roller, transfer roller

14

Roller, film roller

15

-

16

Roller, ductor or dipping roller

17

paintbox

18

Drive means, drive motor

19

Gear, traversing gear, friction gear, cross thrust crank drive

20

-

21

drive connection

22

Traversing drive, traversing gear

23

Drive unit, drive motor

24

Interface, rotary feedthrough

25

-

26

Transmission, belt drive

27

Clutch, magnetic coupling

28

spigot

29

Transmission, transverse drive

30

side frame

31

Intermediate gear

32

gear

33

gear

34

actuator

35

-

36

Belts, timing belts

37

pinion

38

Race, external teeth

39

radial bearings

40

-

41

Rotor, outer rotor

42

Rotor, inner rotor

43

Magnets, permanent magnets

44

Magnets, permanent magnets

45

-

46

collar

47

Frame, housing

48

clamp connection

49

thrust

50

-

51

Output element (19, 19.1, 19.2)

52

wave

53

Crank arm, eccentric

54

radial bearings

55

-

56

crank

57

guide link

58

Guide element, guide ring

59

Guide element, guide shaft

60

-

61

Bracket, frame

62

roller bearing

63

frame

64

Connecting means, screw connection

65

-

66

Connecting means, screw connection

12.1

Roller, changeable, distribution cylinder

12.2

Roller, changeable, distribution cylinder

12.3

Roller, changeable, distribution cylinder

19.1

Gear, traversing gear, friction gear, cross thrust crank drive

19.2

Gear, traversing gear, friction gear, cross thrust crank drive

57.1

guide link

57.2

guide link

61.1

Bracket, frame

61.2

Bracket, frame

e

level

K

crank axle

Z

Roll axis, cylinder axis

e

eccentricity

Claims (15)

1. A printing unit (04) of a printing machine, with a device, the device having at least one axially movably mounted roller (12; 12.1; 12.2; 12.3) on both sides in side frames (30) of an inking unit (08) or a dampening unit (09) of the printing unit (04), to which may be supplied a temperature control means for their temperature control on a front side via an interface (24), wherein at least one traversing drive (22) for producing an axial traverse stroke of the roller (12; 12.1; 12.2; 12.3) as well as at least one drive means (18) for producing a rotary movement of the roller (12; 12.1; 12.2; 12.3) are provided, wherein both the rotary drive means (18) and the traversing drive (22) engage with a same front face facing the interface (24), of the roller (12; 12.1; 12.2; 12.3), characterized in that a coupling (27) with two rotors (41; 42) axially movable relatively to each other is provided between the roller (12; 12.1; 12.2; 12.3) and the rotary drive means (18) for compensating the traverse stroke caused by the traversing drive (22), wherein a first of the rotors (41; 42) is rotatably mounted in or at the side frame (30) however stationary with reference to the direction of the axis of rotation of the roller and is mechanically engaged with the drive means (18) for its being driven into rotation, and the second of the rotors (41; 42) is connected so as to be torsionally rigid as well as tractionally rigid and compressionally rigid, with a trunnion (28) of the roller (12; 12.1; 12.2; 12.3).
2. The device according to claim 1, characterized in that the rotors (41; 42) are formed as rotors of a coupling (27) formed as a magnetic coupling (27).
3. The device according to claim 1 or 2, characterized in that the rotors (41; 42) are positioned coaxially with each other as an inner rotor (42) and an outer rotor (41).
4. The device according to claim 1, characterized in that the rotor (41; 42) connected with the trunnion (28) is connected so as to be tractionally rigid and compressionally rigid, with an output element (51) of the traversing drive (22).
5. The device according to claim 3, characterized in that the inner rotor (42) is connected so as to be torsionally rigid as well as tractionally rigid and compressionally rigid, with the trunnion (28) and the outer rotor (41) is coupled with the drive means (18).
6. The device according to claim 3, characterized in that the outer rotor (41) is connected so as to be torsionally rigid as well as tractionally rigid and compressionally rigid, with the trunnion (28) and the inner rotor (42) is coupled with the drive means (18).
7. The device according to claim 1, characterized in that the traversing drive (22) has a driven crank drive with a rotary crank (56) as well as an output element (51).
8. The device according to claim 7, characterized in that the traversing drive (22) comprises a rotary crank (56) around a crank axis (K) extending perpendicularly to the roller axis (Z) of the traversing roller (12; 12.1; 12.2; 12.3) as well as a guiding link (57; 57.1; 57.2), which is formed cooperating with the crank (56) as a linear guide (58, 59) along a direction running perpendicularly to the roller axis (Z) and to the crank axis (K).
9. The device according to one or more of claims 4 to 8, characterized in that a temperature control means may be supplied to the axially movable roller (12; 12.1; 12.2; 12.3) on a front side via an interface (24) for its temperature control, and in that both the rotary drive means (18) and the traversing drive (22) engage with a same front face facing the interface (24) of the roller (12; 12.1; 12.2; 12.3).
10. The device according to claim 9, characterized in that for linear guidance (58, 59), a guiding element (58) associated with the crank (56) encompasses a guiding element (59) associated with the guiding link (57; 57.1; 57.2).
11. The device according to one or more of the preceding claims, characterized in that the traversing drive (22) may be driven mechanically independently by a drive unit (23) different from the rotary drive means (18).
12. The device according to one or more of the preceding claims, characterized in that the rotary drive of the drive means (18) takes place on the coupling (27) via a gear (26).
13. The device according to one or more of the preceding claims, characterized in that the rotary drive of the drive means (18) takes place through a torsionally rigid connection between the driven rotor (41; 42) of the coupling (27) and a rotor (63) of the drive means (18) formed as a drive motor (18).
14. The device according to one or more of the preceding claims, characterized in that the traversing drive (22) comprises two traversing gears (19; 19.1; 19.2), by which each traversable roller (12; 12.1; 12.2; 12.3) of the inking unit (08) or the dampening unit (09) is driven so as to be traversing.
15. The device according to claim 14, characterized in that at least one of the traversable rollers (12; 12.1; 12.2; 12.3) forcibly driven into rotation in a production operation and another one of the traversable rollers (12; 12.1; 12.2; 12.3) is driven into rotation in a production operation only by friction with other rollers and/or cylinders (06; 07) of the printing unit (04).

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