EP2195166B1 - Color deck of a printing machine - Google Patents

Description

The invention relates to an inking unit of a printing press according to the preamble of claim 1.

By the WO 2006/100158 A2 an inking unit of a printing machine for coloring a forme cylinder is known, which has a compactor with at least one near the cylinder and a form cylinder remote distribution cylinder. The form cylinder near the distribution cylinder is rotationally driven only by friction with adjacent rollers, ie it is designed to the rotational drive without a mechanical drive connection going beyond the friction to a drive motor. In this way, in comparison to an inking unit, which has a compactor with at least one near the cylinder and a form cylinder remote friction cylinder, both of which are rotationally driven, created an improved color flow by near-cylinder region of the compactor almost undisturbed rolling of the juxtaposed rollers is achieved. In addition, a reduced wear and a reduced power consumption and control effort is achieved.

From the CH 614 157 A an inking unit of a printing machine is known, wherein a distribution cylinder of the inking unit is selectively driven by a reversible auxiliary motor.

On the EP 1 167 026 A2 and the EP 1 314 560 A2 In each case, an inking unit is known in which a distribution cylinder is connected via a switchable coupling with a drive motor.

The GB 1 366 228 A discloses a freewheel in a gear transmission for driving a Ink roller.

The GB 2 019 317 A describes a paint roller, which is driven by a geared motor via a freewheel.

The invention has for its object to provide an inking unit of a printing press.

The object is achieved by the features of claim 1.

It will be appreciated that the invention is in any case realized by a Inking unit, which has a roller train with at least one distribution cylinder, a drive for all distribution cylinders in a washing function against a production direction of rotation, whereas in a production direction of rotation at least not all distribution cylinders have a drive, but at least one distribution cylinder in the production direction without drive, then by Friction is driven by at least one other roller.

The achievable with the present invention consist in particular in that, in particular during cleaning or a color change, an increased cleaning quality is achieved without having to give up the well-known inking.

It is advantageous that at least one first distribution cylinder of a compactor roller has no drive connection to a drive motor in the production direction, but is rotationally driven in the production direction only via the frictional contact with cooperating rollers. He therefore exerts in the direction of production no forced via a mechanical drive connection with a drive motor rotational movement, while preferably a second z. B. formzylinderferner or receives in a zweizügigen roller train near dampening cylinder in addition to the friction gear of the rollers rotational drive energy in the production direction by mechanical coupling with a drive motor. Conversely, by a positive drive of the distribution cylinder in the setup operation, in which, for example, an ink fountain washing or doctoring takes place with a direction of rotation opposite to the direction of production rotation, a better result. For example, a wash blade can be applied without the distribution cylinder stopping.

In an advantageous embodiment, the inking unit or the roller train of the inking unit can be formed with its own side frame as a module. The drive of the inking unit can also be designed as a gear module with releasably connected drive motor and already detachably connected outside the printing machine with the side frame of the inking unit be.

In an additional advantageous embodiment, at least one distribution cylinder for maintenance purposes at standstill is preferably swung off by means of a pivotable connecting rod mechanism. This simplifies maintenance because accessibility is improved.

Furthermore, according to another advantageous development of the invention identical or identical Querverreibgetriebe assemblies for all formats, ie for different sizes and different material web widths can be used.

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

Fig. 1

eine schematische Darstellung einer Druckeinheit;

Fig. 2

eine vergrößerte Darstellung eines Doppeldruckwerkes in ebener Bauweise im Druckbetrieb mit Farbwerken, welche jeweils einen zweizügigen Walzenzug mit zwei Reibzylindern aufweisen, bei:

1. a) einem Formzylinder mit maximalem Umfang und
2. b) einem Formzylinder mit minimalem Umfang;

Fig. 3

eine schematische Darstellung der Einbaulagen zweier Reibzylinder eines Farbwerks mit zweizügigem Walzenzug eines Druckwerks des Doppeldruckwerks aus Fig. 2 bei:

1. a) einem Formzylinder mit maximalem Umfang und
2. b) einem Formzylinder mit minimalem Umfang;

Fig. 4

eine schematische Darstellung a) der Produktionsdrehrichtung und b) des Antriebsschemas eines Druckwerks des Doppeldruckwerks aus Fig. 2;

Fig. 5

eine schematische Darstellung a) der Drehrichtung entgegen der Produktionsdrehrichtung beim Farbwerkswaschen und b) des Antriebsschemas eines Druckwerks des Doppeldruckwerks aus Fig. 2;

Fig. 6

eine schematische Darstellung eines Reibzylinders in einer von einer Auftragswalze abgeschwenkten Stellung in

1. a) einer Seitenansicht und
2. b) in einer Vorderansicht;

Fig. 7

eine schematische Darstellung des festen Achsabstandes der Reibzylinder eines Druckwerks des Doppeldruckwerks aus Fig. 2 bei unterschiedlichen Formaten a), b), c) bzw. Papierbahnbreiten;

Fig. 8

eine schematische Darstellung einer Querverreibgetriebe-Baugruppe;

Fig. 9

eine schematische Darstellung der Querverreibgetriebe-Baugruppe aus Fig. 8 in einem Einbauzustand bei Produktionsdrehrichtung;

Fig. 10

eine schematische Darstellung der Querverreibgetriebe-Baugruppe aus Fig. 8 in einem Einbauzustand bei Drehrichtung entgegen Produktionsdrehrichtung;

Fig. 11

eine schematische Darstellung der Querverreibgetriebe-Baugruppe aus Fig. 8 in einem Einbauzustand in abgeschwenkter Stellung;

Fig. 12

eine schematische Darstellung der Querverreibgetriebe-Baugruppe aus Fig. 8 in an eine Auftragswalze angestellter Stellung in:

1. a) einem in einer durch die Achsen der Reibzylinder gebildeten Ebene liegenden Querschnitt und
2. b) einem Querschnitt senkrecht zu den Achsen der Reibzylinder;

Fig. 13

eine schematische Darstellung der Querverreibgetriebe-Baugruppe aus Fig. 8 in einer von einer Auftragswalze abgeschwenkten Stellung in:

1. a) einem in einer durch die Achsen der Reibzylinder gebildeten Ebene liegenden Querschnitt und
2. b) einem Querschnitt senkrecht zu den Achsen der Reibzylinder und
3. c) einer Ansicht auf Schwenkhebel und Querverreibgetriebe-Baugruppe von der Seite;

Fig. 14

eine schematische Darstellung eines Schubkurbelgetriebes zum axialen Antrieb eines durch einen Antriebsmotor in und entgegen Produktionsdrehrichtung angetriebenen Reibzylinders;

Fig. 15

eine schematische Darstellung eines Schubkurbelgetriebes zum axialen Antrieb eines durch einen Antriebsmotor nur entgegen Produktionsdrehrichtung angetriebenen Reibzylinders in an eine Auftragswalze angestellter Stellung;

Fig. 16

eine schematische Darstellung eines Schubkurbelgetriebes zum axialen Antrieb eines durch einen Antriebsmotor nur entgegen Produktionsdrehrichtung angetriebenen Reibzylinders in von einer Auftragswalze abgeschwenkter Stellung;

Fig. 17

eine schematische Darstellung eines abschwenkbaren Pleuelmechanismus in einer Seitenansicht in a) in an eine Auftragswalze angestellter Stellung und b) in von einer Auftragswalze abgeschwenkter Stellung, sowie in einer Draufsicht in c) in an eine Auftragswalze angestellter Stellung und d) in von einer Auftragswalze abgeschwenkter Stellung;

Fig. 18

eine schematische Darstellung eines Getriebes, welches in Produktionsdrehrichtung über einen Freilauf, und entgegen der Produktionsdrehrichtung über eine drehmomentschlüssige Kopplung verfügt.

Show it:

Fig. 1

a schematic representation of a printing unit;

Fig. 2

an enlarged view of a double printing in a flat design in the printing operation with inking units, each having a two-speed compactor with two Reibzylindern, in:

1. a) a forme cylinder with maximum circumference and
2. b) a form cylinder with a minimum circumference;

Fig. 3

a schematic representation of the mounting positions of two distribution cylinders of an inking with zweizügigem roller train of a printing unit of the double printing from Fig. 2 at:

1. a) a forme cylinder with maximum circumference and
2. b) a form cylinder with a minimum circumference;

Fig. 4

a schematic representation of a) the production direction of rotation and b) the drive scheme of a printing unit of the double printing from Fig. 2 ;

Fig. 5

a schematic representation of a) the direction of rotation against the production direction of rotation during inking unit washing and b) the drive scheme of a printing unit of the double printing from Fig. 2 ;

Fig. 6

a schematic representation of a Reibzylinders in a pivoted-off from an applicator roll position in

1. a) a side view and
2. b) in a front view;

Fig. 7

a schematic representation of the fixed center distance of the distribution cylinder of a printing unit of the double printing from Fig. 2 for different formats a), b), c) or paper web widths;

Fig. 8

a schematic representation of a Querverreibgetriebe assembly;

Fig. 9

a schematic representation of the Querverreibgetriebe assembly from Fig. 8 in an installed state in the production direction of rotation;

Fig. 10

a schematic representation of the Querverreibgetriebe assembly from Fig. 8 in an installed state in the direction of rotation against the direction of production rotation;

Fig. 11

a schematic representation of the Querverreibgetriebe assembly from Fig. 8 in an installed state in the pivoted position;

Fig. 12

a schematic representation of the Querverreibgetriebe assembly from Fig. 8 in Position employed on an applicator roll in:

1. a) lying in a plane formed by the axes of the distribution cylinder cross-section and
2. b) a cross section perpendicular to the axes of the distribution cylinder;

Fig. 13

a schematic representation of the Querverreibgetriebe assembly from Fig. 8 in a position deviated from an applicator roll in:

1. a) lying in a plane formed by the axes of the distribution cylinder cross-section and
2. b) a cross section perpendicular to the axes of the distribution cylinder and
3. c) a view of the pivot lever and Querverreibgetriebe assembly from the side;

Fig. 14

a schematic representation of a slider-crank mechanism for the axial drive of a driven by a drive motor in and against production rotation direction of the friction cylinder;

Fig. 15

a schematic representation of a sliding-crank mechanism for the axial drive of a driven by a drive motor only against production rotation direction of the friction cylinder in an employed job roll position;

Fig. 16

a schematic representation of a slider-crank mechanism for the axial drive of a driven by a drive motor only against production rotation direction of the friction cylinder in a swung-off position of an applicator roller position;

Fig. 17

a schematic representation of a pivotable connecting rod mechanism in a side view in a) employed in an applicator roll position and b) pivoted away from an applicator roller position, as well as in a plan view in c) in an employed position on an applicator roll and d) in a position pivoted away from an applicator roll;

Fig. 18

a schematic representation of a transmission which has in the production direction of rotation via a freewheel, and contrary to the production direction of rotation via a torque-locking coupling.

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 web of material 02, short web 02 on both sides simply or in particular successively multiple, z. B. here four times, or several tracks at the same time one or more times are printable. The printing unit 01 has a plurality of, in the present case four, vertically stacked double printing units 03 for the two-sided printing in the 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 06 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. 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, however, can be made identical, in particular in the embodiment of the features relevant to the invention. The double printing units 03 can - as well as the below-described advantageous feature of the linear arrangement - as well contrary to the illustration in Fig. 1 as an upwardly opening U unit or as in Fig. 2 represented as Ebenes double printing unit 03, that is, wherein the axes of rotation of the printing cylinder 06; 07 in pressure-on position in a common plane, 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.

The inking 08, z. B. as well as a "short inking unit" designated, two-drum roller unit 08 executed, has a plurality of rollers 11; 12; 13; 14; 16 on. The inking unit 08 according to Fig. 2 . 4, 5 and 6 comprises three, the color to the printing plate of the forme cylinder 07 rollers 11, in particular applicator rollers 11, the color of a moist machine remotely changeable roller 12.1, in particular Reibzylinder 12.1 (eg., With a hard surface), a second, near the humidor Changable roller 12.2 in particular Grater cylinder 12.2, another ink or transfer roller 13 (eg, with a soft surface), a roller 14, in particular film roller 14 and a roller 16, in particular ductor or dip roller 16 from a color box 17 receives. Dipping and film roller 16; 14, which are characteristic of a film inking, can also be advantageous by another Farbzuführ- or -dosiersystem, z. B. by a pumping system in Pumpfarbwerk, or lift system in the elevator inking unit to be replaced. It is also conceivable that more than three applicator rollers 11, the ink from the Reibzylindern 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 is expressed by the concentric circles.

Now, the rollers 11; 12; 13; 14 of the inking 08 hired together, so dive depending on the contact pressure and / or travel the hard surfaces of the distribution cylinder 12.1; 12.2 in the soft surfaces of the respective cooperating soft rollers 11; 13 more or less far. As a result, depending on the indentation depth, the circumferential ratios of successively rolling, cooperating rollers 11 change; 12; 13; 14th

Now, for example, for one of several co-acting rollers a rotary positive drive by specifying a speed, z. Example, via a drive motor or a corresponding mechanical drive connection to another driven component, then rotates an adjacent, driven only by friction of the former roller ago soft roller depending on Eindrückiefe with different speed. In the event that this soft roller but additionally driven by a separate drive motor or additionally via friction in a second Nipstelle from another speed-determined roller ago, this can in the first case to a difference between motor-specified speed and friction caused by friction, and in the second case, there is a difference between the two speeds caused by friction. Slippage occurs at the nip points and / or the drive motor (s) are unnecessarily heavily loaded.

In the area close to the cylinder surface of the inking unit 08, in particular in the region of the application of ink by the rollers 11 to the printing forme, a slip-free rolling, so-called "true rolling", and inking is achieved by the solution described below.

The dampening remote drive cylinder 12.1 is rotatory in the production direction only via friction with adjacent rollers 11; 13 driven and points to its rotary drive in the production direction ( Fig. 2 and 4 ) neither an additional mechanical drive connection for driving the printing cylinder 06; 07 or another rotationally driven roller of the inking unit still on its own drive motor. In this way, the first distribution cylinder 12.1 predominantly over in this Example three driven by friction with the forme cylinder 07 applicator rollers 11 rotationally driven and has, regardless of the indentations in the intermediate Nipstellen substantially the peripheral speed of the forme cylinder 07 on. The dampening near proximity cylinder 12.2 has, as in Fig. 2 indicated, a rotationally driving in the direction of production drive motor 18, which, however, in an in Fig. 2 indicated direction of production next to the through the rollers 12.2; 13; 12.1 formed friction gear has no mechanical coupling to the first distribution cylinder 12.1. However, the drive motor 18 is able to drive both the first, remotely dampened distribution cylinder 12.1, and the second, near the wet offset near cylinder 12.2 in a washing or Rüstdrehrichtung against the production direction of rotation. By a positive drive of the distribution cylinder 12.1; 12.2 in the setup operation, in which, for example, an inking unit washing or doctoring takes place with a rotational direction counter to the production direction of rotation, a better result is achieved, for example, as a wash blade 10 (FIG. Fig. 2 . 4 . 5 . 9 and 10 ) can be recognized without the distribution cylinder 12.1 stops. Thus, the first, dampening remote drive cylinder 12.1 rotationally in the production direction only by friction with adjacent rollers 11; 13 driven, ie that it is designed to the rotational drive in the production direction without rotation beyond the friction, a torque transmitting mechanical drive connection to the drive motor 18, and that the first, remotely dampening distribution cylinder 12.1 in a washing or Rüstdrehrichtung against the production direction of rotation rotatory is driven by the drive motor 18, that is, that it is formed to the rotational drive against production rotation direction with a torque transmitting mechanical drive connection to the drive motor 18. In contrast, the second, near-the wet offset cylinder 12.2 in both directions of rotation additionally forcibly driven by the drive motor 18 both in and against the production direction of rotation. In addition, in addition, since it is too frictional with adjacent rollers 11; 13 is coming. For more than two friction cylinders 12.1; 12.2, z. B. three, the two dampened close rotationally forced, or only the middle or the next adjacent to the dampening cylinder distribution cylinder 12.2 can be rotationally forced driven.

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 by double arrows in the Fig. 4 b) and 5 b ) perform indicated traversing movement.

In a mechanically less complex design, the dampening remote drive cylinder 12.1 has its own, only his in the direction of production only by friction with an adjacent roller 11; 13 generated rotational movement in a traversing movement forming traversing gear 19. This can be advantageously designed as a cam gear, wherein z. B. a frame-mounted 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 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 first Reibzylinders 12.1 is mechanically coupled via a gear 21 with the traversing mechanism 19 of the second Reibzylinders 12.2 in an advantageous manner. Advantageously, the two coupled traversing gear 19 is a common traversing drive 22 or traversing gear 22 and are for their traversing movement forcibly driven by a drive motor 18. Preferably, the forced drive of the traversing gear 22 is effected by the drive motor 18 rotatably driving the second distribution cylinder 12. 2 in the production direction of rotation (FIG. Fig. 2 and 12 ).

That in the 4, 5 and 6 shown again schematically inking 08 has improved print quality at the same time shorter inking unit 08 and thus lower ink layer thicknesses in the inking unit 08, resulting in less spraying and less mist in the inking unit 08. Preferably, at least one distribution cylinder 12.1 of the compactor is in the pressure on position ( 4 and 5 ) in the production direction of rotation ( Fig. 4 ) exclusively via friction with at least one adjacent roller 11; 13 rotationally driven, and contrary to the production direction of rotation ( Fig. 5 ) driven by a motor. Preferably, in the production direction of rotation is exclusively via friction with at least one adjacent roller 11; 13 rotatably driven distribution cylinder 12.1 a dampening remoteness distribution cylinder 12.1. Preferably, both in and against the production direction of rotation in addition by the drive motor 18 rotatably driven distribution cylinder 12.2 is a dampening near the cylinder 12.2. In print on position ( 4 and 5 ) finds it in the Fig. 4 b) and 5 b ) indicated by double arrows traversing the distribution cylinder 12.1; 12.2 both in one direction of rotation in, and against the production direction of rotation instead, whereas in pressure-off position ( Fig. 6 ) no oscillation takes place at standstill. The positive drive of the distribution cylinder 12.2 in the production direction of rotation is in Fig. 4b) indicated by a rotary arrow, as well as the positive drive of both distribution cylinders 12.1; 12.2 contrary to the direction of production in Fig. 5b) ,

In the Fig. 12 and 13 is an advantageous embodiment for the drive of the distribution cylinder 12.1; 12.2, wherein only the second distribution cylinder 12.2 is forcibly driven rotationally in the production direction of rotation, however, both distribution cylinders 12.1, 12.2 are axially forcibly driven in rotation via the common traversing drive 22, as well as counter to the production direction of rotation.

For this purpose drives the drive motor 18 via a coupling 23 via a shaft 24 to a drive pinion 26, which in turn interacts with a non-rotatably connected to the second distribution cylinder 12.2 spur gear 27 together. Between the drive pinion 26 and the Spur gear 27 is an intermediate 25 is arranged. The connection can z. B. via a spur gear 27 supporting shaft portion 28 on a pin 29 of the second Reibzylinders 12.2 done. A corresponding axle section 28 of the first distribution cylinder 12. 1 has an in Fig. 18 enlarged illustrated transmission 35 in the form of a spur gear 35 with a freewheel 50 in the production direction of rotation or in the production direction of rotation no torque transmitting mechanical drive connection to the drive motor 18.

Thus, in the production direction of rotation is exclusively via friction with at least one adjacent roller 11; 13 rotationally driven, and to drive in washing or Rüstdrehrichtung contrary to the production direction of rotation with a torque transmitting mechanical drive connection to the drive motor 18 fitted friction cylinder 12.1 connected by means of the gear 35 and spur gear 35 to the drive motor 18, which in the production direction of rotation via a freewheel 50th , And in washing or Rüstdrehrichtung contrary to the production direction of rotation has a torque-locking coupling.

Under a freewheel 50 is understood in the present context, a direction of rotation independent coupling. The direction of production is the direction of rotation during printing.

The drive connections between the drive pinion 26 and the spur gear 35 of the first friction cylinder 12.1 and between the drive pinion 26 and the spur gear 27 of the second friction cylinder 12.2 are preferably straight toothed and formed with a sufficiently large overlap in the teeth engagement for each position of the traversing movement. The two distribution cylinders 12.1; 12.2 are in a side frame 31 in bearings 32, z. B. radial bearings 32 are mounted, which additionally allow an axial movement ( FIGS. 15 and 16 ). A rotational drive connection between the drive motor 18 and the first distribution cylinder 12.1 in the production direction of rotation does not exist here. The freewheel 50 of the gear 35 designed as a spur gear 35 can not torque in Production direction of rotation on the load-bearing clamping hub 51 (FIG. Fig. 18 ) transmitted to the pin 29 of the first Reibzylinders 12.1. Drive pinion 26 and arranged on the axle portion 28 spur gear 27 together represent a transmission, in particular reduction gear, for the rotary drive in and against the production direction of rotation. Drive pinion 26 and arranged on the axle portion 28 spur gear 35 together constitute a transmission, in particular reduction gear for The two drives constitute a closed and / or preassembled unit with its own housing 30. The unit can be coupled on the output side to the pins 29.

The traversing drive 22 is also by the drive motor 18, z. B. via a worm drive 33, 34, driven. In this case, is rubbed by a shaft 24 disposed from the screw 33 and a screw 33 formed as a portion of the shaft 24 on a worm wheel 34 which rotatably with a perpendicular to the axis of rotation of the distribution cylinder 12.1; 12.2 extending shaft 36 is connected. Each end face of the shaft 36, a driver 37 is arranged eccentrically to the axis of rotation, which in turn z. B. via a crank mechanism, for example via a rotatably mounted on the driver 37 connecting rod 38 and a hinge 39, in the axial direction of the distribution cylinder 12.1; 12.2 pressure and zugsteif with the pins 29 of the distribution cylinder 12.1; 12.2 is connected. In Fig. 8 the friction gear 19 of the dampening remote drive cylinder 12.1 and the dampening cylinder near the friction cylinder 12.2 are merely indicated because they are hidden in this view by the spur gear 35 and by the spur gear 27. A rotation of the shaft 36 causes a rotation of the driver 37, which in turn via the crank drive an axial stroke of the distribution cylinder 12.1; 12.2 causes. The output to the traversing drive 22 can also take place at another point of the rotary drive train between the drive motor 18 and the distribution cylinder 12.2 or even on the other side of the machine located on the other end face of the Reibzylinders 12.2 pin 29 to a corresponding traversing gear 22. Also, if necessary, one of a worm drive 33, 34 different gear for decoupling the axial drive may be provided.

As in the Fig. 12 and 13 shown, the traversing drive 22 and the traversing gears 22 are overall designed as a unit with its own housing 41, which can be designed additionally encapsulated. The traversing gear 22 may be lubricated in the enclosed space either with oil, but preferably with a grease. The traversing gear 22 is supported in the illustrated embodiment by a holder 42 connected to the side frame 31. The drive motor 18 is in this case releasably connected to the housing 41 of the traversing gear 22.

Fig. 5 16 and 16 show an advantageous embodiment of a torsionally rigid connection between the axle portion 28 and the respective pin 29. This is with respect to a rotation about a frictional engagement, which by clamping a tapered portion of the pin 29 made by this comprehensive, slotted shaft portion 28 becomes. The position of a clamping screw 43 is dimensioned such that it - at least partially immersed in a circumferential groove of the pin 29 - viewed transversely to the axis of rotation of the pin 29. It thus represents an interlocking securing of the connection with respect to an axial direction.

Based on Fig. 12 . 13 . 14 . 15 and 16 a further advantageous development is explained, wherein the distribution cylinder 12.1; 12.2 including rotary and axial drive in the manner of a total pre-assembled and / or movable module on its own, of a the printing cylinder 06; 07 carrying side frame 44 structurally different side frame 31 are arranged. A second, the distribution cylinder 12.1; 12.2 on its other front side supporting frame side is in the Fig. 14 . 15 and 16 not shown. These the distribution cylinders 12.1; 12.2 and their drive supporting side frames 31 are then depending on the size and geometric arrangement of the printing cylinder 06; 07 positionable on the side frame 44.

The prefabricated preferably as a module transmission unit (from axial and / or traversing 22) can be completely pre-assembled as a subunit for example designed as a module inking 08 and be pre-assembled in an advantageous embodiment before use in the printing unit 01 on the side frame 31 of the inking unit module. On the other hand, the modularity also allows the installation / replacement / replacement of the module designed as a transmission when the inking unit module is already inserted into the machine.

Due to the fact that the dampening remoteness cylinder 12.1 does not have a rotational forced drive in the production direction of rotation, the rollers 11 (13) roll off each other largely without slippage, at least in the inking unit area remote from the dampening unit.

In principle, the drive motor 18, which drives the second distribution cylinder 12.2 both rotationally in the direction of production rotation and counter to the direction of production rotation, can be designed as an electric motor which can be controlled with respect to its power and / or torque and / or also with respect to its speed. In the latter case, if the drive motor 18 is also operated in speed-controlled / pressure-controlled manner, then it can still be in the vicinity of the inking unit 08 in the vicinity of the dampening system. Problems arise with regard to different effective roll circumferences.

In view of the above-described problematic of a competing with the friction gear speed specification, however, the drive motor 18 is advantageously designed such that it at least during the printing operation with respect. Its power and / or its torque is controlled or regulated. This can basically be done by means of a drive motor 18 designed as a synchronous motor 18 or as an asynchronous motor 18:

In a first, with respect to the effort most simple embodiment of the drive motor 18 designed as an asynchronous motor 18, which in an associated drive control 46 ( Fig. 12 ) only one frequency, z. B. in pressure-down of the inking unit 08, as in Fig. 13 illustrated, and / or an electrical drive power or a torque in pressure on the inking unit 08, as in Fig. 12 represented, is given. In print-Ab of the inking unit 08, ie the applicator rollers 11 are out of rolling contact with the forme cylinder 07 ( Fig. 6 . 11 and 13 ), over a predetermined frequency, the inking unit 08 via the second distribution cylinder 12.2 can be brought to a suitable for the pressure-On-sites peripheral speed in production direction of rotation, in which the peripheral speeds of forme cylinder 07 and applicator rollers 11 only by less than 10%, in particular less than 5%, differ from each other. This limit is also advantageous as a condition for the pressure-on-sites of the embodiments mentioned below. A suitable frequency or performance or torque specification is empirically and / or computationally determined beforehand and held either in the drive control itself, a machine control or a control center computer, wherein the default value is preferably changeable by the operator. This also applies advantageously to the default values mentioned below.

In print-on, ie the applicator rollers 11 are in rolling contact with the forme cylinder 07 and all rollers 11; 12.1; 12.2; 13; 14 of the inking 08 hired against each other, as shown schematically in the Fig. 1 . 2 . 4, 5 . 9 . 10 and 12 shown, the rollers 11; 12.1; 13; 12.2; 13; 14 to a part of the forme cylinder 07 via the now produced friction gear between the rollers 11; 12.1; 13; 12.2; 13; 14 in the production direction of rotation ( Fig. 2 . 4 and 9 ) or contrary to production direction of rotation ( Fig. 5 and 10 ) rotationally driven, so that the drive motor 18 only has to bring in the increasing power dissipation in the friction gears with increasing distance from the forme cylinder 07. D. h., The drive motor 18 can be operated with a small (drive) torque or a small drive power, which only contributes to the rear of the inking unit 08 on the substantially predetermined by the frictional contact To maintain peripheral speed. This drive power can be left constant in a first variant for all production speeds or speeds of the forme cylinder 07 and either correspond to those specifications for starting in pressure-Ab or represent their own constant value for production. In a second variant, the frequency and / or drive power can be predetermined and stored for different production speeds and additionally, if necessary, for starting in pressure-off different specifications. Depending on the production speed, depending on the production speed, then the default for the drive motor 18 can vary.

In a second embodiment, the drive has in addition to the drive control 46 ( Fig. 12 ) and the asynchronous motor 18 of the first embodiment, a speed feedback, so that the drive motor 18 in the phase of the inking unit operation in pressure-Ab ( Fig. 6 . 11 and 13 ) With the speed of the associated forme cylinder 07 and the printing cylinder 06; 07 is essentially synchronized. For this purpose, the actual speed detecting sensor 47, z. As a rotary encoder 47, on a rotatably connected to the distribution cylinder 12.2 rotating component, eg. Example, a rotor of the drive motor 18, the shaft 24, the shaft portion 28 or the pin 29, be arranged ( Fig. 12 ). In Fig. 12 a rotary encoder 47 having a co-rotating initiator and stationary sensor 47 is shown by way of example on the coupling 23, the signal of which is fed to the drive control 46 via a signal connection shown by dashed lines for further processing. Due to the speed feedback, the comparison with a rotational speed M representing the engine speed and a corresponding adjustment of the power or frequency specification, a slip at the moment of pressure on-position can be avoided or at least minimized to a few percent. In the print-on operation, the drive motor 18 is then preferably no longer strictly with respect to. The described speed feedback but essentially operated according to the above-described frequency or power specification.

A third embodiment has a synchronous motor 18 instead of the asynchronous motor 18 of the second embodiment. A speed feedback and a related synchronization and control in the pressure-off phase is carried out according to the second embodiment, for. B. again in the drive control 46th

In a fourth embodiment, a drive motor 18, in particular a synchronous motor 18, is provided, which is optionally speed-controlled in a first mode (for inking unit 08 in print-Ab) and in a second mode with respect to a torque (for inking unit 08 in print-on). is controllable. Drive control 46 and drive motor 18 preferably have an internal control loop for speed control, which, similarly to the second embodiment, comprises a return from an external rotary encoder 47 or an internal motor sensor system. When synchronous motors 18 are used, a plurality of these synchronous motors 18 of a printing unit 01 can be assigned a common frequency converter or converter.

A respect to versatility advantageous, but more complex development of the fourth embodiment is the formation of the drive motor 18 as an optional position and torque controllable servo motor 18, d. H. a three-phase synchronous motor with a device which allows to determine the current rotational position or the angle of rotation with respect to an initial position of the rotor. The feedback of the rotational position can via a rotary encoder, z. As a potentiometer, a resolver, an incremental encoder or an absolute encoder done. In this embodiment, each drive motor 18 is assigned its own frequency converter or converter.

In the case of an at least speed-synchronizable, in particular speed-controllable drive motor 18 designed in the manner of the second, third or especially fourth embodiment, the drive control 46 is advantageously in signal connection with a so-called virtual master shaft in which an electronically generated master axis position Φ circulates. The circumferential Leitachsposition Φ serves the Synchronization, with respect to correct angular position and its temporal change (angular velocity Φ̇) mechanically independent drive motors of aggregates, which are assigned to the same path, in particular drive motors of individual printing cylinders or groups of printing groups and / or the drive of a folder. In the mode of operation in which the inking unit 08 is to be driven in synchronism with respect to the rotational speed of the forme cylinder 07, a signal connection to the virtual master axis can thus provide the drive controller 46 with the information about the engine speed.

The drive of the friction cylinder 12.2 is thus preferably moved by the drive motor 18 in such a way that the drive motor 18 is driven or regulated in a controlled manner in the case of the inking unit 08 running in the production direction of rotation but in the down position (ie parked applicator rollers 11) and when the printing press is running, as soon as a printing on the inking unit 08 (ie the applicator rollers 11) is done, the speed control or control is deliberately abandoned. D. h., It is no longer held at a speed, but the drive motor 18 is in the further course of a torque, for. B. over a predetermined electrical power, and / or in terms of a controller on the drive motor 18, in particular asynchronous motor 18, adjustable torque operated. The torque to be set or the power to be adjusted is chosen, for example, smaller than a limit torque, which would lead to a first rotation (under slip) of the driven in the production direction of rotation friction cylinder 12.2 at salaried, but with respect. Set the rotation cooperating rollers 13.

The load characteristic of a drive motor 18 embodied as an asynchronous motor 18 counteracts the behavior intended for the purpose here in such a way that, as the load increases, the frequency is reduced while the drive torque increases. Goes in the friction gear between form cylinder 07 and second Friction cylinder 12.2, for example, already much of the forme cylinder 07 derived drive energy and thus lost peripheral speed, so that the load of the drive motor 18 increases, so the increased torque is provided at a reduced frequency. Conversely, little torque is transmitted by the drive motor 18 - it runs virtually empty - if, for example, sufficient energy is transmitted via the friction gear to the distribution cylinder 12.2 in the production direction of rotation.

Furthermore, the inking unit 08, as in the Fig. 2, 3rd and 7 shown schematically, a constant distance of the distribution cylinder 12.1; 12.2 for all formats, so for different sizes and different web widths on. In this case, the axial distance A of the two distribution cylinders 12.1; 12.2 identical for different shape cylinder diameter, as in the Fig. 2 a) and 3 a ) for a forme cylinder 07 with maximum circumference, and in the Fig. 2 b) and 3 b ) indicated for a forme cylinder 07 to a minimum extent. Advantages of this result from the fact that regardless of the diameter of the forme cylinder 07 in the Fig. 4 b), 5 b), 6 b ) 8, 9 . 10 and 11 shown, identical or identical Querverreibgetriebe assembly 45 consisting of traversing gears 19, spur gear 20, 21 gear and traversing 22 for all formats, so for different sizes and different material web widths can be used.

At least one distribution cylinder 12.1; 12.2 is, for example, for maintenance or for inking from a in the Fig. 4, 5 . 9 and 10 shown, employed on an applicator roll 11 position in a in the Fig. 6 and 11 represented pivoted from the applicator roller 11 position preferably swung down at a standstill. This is an in Fig. 17 illustrated, pivotable connecting rod mechanism 48 is provided to the at least one distribution cylinder 12.1; 12.2 to reduce ( Fig. 12 and 13 ).

1. a) Rotatorischer Antrieb lediglich eines von mehreren Reibzylindern 12.1; 12.2 im Druckbetrieb, um Schlupf, Verschleiß und Antriebsbelastung durch unterschiedliche wirksame Durchmesser bei an weiche Walzen 11; 13 angestellten Zylindern 06; 07 zu verringern (Fig. 4 und 9).
2. b) Rotatorischer Zwangsantrieb aller Reibzylinder 12.1; 12.2 im Rüstbetrieb entgegen der Produktionsrichtung, um ein Farbwerkwaschen bzw. Rakeln mit Drehrichtung entgegen Druckbetrieb zu ermöglichen (Fig. 5 und 10). Beim Rakeln/Farbwerkwaschen findet dabei, wie in den Fig. 5 und 10 dargestellt, eine Drehrichtung entgegen der Produktionsdrehrichtung statt. Die Reibzylinder 12.1; 12.2 sind dabei zwangsangetrieben, um nicht durch eine Waschrakel 10 zum Stillstand gebracht werden zu können, wodurch das Waschergebnis nicht zufriedenstellend wäre.
3. c) Abschwenkbarer Reibzylinder 12.1; 12.2 für Wartungszwecke im Stillstand mittels abschwenkbarem Pleuel-Mechanismus 48 (Fig. 17), um die Zugänglichkeit beispielsweise beim Farbwerkswaschen und/oder Formzylindertausch zu verbessern (Fig. 6 und 11). Zum Tausch der zweiten, mittleren Auftragswalze 11 nach oben, ist es erforderlich, den im Druckbetrieb friktionsgetriebenen Reibzylinder 12.1 soweit vom dem in Druck-Ab stehenden Formzylinder 07 wegzubewegen, dass der Abstand der beiden Oberflächen größer ist, als der Durchmesser der auszubauenden Auftragswalze 11. Dies erfolgt ausschließlich bei Stillstand der Druckmaschine. Das Abschwenken stellt eine bedienerfreundliche Lösung dar, die keine Demontage von Bauteilen erfordert. Um einen Ausbauraum für die mittlere Auftragswalze 11 zu schaffen ist wie in den Fig. 12, 13, 15 und 16 dargestellt, der Reibzylinder 12.1 in einem Schwenkarm 59 gelagert. Dabei zeigen die Fig. 12 und 15 eine angeschwenkte Stellung, und die Fig. 13 und 16 eine abgeschwenkte Stellung des feuchtwerkfernen Reibzylinders 12.1. Der feuchtwerksferne Reibzylinder 12.1 ist beidseitig, wie in den Fig. 12 und 13 dargestellt, in einem Lager 49, vorzugsweise einem Zylinderrollenlager 49 mit Gelenkkalotte am Außenring gelagert, die sich wiederum in abschwenkbaren, gestellinnenseitigen Hebeln 59 befinden, die den Schwenkarm 59 bilden. Die Fig. 15 und 16 zeigen dabei jeweils eine vergrößerte Darstellung nur der antriebsseitigen Seite. Die Gelenklager sind erforderlich zum Ausgleich einer Schiefstellung bei einseitiger Schwenkarm 59 An-/Abstellung. Dadurch ist keine Synchronabstellung nötig. Die Drehpunkte der Schwenkarme 59 und die Mittelpunkte der Walzenschlösser 15 der Farbwalze 13 fallen dabei zusammen (Fig. 13 c)). Vorzugsweise sind die Schwenkarme 59 um die Walzenschlösser 15 gelagert und mittels 62 Stellschrauben und Stellmuttern 64 in ihrer Lage in Bezug auf einen gestellfesten Gelenkpunkt 63 verstellbar. Im Seitengestell 44 sind Anschläge 60; 61 für eine Schwenkarmlage in An- (Anschlag 60) und Abstellungposition (Anschlag 61) vorgesehen. Durch eine geschickte Lage bzw. Anordnung des Zwischenrades 25 (Lage in Richtung Mitte Farbwalze 13) bleibt auch bei abgeschwenktem Reibzylinder 12.1 das Stirnrad 35 mit Freilauf 50 im Zahneingriff mit dem Zwischenrad 25. Hierzu ist vorzugsweise der Modul der Verzahnung vom Zwischenrad 25 und Stirnrad 35 mit Freilauf 50 angepasst (vorzugsweise m = 2) und der Einbauachsabstand um vorzugsweise 0,5 mm größer als der Verzahnungs-Nennachsabstand gewählt. Der in Fig. 17 dargestellte abschwenkbare Pleuelmechanismus 48 weist ein gegenüber einem festen Pleuel 69 um eine Drehachse 66 abschwenkbares Pleuel 70 auf. Am abschwenkbaren Pleuel 70 ist ein Gelenk 39 vorgesehen, zur Herstellung einer Verbindung mit einer das Lager 49 tragenden Lagerung des Reibzylinders 12.1. Das feste Pleuel 69 und das abschwenkbare Pleuel 70 sind um eine Kurbelachse 75 verdrehbar. Am festen Pleuel 69 ist ein Nutenstein 71 angeordnet. Der Nutenstein 71 ist mit einer Mutter 72 gesichert an einem Lager 73, z. B. Wälzlager 73 am Pleuel 70 gelagert. Nutenstein 71 und Kurbelachse 75 bilden einen Exzenter 76. Festes Pleuel 69 und abschwenkbares Pleuel 70 sind mittels Passschrauben 67 und Lagern 68, z. B. Gelenklagern 68 miteinander verbunden.
4. d) Identische bzw. baugleiche Quervereibgetriebe-Baugruppe 45 für alle Formate mit verschiedenen Umfängen bzw. verschiedenen Papierbahnbreiten, um das Farbwerk 08 universell in Verbindung mit Formzylindern 07 mit unterschiedlichen Durchmessern einsetzen zu können (Fig. 2, 3 und 7). Durch Beibehaltung eines festen Achsabstandes A von beispielsweise 240 mm zwischen den beiden Reibzylindern 12.1; 12.2 kann auch bei Verwendung von größeren Walzendurchmessern für große Papierbahnbreiten die gleiche Quervereibgetriebe-Baugruppe 45 eingesetzt werden. Lediglich der Schwenkarmabstand von Mitte Farbwalze 13 zu Mitte Reibzylinder 12.1; 12.2 muss hierzu wie in Fig. 7 am Beispiel einer doppelbreiten 4/2 Druckmaschine in Fig. 7 a) und einer dreifachbreiten 6/2 Druckmaschine in Fig. 7 b) angedeutet, wie in Fig. 7 c) dargestellt angepasst werden. Vorteilhafterweise gilt für 4/2 Druckmaschinen ein Reibzylinderdurchmesser von 185 mm und ein Farbübertragwalzendurchmesser von 150 mm. Vorteilhafterweise gilt es für 6/2 Druckmaschinen ein Reibzylinderdurchmesser von 196 mm und ein Farbübertragwalzendurchmesser von 170 mm, jedoch sind auch andere Durchmesser-Kombinationen denkbar. Aufgrund der unterschiedlichen Umfänge von beispielsweise min. 940 mm bis beispielsweise max. 1.156 mm ergeben sich wie in den Fig. 2 a) und 3 a) für maximalen Umfang und in den Fig. 2 b) und 3 b) für maximalen Umfang dargestellt verschiedene Einbau-Winkellagen für die Reibzylinder 12.1; 12.2 relativ zueinander. Diese unterschiedlichen Einbau-Winkellagen sind durch eine gegenüber der Vertikalen unterschiedlich geneigte Verbindungslinie der Reibzylinderachsen dargestellt. Der Achsabstand A von Reibzylinder 12.1 zu Reibzylinder 12.2 entspricht vorzugsweise A = 240 mm, wodurch sich im Druckwerk 04 unterschiedliche Einbau-Winkellagen von min. 10° bis max. 35° Grad ergeben. Die QuerverreibgetriebeBaugruppe 45 kann in diesem Bereich ohne pumpenbetriebene Ölumlaufschmierung betrieben werden. Alle notwendigen Getriebekomponenten werden durch eine vorhandene Ölsumpfschmierung versorgt. Lediglich der Freilauf 50 des Stirnrades 35 ist lebensdauerfettgeschmiert. Ebenso ist denkbar alle Lager lebensdauerfettgeschmiert auszuführen und die jeweiligen Verzahnungsgetriebe mit Spezialfett zu schmieren.

The inking unit 08 thus has the following properties:

1. a) Rotary drive only one of a plurality of Reibzylindern 12.1; 12.2 in printing operation to slip, wear and drive load by different effective diameter at soft rollers 11; 13 hired cylinders 06; 07 to reduce ( Fig. 4 and 9 ).
2. b) Rotatory positive drive of all distribution cylinders 12.1; 12.2 in setup mode contrary to the production direction, in order to allow inking unit washing or doctoring with a direction of rotation against printing operation ( Fig. 5 and 10 ). When squeegee / Inkwerkwaschen thereby, as in the Fig. 5 and 10 shown, a direction of rotation opposite to the production direction of rotation instead. The distribution cylinder 12.1; 12.2 are forcibly driven so as not to be brought to a standstill by a washing blade 10, whereby the washing result would not be satisfactory.
3. c) Abschwenkbarer distribution cylinder 12.1; 12.2 for maintenance purposes at standstill by means of pivotable connecting rod mechanism 48 ( Fig. 17 ) in order to improve the accessibility, for example during inking unit washing and / or die cylinder exchange ( Fig. 6 and 11 ). For exchanging the second, middle application roller 11 upward, it is necessary to move the friction cylinder 12.1, which is friction-driven in the printing operation, away from the forme cylinder 07 in pressure-off, that the distance between the two surfaces is greater than the diameter of the applicator roller 11 to be removed. This takes place exclusively when the printing machine is at a standstill. Swinging is a user-friendly solution that does not require disassembly of components. To create a development space for the middle application roller 11 is as in the Fig. 12 . 13 . 15 and 16 represented, the distribution cylinder 12.1 mounted in a pivot arm 59. The show Fig. 12 and 15 a swiveled position, and the Fig. 13 and 16 a pivoted-off position of the moisture-remover cylinder 12.1. The damp remover Friction cylinder 12.1 is on both sides, as in the Fig. 12 and 13 represented, in a bearing 49, preferably a cylindrical roller bearing 49 mounted with a joint calotte on the outer ring, which in turn are in pivotable, frame inside levers 59 which form the pivot arm 59. The FIGS. 15 and 16 each show an enlarged view of only the drive side. The joint bearings are required to compensate for a misalignment in one-sided swivel arm 59 on / off. As a result, no synchronization is necessary. The pivot points of the pivot arms 59 and the centers of the roller locks 15 of the ink roller 13 coincide ( Fig. 13c) ). Preferably, the pivot arms 59 are mounted around the roller locks 15 and adjustable by means of 62 setscrews and adjusting nuts 64 in their position with respect to a frame-fixed hinge point 63. In the side frame 44 are stops 60; 61 for a Schwenkarmlage in arrival (stop 60) and parking position (stop 61) provided. By a clever position or arrangement of the intermediate wheel 25 (position towards the center inking roller 13) remains even with pivoted-off friction cylinder 12.1, the spur gear 35 with freewheel 50 in meshing with the intermediate gear 25. For this purpose, preferably the module of the teeth of the intermediate gear 25 and spur gear 35th adapted with freewheel 50 (preferably m = 2) and the mounting axis distance selected by preferably 0.5 mm larger than the nominal tooth pitch. The in Fig. 17 shown pivotable connecting rod mechanism 48 has a relation to a fixed connecting rod 69 about a pivot axis 66 pivotable connecting rod 70. At the pivotable connecting rod 70, a hinge 39 is provided for establishing a connection with a bearing 49 supporting the bearing of the Reibzylinders 12.1. The fixed connecting rod 69 and the pivotable connecting rod 70 are rotatable about a crank axis 75. At the fixed connecting rod 69, a sliding block 71 is arranged. The sliding block 71 is secured with a nut 72 to a bearing 73, z. B. bearings 73 mounted on the connecting rod 70. T-nut 71 and crank shaft 75 form an eccentric 76. Fixed connecting rod 69 and pivotable connecting rod 70 are by means of fitting screws 67 and bearings 68, z. B. joint bearings 68 connected to each other.
4. d) Identical or structurally identical cross-gear unit assembly 45 for all formats with different perimeters or different paper web widths in order to use the inking unit 08 universally in conjunction with form cylinders 07 with different diameters ( Fig. 2, 3rd and 7 ). By maintaining a fixed center distance A of, for example, 240 mm between the two friction cylinders 12.1; 12.2, the same cross gear unit assembly 45 can be used even with larger roll diameters for large paper web widths. Only the Schwenkarmabstand from center ink roller 13 to center distribution cylinder 12.1; 12.2 must do this as in Fig. 7 using the example of a double width 4/2 press in Fig. 7 a) and a triple-width 6/2 press in Fig. 7b) indicated as in Fig. 7c) be adjusted shown. Advantageously, for 4/2 presses a Reibzylinderdurchmesser of 185 mm and a Farbübertragwalzendurchmesser of 150 mm. Advantageously, it applies to 6/2 presses a Reibzylinderdurchmesser of 196 mm and a Farbübertragwalzendurchmesser of 170 mm, but other diameter combinations are conceivable. Due to the different sizes of, for example, min. 940 mm to, for example, max. 1,156 mm arise as in the Fig. 2 a) and 3 a ) for maximum extent and in the Fig. 2 b) and 3 b ) for maximum extent shown different installation angular positions for the distribution cylinder 12.1; 12.2 relative to each other. These different installation angular positions are represented by a relation to the vertical differently inclined connecting line of the Reibzylinderachsen. The axial distance A of the distribution cylinder 12.1 to distribution cylinder 12.2 preferably corresponds to A = 240 mm, resulting in the printing unit 04 different installation angular positions of min. 10 ° to max. 35 ° degrees. The transverse sprocket assembly 45 can be operated in this area without pump-driven oil circulation lubrication. All necessary transmission components are supplied by an existing oil sump lubrication. Only the freewheel 50 of the spur gear 35 is lifetime-lubricated with grease. It is also conceivable to carry out all bearings life fat lubricated and to lubricate the respective gear transmission with special grease.

The gear 35 and spur gear 35 is substantially as in Fig. 18 represented by a spur gear 53, which is connected by means of the freewheel 50 with the clamping hub 51. The clamping hub 51 has a clamping screw 43 for clamping on the pin 29 of the distribution cylinder 12.1 ( FIGS. 15 and 16 ). A draw bolt 55 is by means of a bearing 40, z. B. Rolling bearing 40 mounted in a bush 54 in the interior of the spur gear 53. The bushing 54 ensures an axial alignment between the journal 29 of the friction cylinder 12. 1 or the clamping hub 51 and the tension bolt 55. A groove nut 56 holds the roller bearing 40 on the tension bolt 55. A bearing 52, z. B. bearings 52 and the freewheel 50 support the sleeve 54 radially from the spur gear 53 from.

The drive motor 18 of the or the distribution cylinder 12.1; 12.2 is not in positive drive connection with the forme cylinder 07th

At least the form cylinder 07 to be inked by the inking unit 08 has a different, preferably angle-position-controlled drive motor than the inking unit 08 driven by the drive motor 18.

Preferably, each of the forme cylinder 07 and each of the transfer cylinder 06 has its own angular position-controlled drive motor.

LIST OF REFERENCE NUMBERS

01

printing unit

02

Material web, train

03

Double printing

04

printing unit

05

Pressure point, double pressure point

06

Cylinder, printing cylinder, transfer cylinder

07

Cylinder, printing cylinder, form cylinder

08

Inking unit, roller inking unit

09

dampening

10

wash-up blades

11

Roller, applicator roll

12

Roller, distribution cylinder

13

Roller, ink roller, transfer roller

14

Roller, film roller

15

roller lock

16

Roller, ductor roller, dipping roller

17

paintbox

18

Drive motor, synchronous motor, asynchronous motor, servomotor

19

Gear, traversing gear, friction gear

20

Spur gears

21

transmission

22

Traversing drive, traversing gear

23

clutch

24

wave

25

idler

26

pinion

27

spur gear

28

intercept

29

spigot

30

casing

31

side frame

32

Bearings, radial bearings

33

slug

34

worm

35

Transmission, spur gear

36

wave

37

takeaway

38

pleuel

39

joint

40

Bearings, Rolling Bearings

41

casing

42

bracket

43

clamping screw

44

side frame

45

Querverreibgetriebe assembly

46

drive control

47

Sensors, encoders

48

Connecting rod mechanism

49

Bearings, cylindrical roller bearings

50

freewheel

51

Clamp hub, carrying

52

Bearings, Rolling Bearings

53

spur gear

54

Rifle

55

tension bolt

56

locknut

57

-

58

-

59

Swivel arm, lever

60

attack

61

attack

62

screw

63

Hinge point, frame-fixed

64

Adjusting nut (63)

65

-

66

axis of rotation

67

Passschraube

68

Bearings, spherical plain bearings

69

pleuel

70

Connecting rod, swiveling off

71

sliding block

72

mother

73

Bearings, Rolling Bearings

74

-

75

crank axle

76

eccentric

12.1

Roller, distribution cylinder, remotely damp, first

12.2

Distribution cylinder, close to the damp, second

A

Wheelbase

M

rotation speed

Claims (10)

1. Inking unit (08) of a printing press for inking a form cylinder (07), which has a compactor having at least one first friction cylinder (12.1), for its rotational drive the at least one friction cylinder (12.1) being driven by a drive motor (18), characterized in that between the first friction cylinder (12.1) and the drive motor (18) is arranged a freewheel (50), in that the first friction cylinder (12.1) is driven rotationally in a production direction of rotation only by means of friction with adjacent rolls (11; 13), in that the first friction cylinder (12.1) is driven rotationally contrary to the production direction of rotation by means of the drive motor (18) and in that the inking unit (08) has at least one second friction cylinder (12.2), which is additionally forcibly driven both in as well as contrary to the production direction of rotation by a drive motor (18).
2. Inking unit according to Claim 1, characterized in that the first friction cylinder (12.1) and the second friction cylinder (12.2) are driven contrary to the production direction by a common drive motor (18).
3. Inking unit according to Claim 1, characterized in that the drive motor (18) and an associated drive control (46) are designed in such a way that the drive motor (18) is operated in a controlled or regulated manner with respect to its performance and/or its torque, at least during a printing operation in print-on position of the printing press (08).
4. Inking unit according to Claim 1, characterized in that the first friction cylinder (12.1) is forcibly driven rotationally in the production direction of rotation only by means of friction and the second friction cylinder (12.2) is additionally forcibly driven rotationally in the production direction of rotation by the drive motor (18).
5. Inking unit according to Claim 1, characterized in that the friction cylinders (12.1; 12.2) are driven by means of a common traversing gear (22) with respect to a forced traversing movement.
6. Inking unit according to Claim 5, characterized in that the common traversing gear (22) is driven by the drive motor (18).
7. Inking unit according to Claim 1, characterized in that a first friction cylinder (12.1) driven rotationally in the production direction of rotation exclusively by friction is driven only by means of a transmission transforming the rotation of this friction cylinder (12.1) into an axial movement and without mechanical drive connection to a traversing gear (22) of another friction cylinder (12.2) with respect to a forced traversing movement.
8. Inking unit according to Claim 1, characterized in that the friction cylinder (12.1) driven exclusively by means of friction in the production direction of rotation, and for drive contrary to the production direction of rotation equipped with a mechanical drive connection transmitting a torque to a drive motor (18), is connected by means of a transmission (35) to the drive motor (18), which in the production direction of rotation has a freewheel, and contrary to the production direction of rotation has a torque coupling.
9. Inking unit according to Claim 1, characterized in that the drive motor (18) of the first friction cylinder (12.1) and/or of the second friction cylinder (12.2) has no positive drive connection to the form cylinder (07).
10. Inking unit according to Claim 1, characterized in that the form cylinder (07) to be inked by the inking unit (08) is driven by a drive motor different from the drive motor (18) of the first friction cylinder (12.1) and/or of the second friction cylinder (12.2).

Images