DE102006003005B3 - Press for flexographic printing has drive motor in form of synchronous motor with permanent magnet excitation - Google Patents

Abstract

The press has at least one rotary body (06, 07) in linear bearings in side mountings, and a motor stator moving with the linear bearing or the rotary body. The drive motor is in the form of a synchronous motor with permanent magnet excitation. The rotary body journals do not pass through the side mountings. The rotary body serves as a form cylinder. There are several form cylinders acting with satellite cylinders (05).

Description

The The invention relates to a flexographic printing machine according to the preamble of the claim 1.

The DE 101 03 631 A1 discloses a flexographic printing press with cylinders displaceable in linear bearings, each driven by a drive motor.

The DE 10 2004 001 467 A1 , the EP 1 082 225 B1 , the DE 101 23 138 A1 and the DE 102 51 977 A1 describe electric motors with permanent magnets.

Of the Invention is based on the object, a simple to produce, to create a compact flexographic printing press with high print quality.

The The object is achieved by the Characteristics of claim 1 solved.

The particular advantages of the invention are that an easily manufacturable or operable and / or spatially comparatively compact and / or a high quality printing enabling machine created becomes.

By the use of linear guides for the Form cylinders and anilox rollers of the printing units become an ideal installation position the cylinder or rollers with respect to possible cylinder vibrations reached. In addition, the cylinder bearings in linear guides realized low travel and therefore no sync spindle required. The elaborate Installation of three-ring bearings omitted.

By Use of a synchronous motor and / or a drive with permanent magnet excitation as a drive motor for the printing cylinder or the anilox roller gives the advantage that a particularly simple and yet strong drive for this body of revolution is created.

By Arrangement of a dryer such that the waste heat of the dryer a running over it Paper web dries again, which is required for drying Time or shortened required for drying way.

By the proposed coupling of the chambered doctor blade with the linear bearing the anilox roller results additionally The following advantage: It is advantageous in a hydraulic employment the squeegee system opposite a pneumatic adjustment that the hydraulic pressure column is not is compressible. The disadvantage, however, in this embodiment, that a quick shutdown of the doctor chamber from the anilox roller a necessary change of position the anilox roller, z. B. due to a paper tear, is not possible. By provided according to the invention coupling with the linear slide the anilox roll this disadvantage is avoided.

According to others embodiments the invention it is possible with variable section lengths too Print, which is a particularly economical way the operation of a flexographic printing machine.

According to one Another aspect of the invention is proposed, the surface of a Vacuum anilox roller before entering the chambered doctor blade; hereby In particular, the print quality of the machine can be improved and pollution is reduced.

According to one Another aspect of the invention, the possibility is created in a simple manner to allow the printing of different paper web widths.

embodiments The invention is illustrated in the drawings and will be described below described in more detail.

It demonstrate:

1 a schematic representation of a flexographic printing press with two adjacent printing towers, each with two superposed satellite printing units;

2 a printing tower of a flexographic printing machine according to 1 ;

3 a longitudinal section through a bearing unit of a cylinder of a printing unit of a flexographic printing machine;

4 a cross section through the storage unit according to 3 :

5 a detail from 3 in an enlarged view;

6 a drive motor of a cylinder or a roller of a flexographic printing press designed as a synchronous motor and / or as a permanent-magnet excited motor;

7 another embodiment of a drive motor;

8th another embodiment of a drive motor;

9 another embodiment of a drive motor;

10 another embodiment of a drive motor;

11 a side view of a forme cylinder with a linear bearing;

12 a plan view of a mechanical coupling of the linear bearing of a chamber doctor blade with the linear bearing of an anilox roller in the salaried state of the chambered doctor blade;

13 a plan view accordingly 12 , but in the parked state of the chambered doctor blade;

14 the coupling between the anilox roller and chamber doctor blade in the salaried state in a view perpendicular to that according to FIG 12 ;

15 the coupling according to 14, but in the parked state;

16 a plan view of a cylinder group consisting of satellite cylinder, forme cylinder and chamber doctor blade;

17 a side view of a flexographic printing unit in a first state of setting a zero position;

18 a side view of the flexographic printing according to 14 in a second state of setting a zero position;

19 a side view of another embodiment of a satellite printing unit with horizontal parallel linear guides;

20 a side view of another embodiment of a satellite printing unit with vertical lower linear guides;

21 a top view of a mechanical coupling of the linear bearing of the chamber doctor blade with the linear bearing of the anilox roller in the case of the embodiment according to 20 ;

22 a side view of another embodiment of a satellite printing unit with eight cylinders form;

23 a further embodiment of a linear bearing with two stop wedges for an anilox roller for a satellite printing unit according to 22 ;

24 a side view of another embodiment of a satellite printing unit that allows variable section lengths;

25 an illustration of the printing process using the satellite printing unit after 24 ;

26 a folding apparatus for use in a flexographic printing machine in a side view;

27 a second embodiment of a folding apparatus for use in a flexographic printing machine in a side view;

28 a schematic representation of a cutting cylinder pair of a folder after 26 or 27 in cross-section;

29 a second embodiment of a cutting cylinder pair of a folder after 26 or 27 in cross-section;

30 a side view of another embodiment of a satellite printing unit with suction devices for the anilox rollers;

31 an enlarged side view of an anilox roller after 30 with suction device;

32 an enlarged plan view of an anilox roller after 30 with suction device;

33 a schematic view of the four printing plates of a forme cylinder, which cooperate with register stops;

34 a schematic representation accordingly 33 , but in the case of paper web narrowing.

First, it will open 1 and 2 Referenced. An otherwise not shown flexographic printing machine comprises several, for example, two adjacent printing towers 01 of which each one has several, in particular two superimposed pressure units 03 , in particular satellite printing units 03 comprises, through which printing material webs 02 , especially paper webs 02 for two-sided, multi-color printing are performed. The printing towers 01 can be arranged on a machine platform, not shown, and below the pedestal not shown reel changers can be arranged, which the printing towers 01 with the paper webs 02 Food. The printing towers 01 be from the paper webs 02 in the transport direction from bottom to top. Printed, from the printing towers 01 led out paper webs 02 can zusam together in a superstructure of the printing press, not shown mengeführt and one or more processing stations such as a cutting station and one or more post-processing stations such as a folding unit 123 , see. also 26 be supplied.

Each satellite printing unit 03 includes a counter-pressure cylinder 05 serving central cylinder 05 namely the satellite cylinder 05 , as well as several, preferably at least four, in the case of the embodiment exactly four on the satellite cylinder 05 arranged printing units 04 , Every printing unit 04 is designed for high pressure, especially for flexographic printing. The general structure and functioning of flexographic printing units 04 is the general state of the art, so that it does not have to be discussed in detail. In the highly schematic representation according to 1 and 2 For clarity, therefore, only the two cylinders 06 ; 07 namely the one at the satellite cylinder 05 adjoining and with this a pressure nip forming cylinder shape 06 and those on the forme cylinder 06 adjacent anilox roller 07 (component 07 ), as well as the anilox roller 07 with ink feeding component 08 , z. B. chambered scraper 08 sketched schematically.

The embodiment according to 2 differs from the embodiment according to 1 essentially only by the respectively slightly different arrangement of the printing units 04 at the satellite cylinder 05 ,

The flexographic printing machine is designed, for example, for newspaper printing. The width of the machine is, in the axial direction of the cylinder 05 ; 06 ; 07 seen, such that the form cylinder 06 in the axial direction as a print image 29 have at least two, preferably four newspaper pages. The diameter of the form cylinder 06 is preferably chosen so that the forme cylinder 06 in the circumferential direction as a print image 29 have four newspaper pages. In particular, the bale of the forme cylinder 06 have a circumference of 1,100 mm to 1,300 mm and a length of 1,400 mm to 1,800 mm.

Preferably, the form cylinder wear 06 in the axial direction four (not shown here) flexographic printing plates side by side and in the circumferential direction two flexographic printing plates behind the other.

The diameter of the satellite cylinder 05 is preferably an integer multiple, in particular a triple of the diameter of the associated form cylinder 06 ; however, it may also be advantageous to use the satellite cylinder 05 so dimensioned that its diameter in particular a 2.5 times the diameter of the associated form cylinder 06 is. In another aspect, it is advantageous to have the circumference of the satellite cylinder 05 be dimensioned so that it corresponds to an integer multiple of the section length of a printed product manufactured with the flexographic printing machine.

The form cylinder 06 , the anilox roller 07 and the chambered scraper 08 of every printing unit 04 are each guided so that they are connected to the satellite cylinder 05 adjustable and can be switched off from this. For this purpose, the form cylinder 06 , the anilox rollers 07 and the chamber knives 08 each in storage units 14 stored, cf. 2 , which, in addition to a rotary bearing, each also a linear bearing 15 as will be explained in detail below. Preferably, each form cylinder 06 , every anilox roller 07 and every chamber doctor 08 each with its own linear bearing 15 assigned. The storage units 14 or linear bearings 15 the form cylinder 06 and the anilox rolls 07 on the one hand and the chamber doctor blades on the other 08 On the other hand, constructively in each case can be designed differently in each case.

Furthermore, preferably all cylinders 05 ; 06 ; 07 , ie in particular the satellite cylinder 05 , the form cylinder 06 and the anilox rolls 07 each of their own, in 1 and 2 not shown drive motors 121 driven, which in particular each angular position-controlled electric motors 121 , preferably a synchronous motor 121 and / or a drive motor 121 can act with permanent magnet excitation. A detailed description of the drive motors preferably used here 121 follow below.

The following are with reference to 3 to 5 in particular for storage and management of the form cylinder 06 and the anilox rolls 07 usable storage units 14 or linear bearings 15 in terms of their basic structure described in more detail:
3 and 4 show a preferably based on linear trajectories bearing unit 14 in the schematic longitudinal and cross-section. The bearing unit which integrates the on / off mechanism 14 points next to a warehouse 71 , z. B. radial bearings 71 , For example, a cylindrical roller bearing 71 , for rotational storage of the cylinder 06 ; 07 bearing means 72 ; 73 or bearing elements 72 ; 73 for a radial movement of the cylinder 06 ; 07 for printing on or off printing. For this purpose, the storage unit 14 (after mounting the bearing unit 14 fixed to the frame) carrier-resistant bearing elements 72 as well as against these movable bearing elements 73 on. The carrier-fixed and movable bearing elements 72 ; 73 are as cooperating linear elements 72 ; 73 and together with corresponding sliding surfaces or intermediate rolling elements as a whole linear guide 70 , z. B. linear bearings 70 educated. The linear elements 72 ; 73 Take this in pairs radial bearings 71 receiving storage block 74 , z. B. slide 74 between themselves. bearing block 74 and the movable bearing elements 73 can also be made in one piece. The carrier-fixed bearing elements 72 are on a carrier 76 arranged, which in total with the side frame 11 ; 12 a printing tower 01 is connected or is. The carrier 76 is for example as a carrier plate 76 executed, which, for example, at least on a drive side a recess 77 for the penetration of a shaft 78 , z. B. drive shaft 78 a pin 63 ; 64 a cylinder 06 ; 07 having. Also the side frame 11 ; 12 on the drive side preferably has a recess or an opening for a drive shaft 78 on. On the opposite side of the drive side does not necessarily have a recess 77 or a recess in the side frame 12 ; 11 be provided.

Preferably, a length of the linear bearing 70 , In particular, at least one length of the frame-fixed in the assembled state bearing means 72 of the linear bearing 70 , considered in the direction of S direction smaller than a diameter of the associated cylinder 06 ; 07 ,

The coupling of the cylinder 06 ; 07 or the storage block 74 on a drive side of the printing tower 01 to a drive, for. B. to a drive motor 121 takes place as in 3 for example, shown on the shaft 78 , which at the end near the cylinder one end of the pin 63 ; 64 includes and for example via a clamping device 66 with the pin 63 ; 64 torsionally rigid is connected. The clamping device 66 is here for example as z. T. slotted hollow shaft end formed, which the journal end (pin 63 ; 64 ) and is to be pulled together by means of a screw in such a way that a frictional rotationally fixed connection between the journal end (pin 63 ; 64 ) and hollow shaft inner surface can be produced. The coupling can also in other ways, for. B. in the circumferential direction having a positive connection, be executed. The wave 78 is through a recess in the side frame 11 ; 12 which is sufficiently large for the movement of the shaft 78 together with the storage block 74 is measured and which z. B. is formed in the manner of a slot. As a protection against dirt, a cover 69 be provided with a slot covering the collar, which z. B. with the bearing block 74 but not with the wave 78 connected is.

To the cylinder-distal end of the shaft 78 is like in 3 illustrated one of possibly more serially arranged coupling 148 , in particular multi-plate clutch 148 through a non-rotatable connection 75 , z. B. a clamping element 75 , can be coupled. In another embodiment not shown is directly a transmission with drive motor 121 without angular and / or offset compensating coupling 148 to the wave 78 coupled. In this embodiment, the drive motor 121 not frame-fixed, but arranged cylinder-tight and is with the cylinder 06 ; 07 moved.

On a drive side opposite side of the cylinder 06 ; 07 , in particular of the form cylinder 06 executed cylinder 06 , is the cone 64 preferably with a device for axially moving the cylinder 06 , ie coupled to a side register drive, not shown. The example of the type 3 with the pin 63 ; 64 connected wave 78 is this about a camp, z. B. thrust bearing connected to an axial drive.

The training of linear bearings 70 in such a way that the cooperating bearing elements 72 ; 73 both on the assembly storage unit 14 - and not a part of the side frame 11 ; 12 of the printing tower 01 or the printing unit 03 - Are provided, allows pre-assembly and pre-adjustment or adjustment of the bearing voltage. The advantageous arrangement of the two the bearing block 74 encompassing linear bearings 70 allows a backlash-free adjustment, as the two linear bearings 70 are opposed in such a way that the bearing preload and the bearing forces an essential component in a direction perpendicular to the axis of rotation of the cylinder 06 ; 07 learn or record. The linear bearings 70 are thus adjustable in the direction to which it is at play-free positions of the cylinder 06 ; 07 also arrives.

As the cylinder 06 ; 07 including pins 63 ; 64 and storage unit 14 the side frame 11 ; 12 not penetrate, these are already pre-assembled and the bearings (radial bearings 71 as well as linear bearings 70 ) pre-set or correctly preloaded as module cylinder unit 80 in the printing unit 01 used. The term "non-penetration" and the above definition with respect to the clear width is to be understood in a broader sense to mean that, at least in the region of the intended end position, the cylinder 06 ; 07 and at least on a continuous path from a frame edge to the location of the end position such a "non-penetration" is present, so that the cylinder unit 80 from an open, between the two frontal side frames 11 ; 12 lying side without tilting, ie brought in a position with the frame plane perpendicular axis of rotation to the end position and there are arranged between the two frame inner walls, in particular attached to the frame inner walls, can. This is z. Example, even if possible on the inside while Angussteile or other surveys are provided, a named continuous assembly path is provided, however.

The storage units 14 are in the way on the inner walls of the side frames 11 ; 12 arranged that the cylinder 06 ; 07 , in particular their storage units 14 on cylinder side by the side frame 11 ; 12 are supported, which has static and mounting advantages.

In the 3 and 4 recognizable linear bearings 70 ( 72 ; 73 ) thus each have pairings of corresponding cooperating bearing means 72 and 73 or their guiding or active surfaces, as sliding surfaces (not shown) formed or arranged therebetween rolling elements 65 , on. As in 5 shown, in a preferred embodiment, at least one of the two, advantageous both linear bearings 70 a storage unit 14 executed such that the two corresponding bearing means 72 and 73 in each case at least two guide surfaces 72.1 ; 72.2 ; 73.1 ; 73.2 have, which in two mutually inclined planes E1; E2 are lying. The two guide surfaces 72.1 ; 72.2 ; 73.1 ; 73.2 (or their planes E1, E2) of the same storage means 72 ; 73 are z. B. V-shaped to each other, for. B. with an intermediate angle between 30 to 60 °, in particular between 40 and 50 °, inclined. The two guide surfaces 73.1 ; 73.2 ; 72.1 ; 72.2 of the cooperating bearing means 73 ; 72 are complementary in shape. At least one of the two pairings of cooperating guide surfaces 72.1 ; 73.1 respectively. 72.2 ; 73.2 is parallel to a plane E1 or E2, which has a component not equal to zero in the radial direction of the cylinder axis and thereby the degree of freedom of movement in a purely axial direction of the cylinder 06 ; 07 in derogation. Preferably, both pairings lie to planes E1; E2, both having a non-zero component in the radial direction of the cylinder axis, but in reverse tilt against the cylinder axis and thereby the degree of freedom of movement in both axial directions of the cylinder 06 ; 07 prevention. A section line of the two planes E1; E2 is parallel to the direction S

Is, as in 3 to recognize the storage block 74 between the two, two pairs of co-operating guide surfaces 72.1 ; 73.1 and 72.2 ; 73.2 having linear bearings 70 bordered, in particular biased with a bias, so the bearing block 74 only a single degree of freedom of movement along the direction of adjustment S on.

The inclined active or guide surfaces 72.1 ; 72.2 ; 73.1 ; 73.2 are arranged so that they a relative movement of the bearing parts of the linear bearing 70 in the axial direction of the cylinder 06 ; 07 counteract, ie the camp is "tied off" in the axial direction.

Preferably, the linear bearings 70 both a cylinder 06 ; 07 frontally assigned storage units 14 two mutually arranged pairs of interacting active or guide surfaces 72.1 ; 72.2 ; 73.1 ; 73.2 on. In this case, however, advantageously has at least one of the two radial bearings 71 the two storage units 14 a slight bearing clearance .DELTA.71 in the axial direction.

In 3 and 4 have the guide surfaces 72.1 ; 72.2 the frame-fixed storage means 72 the linear guide 70 in the cone 63 ; 64 facing half space. The frame-fixed storage means 72 here enclose the storage block arranged between them 74 , The frame-fixed guide surfaces 72.1 ; 72.2 the two linear bearings 70 thus partially cover the guide surfaces 73.1 ; 73.2 of the storage block 74 with respect to an axial direction of the cylinder 06 ; 07 ,

For correct placement of the storage units 14 or cylinder units 80 including storage unit 14 , can installation aids 89 , z. B. dowel pins 89 in the side frame 11 ; 12 be provided, to which the storage unit 14 the fully assembled cylinder unit 80 is aligned before passing through releasable holding means 91 , z. B. screws 91 , or even cohesively by welding with the side frame 11 ; 12 get connected. For those already before insertion into the printing unit 03 to be made and / or readjusted after insertion adjustment of the bearing preload in the linear bearings 70 can appropriate means 92 , z. B. clamping screws 92 be provided ( 3 ). Preferably, the storage unit 14 - At least to the cylinder side - through a cover 94 largely protected against contamination or even encapsulated executed as a unit.

In 3 is schematically the cylinder 06 ; 07 with cones 63 ; 64 and a preassembled storage unit 14 designated. This assembly can thus be preassembled between the side frames 11 ; 12 the printing unit 03 or the printing tower 01 easy to install and attached to designated locations. Preferably for a modular design are the storage units 14 for form cylinder 06 and anilox roller 07 - if necessary, except for the permitted operational size of the travel - identical design. The pre-assembled design allows the effective inner surface of the radial bearing 71 and the outer effective lateral surface of the pin 63 ; 64 be cylindrical instead of tapered, as both the mounting of the bearing unit 14 on the cone 63 ; 64 as well as the setting of the bearing clearance outside the printing unit 03 can be done. The storage unit 14 can be shrunk, for example.

The assembly unit which can be mounted as a whole (storage unit 14 ) Is advantageous in the manner of an optionally partially open housing of z. B. the carrier 76 . and / or z. B. a frame (in 4 without reference z. B. the four the storage unit 14 to all four sides outwards bounding plates) and / or z. B. the cover 94 ( 3 ). Within this housing or this frame are the radial bearing 71 bearing block 74 , the linear guides 70 and in an advantageous embodiment, for. B. the actuator 82 or the actuators 82 accommodated.

The frame-fixed bearing elements 72 are arranged substantially parallel to one another and define the actuating direction S ( 4 ).

Pressure on is done by moving the bearing block 74 towards the pressure point by means of a by at least one actuator 82 on the storage block 74 applied force F, in particular by a force-controlled or via a force defined actuator 82 , By means of which for employment a defined or definable force F in pressure-on direction to the bearing block 74 can be brought ( 4 ). The decisive for the color transfer and thus the print quality, among other line force in the Nippstellen is therefore not by a travel, but by the balance of power between the force F and between the cylinders 06 ; 07 resulting line force F _L and the resulting equilibrium defined. In a not specifically illustrated embodiment are cylinders 06 ; 07 in pairs put together by the bearing block 74 with the corresponding adjusted force F via the actuator (s) 82 is charged.

To a pressure point facing side, the storage unit 14 a portable device 79 , z. B. a stop 79 on, which limits the travel to the pressure point out. The stop 79 is locatable in such a way that the stop surface effective as a stop 83 along the direction of adjustment S at least in a range is variable. It is thus in an advantageous embodiment, an adjusting device (adjustable stop 79 ) provided by means of which the position of a pressure near the end position of the bearing block 74 is adjustable. For Wegbegrenzung / adjustment serves z. B. a wedge drive described below. Placing the stop 79 can always be used manually or via an actuator ( 84 , see below) 84 respectively. Next is an advantageous embodiment in 3 and 4 not shown holding or clamping means provided by means of which the stop 79 set in the desired location. Next is at least one spring-acting element 81 , z. B. spring element 81 , provided, which on the storage block 74 a force F _R from the stop 79 in one direction from the stop surface 83 away. Ie. the spring element 81 causes a pressure-off in the event that the bearing block 74 is not prevented from moving in any other way. Pressure on is done by moving the bearing block 74 towards the stop 79 by at least one actor 82 , In particular a force-controlled actuator 82 , By means of which for employment either a defined or definable force F in pressure-on direction to the bearing block 74 can be brought. Is this force F greater than the restoring force F _{R of} the spring elements 81 , so takes place with appropriate spatial training a hiring of the cylinder 06 ; 07 to the adjacent cylinder 06 ; 07 and / or hiring the storage block 74 to the stop 79 ,

Ideally, the applied force F, the restoring force F _R and the position of the stop 79 chosen so that between stop 79 and the abutment surface of the bearing block 74 no significant force .DELTA.F is transmitted in the set position, for example, | ΔF | <0.1 * (F - F _R ), in particular | ΔF | <0.05 * (F - F _R ), ideally | ΔF | ≈ 0. In this case, the contact force between the cylinders 06 ; 07 much above that by the actor 82 applied force F determined. The decisive for the color transfer and thus the print quality, among other things, line force in the Nippstellen is therefore not primarily by a travel, but with quasi-free stop 79 defined by the force F and the resulting equilibrium. Basically, after finding the basic setting with the appropriate forces F would be a removal of the stop 79 or a corresponding, effective only during the basic setting fixation conceivable.

The actor 82 can basically as any, a defined force F applying actuator 82 be executed. The actuator is advantageous 82 as actuatable by pressure medium actuating means 82 , in particular as a piston movable by a fluid 82 executed. Advantageous in terms of possible tilting is the arrangement of several, here two, such actuators 82 , As fluid preferably comes because of their incompressibility a liquid, for. As oil or water, used.

The as a whole mountable storage unit 14 has two simultaneously operable, acting in the same direction and with their force application points on the bearing block 74 in a direction perpendicular to the cylinder axis spaced actuators 82 to the print on position.

To operate here as a hydraulic piston 82 executed actuators 82 is in the storage unit 14 a controllable valve 93 intended. This is performed, for example, electronically controlled and provides a hydraulic piston in a position without pressure or at least to a lower pressure level, while in another position of the force F conditional pressure P is applied. In addition, a non-designated leakage line is provided here for safety.

In order to avoid excessive stopping / stopping distances and still to secure track winders, it can be found on the side of the bearing block away from the pressure side 74 a Wegbegrenzung by a mobile, force-limited stop 88 as overload protection 88 , z. B. spring element 88 be provided, which in the operational pressure-Ab, ie the piston 82 are relieved and / or retracted, although as a stop 88 for the storage block 74 serve in pressure-off position, in the case of a railway winder or other excessive forces from the pressure point but gives way and gives a greater way free. A spring force of this overload protection 88 is therefore chosen larger than the sum of the forces from the spring elements 81 , When operational on / off is therefore only a very short travel, z. B. only 1 to 3 mm, providable.

The stop 79 is in the illustrated embodiment ( 4 ) as transversely to the direction of adjustment S movable wedge 79 executed, wherein when moving the same position of the respective effective stop surface 83 varies along the direction of adjustment S. The wedge 79 is supported, for example, on a carrier-resistant stop 96 from.

The one here as a wedge 79 executed stop 79 is by an actor 84 , For example, a pressure medium actuatable actuating means 84 such as a pressure medium actuated piston 84 in a working cylinder with (double-acting) piston via a z. B. as a piston rod 85 executed transmission element 85 or by an electric motor via a transmission element designed as a threaded spindle 85 , movable. This actor 84 may be either in both directions effective or, as shown here, designed as a one-way actuator, which when activated against a return spring 86 is working. The force of the return spring 86 is for the above reasons (largely force-free stop 79 ) so weak that the wedge 79 is kept in its correct position only against gravity or vibration forces.

Basically, the stop 79 in another way (eg, as a plunger adjustable and fixable to the setting direction S, etc.) in such a way that it can be varied in the adjustment direction S, and - at least during the adjustment process - fixable stop surface 83 for the movement of the storage block 74 forms in the direction of the pressure point. In a non-illustrated embodiment, a place of the stop takes place 79 For example, directly parallel to the direction of adjustment S by a drive means, for example, a pressure medium actuated cylinder with (double-acting) piston or an electric motor.

The following are with reference to 6 to 10 in particular for driving a rotating body 05 ; 06 ; 07 , in particular a cylinder 05 ; 06 ; 07 So the satellite cylinder 05 , the form cylinder 06 and the anilox rolls 07 the flexographic printing machine used drive motors 121 explained in more detail, which in each case in particular each an angular position-controlled electric motor 121 , preferably a synchronous motor 121 and / or a drive motor 121 can act with permanent magnet excitation.

6 shows an embodiment of a drive by means of a synchronous motor 121 and / or as a permanent magnet excited motor 121 trained drive motor 121 with a rotor (runner) 266 , The synchronous motor 121 is z. B. as field weakenable synchronous motor 121 educated. The field weakening of the synchronous motor 121 is for example provided up to a ratio of 1:10. He points z. B. six poles and has an electrical stimulation.

The as a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 preferably has a permanent excitation, that is, it is designed with permanent magnet excitation. The rotor 266 or runner 266 of the synchronous motor 121 has poles of permanent magnets 267 on. He points z. For example, a steady state torque in the range of 100 Nm to 200 Nm. Advantageously, the synchronous motor 121 a maximum torque in the range of 600 to 800 Nm, in particular about 700 Nm, on. The permanent magnets 267 preferably have rare earth materials.

The as a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 has z. B. a theoretical idling speed in the range of 500 U / min to 600 U / min.

As a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 is z. B. upstream a frequency converter for speed control.

Preferably is on as a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 a rotation angle sensor 274 intended.

It is advantageous as a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 a cooling device, in particular a fan or a liquid coolant circuit provided.

Additionally, it can be used as a synchronous motor 121 and / or permanent-magnet motor 121 trained engine 121 a braking device may be provided. The motor 121 but can also be used in generator mode as a braking device.

A rotation axis of a rotation angle sensor 274 can coaxial with the axis of rotation of the rotor 266 of the motor 121 be arranged.

The stator 269 has windings 268 for generating magnetic fields by electrical energy.

7 shows an embodiment of the drive of a roller or a cylinder 06 ; 07 , in particular a forme cylinder 06 or an anilox roller 07 , with storage unit 14 with one as a synchronous motor 121 and / or permanent-magnet motor 121 trained drive motor 121 ie with one on the rotor 266 formed section of permanent magnets. The stator 269 is here, for example, directly on the moving part of the storage unit 14 , z. B. on the movable storage block 74 attached and movable together with this. To support the here permanently excited synchronous motor 121 can be a guide 271 be provided, on which the engine 121 slides.

In an advantageous variant, the drive motor 121 to the rotary drive as an external rotor motor, in particular also with permanent magnets 267 on the now external rotor 266 , educated ( 8th ). The rotor 266 is now z. B. with the jacket body of the cylinder 06 ; 07 connected or formed by this. The windings 268 of the stator 269 be for example by electrical lines 272 energized. The rotation angle sensor 274 can in principle at different place rotationally fixed with the cylinder 06 ; 07 and / or the rotor 266 be connected, z. B. also on the other end face of the cylinder 06 ; 07 , and has z. B. a signal line 276 for drive control. In the example he is with the rotor 266 connected. stator 269 and rotor 266 are over camp 277 , here radial bearings 277 , supported on each other. This eliminates the radial bearings in the bearing block 74 of the 3 , The stator 269 is non-rotatable with the bearing block 74 connected and linearly movable together with this.

9 shows an advantageous variant, in particular in the case of a forme cylinder 06 trained cylinder 06 also an axial movement by the drive motor 121 should be done. For this purpose, the rotor 266 another way with permanent magnets 278 occupied section. The poles of the permanent magnets 278 alternate here, for example, in the axial direction. In contrast, z. As the poles in the provided for the rotary drive portion of permanent magnets 267 z. B. in the circumferential direction from (also in 8th ). The axial movement section of permanent magnets 278 are opposite of the windings 268 different windings 279 arranged, which have their own signal lines 281 can be controlled by a machine control for the purpose of page register setting. Camps 277 are here, for example, as an axial relative movement enabling roller bearings 277 educated.

10 shows an advantageous variant, wherein the cylinder 06 ; 07 in the region of its lateral surface or slightly below the permanent magnets 267 in the circumferential direction. The windings 268 having stator 269 is fixed to the frame outside the cylinder 06 ; 07 (or a roller), but within the two side frames 12 ; 11 arranged. The windings 268 carrying stator 269 this can be around the entire circumference of the cylinder 06 ; 07 rich or just over an angular segment ( 10 , below). The permanent magnets 267 but also on a cone 63 ; 64 or a frontal taper of the cylinder 06 ; 07 be arranged.

11 shows a schematic side view of a forme cylinder 06 with a linear bearing 15 how they are already related in terms of their basic structure 3 to 5 has been described. The stop 79 , here as a stopwedge 79 is designed here drivingly with a servomotor 33 connected and the position of the stop wedge 79 can by means of one with the servomotor 33 cooperating sensor 32 , z. B. a potentiometer 32 be monitored or controlled.

It will be up again 2 Referenced. As stated, each form cylinder 06 , every anilox roller 07 and every chamber doctor 08 each with its own linear bearing 15 the type described above and at least the satellite cylinders 05 , the form cylinders 06 and the anilox rollers 07 one drive motor each 121 associated with the type explained above.

About his linear bearing 15 is every form cylinder 06 to the assigned satellite cylinder 05 fine adjustable adjustable, each anilox roller 07 is about their linear bearing 15 to the assigned form cylinder 06 finely adjustable and each chambered scraper 08 is about their linear bearing 15 to its associated anilox roller 07 preferably adjustable by pressure.

The arrangement of the form cylinder 06 on the circumference of the respective satellite cylinder 05 is such that between each contact line, the forme cylinder 06 with the satellite cylinder 05 forms the same distance, or, in other words, the form cylinder 06 are equidistant on the circumference of the satellite cylinder 05 distributed.

The form cylinder 06 are, as in the case of the embodiment after 1 , in terms of of the respective satellite cylinder 05 arranged so that in each case two forme cylinder 06 to be diametrically opposed; in other words, the axes of rotation of satellite cylinders 05 and two associated with this form cylinders 06 lie on a common line.

The anilox rolls 07 are relative to the form cylinders 06 each arranged so that the axis of rotation of an anilox roller 07 , the axis of rotation of the associated forme cylinder 06 and the axis of rotation of the associated satellite cylinder 05 each lie on a common line. This ensures that at a delivery of the forme cylinder 06 to the satellite cylinder 05 due to the selected position of the cylinder 05 ; 06 to each other, the anilox roller 07 can now be moved synchronously with the same delivery value as the forme cylinder 06 , so that is between the anilox roller 07 and form cylinder 06 set pressure bias does not change.

Furthermore, it is on a linear bearing 15 mounted and the associated anilox roller 07 pressure-controlled chambered doctor 08 with the linear bearing 15 the anilox roller 07 so coupled that the chambered scraper 08 every change of position of the anilox roller 07 without changing the pressure-on position inevitably follows. In principle, such a function can also be solved in terms of control technology, but the following will be described below with reference to FIG 12 and 13 explained mechanical solution chosen:
12 shows a plan view of a mechanical coupling of the linear bearing 15 the chambered doctor 08 with the linear bearing 15 the anilox roller 07 in the salaried state of the chambered doctor blade 08 to the anilox roller 07 , while 13 shows the parked state. The anilox roller 07 is with her thong 64 in linear bearings 15 ie in the carriage 74 the linear bearing 15 stored, in turn, on the linear guide 16 the linear bearing 15 the anilox roller 07 is guided longitudinally displaceable. The chambered doctor 08 is over a traverse attached to it 17 and a holder 18 in a linear bearing 15 ie in the carriage 74 this linear bearing 15 held in turn on the linear guide 16 the linear bearing 15 the chambered doctor 08 is guided longitudinally displaceable. The sled 74 the linear bearing 15 the chambered doctor 08 is with the sled 74 the linear bearing 15 the anilox roller 07 distance variable connected, which can be designed constructively as follows:
An actor 19 , which in particular can be druckmittelbetätigbar and in the case of the embodiment, a force-controlled cylinder-piston device 19 may be between chambered scraper 08 or between the carriages 74 the linear bearing 15 the chambered doctor 08 and the sled 74 the linear bearing 15 the anilox roller 07 effective. This is a cylinder 21 to which a working fluid can be supplied, with the chambered doctor blade 08 or their sled 74 connected and one in the cylinder 21 slidably guided piston 22 is about his piston rod 23 with the sledge 74 the anilox roller 07 connected. About one in the cylinder 21 arranged return spring 24 is the chambered scraper 08 biased in their parked position, cf. 13 , By supplying working fluid into the cylinder 21 becomes the chambered scraper 08 with the desired pressure to the anilox roller 07 against the pressure of the return spring 24 employed, cf. 12 , Due to the compound of anilox roller 07 and chambered scraper 08 by means of the actuator 19 follows the chamber doctor 08 every movement of the anilox roller 07 inevitably, and without the contact pressure between chambered doctor blade 08 and anilox roller 07 would change. Due to the coupling thus the pressure-controlled pressure-on position of the chambered doctor blade 08 maintained.

14 and 15 show in a representation corresponding to those of 11 the coupling between anilox roller 07 and chambered scraper 08 in a view perpendicular to that according to 12 respectively. 13 , In the illustration according to 15 is that of the anilox roller 07 parked chambered doctor 08 swung out of its functional position to prepare a knife change.

It should be noted that the principle of the above-described solution of the coupling of anilox roller 07 and chambered scraper 08 , as well as related to 21 explained principle, also advantageous in other printing units 04 as flexographic printing units 04 or applicable to other web-fed rotary printing presses as flexographic printing machines and in particular not to the coupling of anilox roll 07 and chambered scraper 08 is limited. Rather, in the same way and with advantage also a coupling of other components 07 ; 08 possible, especially if both components 07 ; 08 to be moved simultaneously or synchronously or a particular pressure-controlled pressure-on position between these components 07 ; 08 should be maintained.

The following is the basic setting or zero setting of linear bearings 15 explained. For setting a linear bearing 15 is preferably the forme cylinder 06 without printing plates 27 or with printing plates 27 , z. B flexographic printing plates 27 occupied with a defined thickness. The stopwedge 79 of the linear bearing 70 is retracted and the linear bearing 70 is against suitable attacks such. B. lateral surface of the impression cylinder 05 or measuring rings or frame-fixed stops z. B. hydraulically employed. In this zero position, the stop wedge 79 retracted and it is preferably a feedback of the position of the stop wedge 79 and / or its associated drive (Electric motor 121 ) to a control device. From this zero position of the stop key 79 and thus the forme cylinder 06 and / or anilox roller 07 becomes the stop wedge 79 retracted again a predetermined path, whereby the contact pressure when adjusting the cylinder 06 or the anilox roller 07 is determined.

In particular, a zero adjustment of the linear bearings 15 as follows, cf. also 16 to 18 :
16 shows a schematic view of a cylinder group consisting of satellite cylinder 05 , Forme cylinder 06 and anilox roller 07 , The form cylinder 06 has at its periphery a pressure plate 27 on, which is a carrier material 28 and the print image 29 includes. At the front sides of the forme cylinder 06 are measuring rings 31 appropriate. How out 17 and 18 becomes clear, are both the forme cylinder 06 as well as the anilox roller 07 each in a linear bearing 15 stored the type described above. The stopwedge 79 the respective linear bearing 15 is by means of a servomotor 33 adjustable and the position of the stopwedge 79 can by means of a servomotor 33 assigned potentiometer 32 be monitored.

For employment of the forme cylinder 06 to the satellite cylinder 05 First, the stop wedge 79 the linear bearing 15 of the forme cylinder 06 extended until the potentiometer 32 on the servomotor 33 has reached the maximum value. Subsequently, the form cylinder 06 over the hydraulic pistons 82 (see. 4 ) to the satellite cylinder 05 postponed until the measuring rings 31 attached to the end faces of the forme cylinder 06 are arranged on the lateral surface of the satellite cylinder 05 issue ( 16 and 17 ). The outer diameter of the measuring rings 31 are designed to be the substrate 28 the printing plate 27 slightly beyond, but still the actual diameter, passing through the surface of the printed image 29 is formed, fall below. The form cylinder channel 34 should hereby become the center of the satellite cylinder 05 demonstrate. The setting is characterized with or without applied printing plates 27 possible.

This state shows 17 , The measuring rings 31 of the forme cylinder 06 are to the lateral surface of the satellite cylinder 05 employed and the form cylinder channel 34 is to the middle of the satellite cylinder 05 aligned. In the enlarged detail view of 17 is the structure of the measuring rings 31 to the carrier material 28 and to the printed image 29 the printing plate 27 seen.

The next step will be the hydraulic pistons 82 subjected to a maximum pressure p _max and then the stop wedge 79 via the servomotor 33 drove into the gap. The end position of the stop wedge 79 is due to the increased to maximum current consumption of the servomotor 33 indexed. The servomotor 33 is switched off, the pressure on the hydraulic piston 82 is set to a lower pressure p ₁ . For this purpose, it should be noted that the pressure p _max must produce a higher setting force than that by the incoming stop wedge 79 generated force F _n , the torque of the servomotor 33 is dependent. The pressure p ₁ generates a lower setting force than the engine torque on the stop wedge 79 However, it is also so large that a secure fixation of the forme cylinder 06 is ensured during the printing process.

Subsequently, the stop wedge 79 via the servomotor 33 by a predetermined distance x in the gap process to the forme cylinder 06 from the satellite cylinder 05 turn it off so far that the gap required for printing is reached. As a rule, then lies the print image 29 with a slight bias on the paper. The position of the stop key 79 is always over the potentiometer 32 on the servomotor 33 indexed. Process-related changes of the gap can be made by adjusting the stop key 79 be realized, wherein the pressurized hydraulic piston 82 the sled 74 of the linear bearing 70 always reliable against the stop wedge 79 tighten.

In the next step, the anilox roller 07 with fully extended stop wedge 79 to the form cylinder 06 moved until the measuring rings 31 attached to the end faces of the forme cylinder 06 are arranged, on the lateral surface of the anilox roller 07 issue. The form cylinder channel 34 must point to the anilox center. The next step will be the hydraulic pistons 82 of the linear bearing 70 the anilox roller 07 subjected to a maximum pressure p _max and then the stop wedge 79 via the servomotor 33 drove into the gap. The end position of the stop wedge 79 is due to the maximum current consumption of the servomotor 33 indexed. The servomotor 33 is switched off, the pressure on the hydraulic piston 82 is set to a lower pressure p ₁ . Subsequently, the stop wedge 79 via the servomotor 33 by a predetermined distance y in the gap process to the forme cylinder 06 from the anilox roller 07 turn it off so far that the gap required for printing is reached.

The upper detail view of 18 shows the relative to the satellite cylinder 05 set form cylinder 06 after setting the gap required for printing, while the lower detail view the delivery of the anilox roller 07 to the measuring rings 31 of the forme cylinder 06 shows, wherein the molding cylinder channel 34 to the axis of the anilox roller 07 is aligned.

It will turn up 2 Referenced. The first guide roller 26 with which the printed paper web 02 after the printing comes into contact, is arranged so that the freshly printed paper side with the surface of the guide roll 26 does not come in contact. For drying the freshly printed paper web 02 are one or more drying facilities 25.1 ; 25.2 or dryer 25.1 ; 25.2 intended. At least one of these dryers 25.1 ; 25.2 , in 2 at least the dryer 25.2 , is arranged so that the waste heat of the dryer 25.2 the overlying paper web 02 dries again. Or, in other words, the paper web 02 is managed so that it is just above a dryer 25.2 , one below the dryer 25.2 running paper web 02 dries, runs. In this way, the time required for drying or the time required for drying is shortened or the energy of the dryer 25.2 very well used.

19 shows a modification of in 2 shown satellite printing unit 03 , In the case of the embodiment according to 19 lie the linear guides 16 the linear bearings 15 from chambered scraper 08 , Anilox roller 07 and form cylinder 06 of every printing unit 04 parallel, in the case of the embodiment in particular on a horizontal, so that the channel beats between form cylinder 06 and anilox roller 07 not on the linear guides 16 can act. Further advantageous in such an arrangement is that all slides 74 the linear bearings 15 a printing unit 04 in common linear guides 16 can lie.

Also, it is in such an arrangement of advantage that now at a delivery of the forme cylinder 06 to the satellite cylinder 05 due to the selected position of the cylinder 05 ; 06 ; 07 to each other, the anilox roller 07 can be moved synchronously with the same feed value as the forme cylinder 06 , so that the pressure bias between the anilox roller 07 and form cylinder 06 does not change.

20 shows a modification of in 19 shown satellite printing unit 03 , wherein the linear guides 16 the two lower form cylinder 06 and anilox rolls 07 to improve the usability of the printing unit 03 are arranged vertically to disk laying.

With a delivery of the forme cylinder 06 to the satellite cylinder 05 may be due to the selected location of the cylinder 05 ; 06 ; 07 to each other, the anilox roller 07 be moved synchronously with the same delivery value as the forme cylinder 06 , so that the pressure bias between the anilox roller 07 and form cylinder 06 does not change.

Deviating from the embodiment according to 19 is the linear bearing 15 the chambered doctor 08 or their linear guide 16 not here in the side frame 11 respectively. 12 the printing unit 03 attached, but on a separate carrier part 36 as an angled plate 36 may be formed and non-positively with the carriage 74 the anilox roller 07 is connected, so that the pressure-on position of the chambered doctor blade 08 to the anilox roller 07 from the movement of the anilox roller 07 is independent, cf. 21 ,

According to another embodiment of the invention is a flexographic printing unit 03 , z. B. a satellite printing unit 03 with at least eight cylinders 06 provided, wherein the form cylinder 06 in pairs may have different diameters and / or two each form cylinders 06 in each case only one common screen roller 07 assigned. In the case of the embodiment according to 22 is a satellite printing unit 03 with eight form cylinders 06 shown, each with two forme cylinders 06 in pairs only one anilox roller each 07 is assigned and both form cylinder 06 a pair of cylinders may have different diameters or may have the same diameter for the purpose of imprinter operation, wherein the anilox roller 07 optionally the larger or the smaller form cylinder 06 can be assigned.

With a printing unit 03 In the configuration shown here it is possible with a printing unit 03 Produce printed products with different section lengths without the need for major remodeling. As a result, the economic use of the machine is considerably increased.

23 shows in the illustration accordingly 11 a linear bearing 15 a cylinder 07 or an anilox roller 07 , which two stop wedges 79 having. In particular, such a linear bearing 15 also applicable in the case of the embodiment described above 22 in which the anilox roller 07 between two form cylinders 06 is movable.

The employment of the anilox roller 07 takes place either alternatively or alternately between the one and the other stop 79 , A middle position of the anilox roller 07 in which she does not use any of the two form cylinder 06 is in contact, z. B. achieved in that of a stop wedge 79 is completely retracted in the associated gap, while at the same time the or the opposite hydraulic piston 82 (see eg. 4 ) is pressurized or become.

In this case, the arrangement may in particular be such that the hydraulic piston 82 both sides with the carriage 74 of the linear bearing 70 the anilox roller 07 mechanically connected. The back of the hydraulic elements is designed as an inclined plane forms and forms with the associated stop wedge 79 a sloping plane.

In addition to the above based on 22 explained embodiment results in another way to produce printed products with variable section lengths, in the case of the embodiment to be described below 24 and 25 ,

Here includes every printing unit 03 a satellite cylinder 05 and at least eight forme cylinders 06 , in the case of the embodiment exactly eight form cylinder 06 or exactly eight flexographic printing units 04 , Every form cylinder 06 is an anilox roller 07 assigned and each anilox roller 07 is a chambered scraper 08 assigned. Every form cylinder 06 and every anilox roller 07 has its own (not shown here) drive motor 121 on.

Furthermore, every form cylinder 06 in a linear bearing 15 stored (not shown here) and to the satellite cylinder 05 fine adjustable adjustable. Each anilox roller 07 is also in a linear bearing 15 (not shown here) stored and the forme cylinder 06 fine adjustable adjustable. Besides, every chambered scraper is 08 on a linear bearing 15 stored and the associated anilox roller 07 adjustable in pressure and with the linear bearing 15 the anilox roller 07 mechanically coupled to any change in position of the anilox roller 05 without changing the pressure-on position inevitably follows. With regard to the relevant details, reference is made to the above description in connection with other embodiments.

The anilox roller 07 of every printing unit 04 is arranged so that the axes of rotation of the anilox roller 07 , the forme cylinder 06 and the satellite cylinder 05 lie on a common line. At a delivery of the forme cylinder 06 to the satellite cylinder 05 may be due to the selected location of the cylinder 05 ; 06 ; 07 to each other, the anilox roller 07 be moved synchronously with the same delivery value as the forme cylinder 06 , so that the pressure bias between the anilox roller 07 and form cylinder 06 does not change.

Every form cylinder 06 has distributed in the circumferential direction at least one printing section 27a ; 27b respectively. 27c ; 27d and at least one non-printing section 30 on. In particular, each form cylinder 06 distributed over its circumference two printing plates 27a ; 27b respectively. 27c ; 27d on top of the printing sections 27a ; 27b respectively. 27c ; 27d define and between which the non-printing sections 30 are located ( 25 ).

The printing sections 27a ; 27b respectively. 27c ; 27d or printing plates 27a ; 27b respectively. 27c ; 27d have in the circumferential direction of the forme cylinder 06 preferably each have the same length and are preferably distributed over the circumference equidistant.

With a printing unit 03 In the configuration described, it is possible to produce variable-size printed products. This is achieved by the print image to be printed 29 in equal parts on two printing plates 27a . 27b respectively. 27c . 27d distributed, the different form cylinders 06.1 respectively. 06.2 are assigned, with the largest length of the printed image 29 Max. the circumference of a forme cylinder 06 less twice the width of the white margin minus an area for decelerating and accelerating the forme cylinder 06 may be.

The printing plate 27a of the first forme cylinder 6.1 puts the first partial print picture 37A on the at the satellite cylinder 05 guided paper web 02 from. The printing plate 27c of the second forme cylinder 6.2 then sets the second partial print image 37C Registered and passerhaltig on the paper web 02 from. Likewise, the pressure plate sets 27b of the first forme cylinder 6.1 the first partial print picture 37B and then the printing plate 27d the drawing file 37D on the paper web 02 from. The on the paper web 02 printed partial images 37A and 37C as well as the printed partial pictures 37B and 37D each form a section length.

To the difference between the cylinder circumference of the forme cylinder 06 and to compensate for the printing length becomes the forme cylinder 06 drivably braked and then accelerated back to production speed, in particular by means of 6 to 10 explained drive motors 121 or synchronous motors 121 , Through this process, the form cylinder 06 brought back into the correct angular position to the printed product to then print at the production speed, ie paper speed.

The advantage here is the high pressure that the printing sections 27a ; 27b ; 27c ; 27d are increased and the non-printing sections 30 lie lower. The deceleration and acceleration process of the forme cylinder 06 takes place in the area where the non-printing sections 30 at the satellite cylinder 05 and on the anilox roller 07 rotate past. It is advantageous in that configuration, in the anilox roller 07 , Forme cylinder 06 and satellite cylinders 05 lying on a straight line that the form cylinder 06 during the acceleration phase neither with the paper web 02 still with the anilox roller 07 is in contact and during the printing process, the one printing plate 27 over the anilox roller 07 is colored while the other pressure plate 27 just prints. It also follows that the peripheral speed of the anilox roller 07 and the satellite cylinder 05 are the same size and "constant" and only the form cylinder 06 must be cyclically accelerated and delayed.

Similarly, the production of three or more printed products with a smaller section length can be realized by the printing plate 27a or the pressure plate 27b an entire partial image as well as half of the second partial image, the printing plate 27c or the pressure plate 27d contains the second half of the second field and a third entire field.

With a pressure unit formed as explained above 03 For example, it is also possible to produce variable-length printed products, provided that the longest product is smaller than half the circumference of the cylinder minus the white edge and a region dimensioned to be the forme cylinder 06 can be accelerated again in the correct angular position to the printed product.

As explained, the embodiments according to 22 on the one hand and 24 and 25 on the other hand, variable section length printed products, whereby the variability with respect to the printed products to be produced can be considerably increased. To produce various newspaper-like products in a printing shop, at least one additional, additional format is often required, which differs from the main format. Additional formats that cause a circumferential change of the plate cylinder have been extremely problematic. Common concepts known from the technology of offset printing are not applicable in the case of flexographic printing.

The explained above possibility a variable section length offers the user an economically attractive option a second format without the same format otherwise unavoidable Print waste. Alone the omission of the otherwise arising additional costs the blending (paper and cutting equipment) can be a cheaper Amortization of the solution described have as a consequence. Optionally, a second printing machine for the second format Completely eliminated and above In addition, the for two formats suitable printing machine particularly busy be, whereby the efficiency of the inventive solution optimized becomes.

To set the printing section length to a folding section length of one of the printing unit 03 or the printing tower 01 downstream folding apparatus 123 to be able to adapt, can advantageously be provided that the section length of the folder 123 is changeable, whereby a highly efficient production of printed products is possible. Based on 26 to 29 will be examples of a suitable folder 123 variable-pitch section length explains how it handles the printing units 03 or the printing towers 01 can be connected directly or indirectly.

In 26 is an embodiment of a variable folder 123 shown with system 7: 7. The type of such a folder can, for example, from the EP 02 57 390 B1 be removed. The folder 123 points at the inlet of the printing material web 02 a Zugwalzenpaar 124 on, with which the printing material web 02 is electrostatically charged. In a downstream cutting roller pair 126 becomes the printing material web 02 cut into individual sheets according to the specified section length. The cutting roller pair 126 are acceleration bands 127 downstream, in which the individual sheets can be accelerated. Subsequently, the sheets reach a cylinder 128 , in particular collecting cylinder 128 and / or folding blade cylinder 128 , and from there to a spring-folding jaw cylinder 129 passed. The cylinder 128 has two multi-arm against each other adjustable dashboard. By adjusting the two dashboard holder against each other, the section length can be changed when folding the cut sheet.

To drive the various functional elements of the folder 123 are electric motors 131 , in particular servomotors 131 provided, which are controlled independently of other drive devices. Cylinder part and delivery of the folder 123 are independently drivable. The cylinder 128 preferably has arranged on dashboard folding blade systems and holding systems, eg. B. gripper systems or point needles systems.

A distance between the holding system and the folding blade of the folding blade cylinder 128 depending on the diameter of a forme cylinder 06 is remotely controlled via a control device.

27 shows a further embodiment of a folding apparatus 123 which can be used in printing presses. The folder 123 is built in the system 5: 5 with double third fold and two cross fold displays. Also on this folder 123 is a cutting roller pair at the inlet 126 intended. The folder inlet of the folder 123 is designed so that the format adjustment depending on the section length in the high pressure by the fixed speed ratio to the forme cylinders 06 rotating cutting roller pair 126 he follows. The cutting roller pair 126 depending on the order at a certain speed, more or less strand length, pass the cross cutting group before the cut takes place.

28 and 29 each show a pair of cutting rollers 126 with the beginning of the band section 127 , z. B. acceleration belts 127 for the acceleration of the bow to the folding cylinder speed. The cutting roller pair 126 can be clocked in time with the forme cylinder 06 are driven. Alternatively or additionally, the cutting roller pair 126 with predetermined speed ratio to the speed of the forme cylinder 06 are driven. As a result, it is achieved in each case that the cutting roller pair 126 independent of the web speed of the substrate web 02 is driven at a predetermined speed, thereby the section length of the folder 123 to vary.

According to a further advantageous aspect of the invention, the anilox roller 07 a web-fed rotary printing press, for example a flexographic printing machine, associated with a suction device.

at the construction of chambered doctor blades must be that over the empty wells the anilox roller in the closed chamber blade air introduced can escape again from the chambered doctor blade or is forcibly discharged. The air introduced into the chamber doctor forms air cushions with overpressure, the to a lifting of the force-controlled employed chamber doctor leads from the anilox roller. As a result, a thin color film is produced on the anilox roller surface, the in turn leads to increasing density values in the printed product.

For example the paint is pumped into the chamber squeegee and it is over a second pump, usually a compressed air driven diaphragm pump, the paint is sucked off with the air introduced into the chambered doctor blade, wherein the extracted color and air mixture amount is twice larger as the amount of ink pumped. To avoid negative pressure is the chambered doctor blade with holes connected to the surrounding air. A disadvantage of this embodiment, that of the anilox roller after contact with the pressure plate of this torn off from the paper web paper dust particles and other dirt particles are conveyed back into the chambered doctor blade and mix with the printing ink in the chambered doctor blade and not forcibly removed from the exhaust system. As well is colored by the contact with the printing plate, although from the Rasterwalzennäpfchen is torn, but is not brought to the paper web, but on the surface the anilox roller is conveyed back again, from the closing squeegee stripped of the chamber doctor blade and dripping on the squeegee, causing soiling the doctor system leads.

According to the invention, it is now proposed that the surface of the anilox roll 07 before entering one of the anilox roller 07 associated coloring device 08 such as a chambered doctor blade 08 suck.

As a result, the disadvantages described in connection with the prior art are avoided. In addition, by sucking the air from the screen roll cups before contact with fresh paint, the filling of the cups with fresh paint is improved and there is no air-enriched and soiled paint on the printing plates 27 passed.

The suction is preferably carried out so that the suction together with the chambered doctor blade 08 forms a closed system and the extracted grid roller cups no longer come into contact with the surrounding air.

An embodiment of this aspect of the invention will be described below with reference to FIGS 30 to 32 described in more detail:
In the 30 shown printing unit 03 is constructed in the case of the embodiment as the printing unit 03 according to 1 respectively. 2 and in this respect reference is made to the description there. In addition, in the case of the invention, a total of the reference numeral 38 designated suction device 38 intended.

The suction device 38 includes an over the entire axial length of the anilox roller 07 extending hood-like housing 39 into which the chambered doctor 08 is integrated and which is different from the chambered doctor 08 in the direction of the in 31 indicated by the arrow direction of rotation of the anilox roller 07 extends. The housing 39 is to the cylindrical surface of the anilox roller 07 open and in the axial direction over sealing side walls 41 , z. B. a seal 41 opposite the anilox roller 07 sealed. The side walls 41 of the housing 39 overlap the side seals of the chambered doctor blade 08 and thus form with the chambered doctor blade 08 a closed room.

In the case 39 is at least one suction opening 42 educated. In the case of the embodiment is a single suction opening 42 in one of the side walls 41 provided by a preferably extending in the axial direction connecting piece 43 is defined for connecting a hose or pipe, not shown, for sucking the in the housing 39 located mixture of air and paint. The extracted mixture becomes a color tank 44 with downstream filter circulation 45 , z. B. a filter device 45 supplied and the purified color fed back to the printing process. In particular, the suction opening 42 paraxial to the anilox roller 07 aligned.

According to a further advantageous aspect of the invention, hereinafter in connection with 33 and 34 is explained, the possibility is created to enable with simple means the printing of different paper web widths.

33 schematically shows the arrangement of form cylinder side register elements 51 ; 52 ; 53 ; 54 , in particular register stops 51 ; 52 ; 53 ; 54 in the closures of a (not shown here) forme cylinder 06 with four printing plates 56 respectively. 56A ; 56B ; 56C ; 56D in width for printing on a (not shown here) printing substrate 02 or paper web 02 a predetermined (maximum) width b. In general, the corresponding with pressure plate side register elements 57 in particular punching 57 cooperating register stops 51 ; 52 ; 53 ; 54 in the closures as in 33 Placed so that the distance between each register stops 51 ; 52 ; 53 ; 54 always the same. With such an arrangement, it is also possible, narrower paper webs 02 printing on four sides in width, if either the printed image on the printing plates 56A ; 56B ; 56C ; 56D is offset relative to the center of the plate in width or by the use of panoramic panels.

The disadvantage in the first case is that the narrowing of the paper web 02 can only be done in a very small and out of proportion to the economic benefits, since usually the side non-printing area has already been optimized accordingly and also in the pre-press the location of the printed image 29 to the center line of the printing plate 56 respectively. 56A ; 56B ; 56C ; 56D depending on the final position of the printing plate 56 respectively. 56A ; 56B ; 56C ; 56D must be determined in the machine, which requires a logistical masterpiece, especially in large machinery.

adversely in the second case, that processes panoramic panels in prepress Need to become, which usually has an extra Effort through the procurement of separate imagesetter and Plate processing lines and their availability and maintenance conditional. Negative affects also from that in case of a partial update change of the newspaper pages Even unaffected newspaper pages need to be changed since they lying on the same panorama plate as the newspaper pages to be changed. On the other hand, it is advantageous that a wide range of different paper web widths is infinitely realize. In practice, however, the paper web widths to be printed, in order to include paper logistics and the printing machine downstream transport and shipping facilities not unnecessary to complicate.

In order to avoid these disadvantages and to be able to realize the printing of at least three different paper web widths with simple means (the maximum narrowing is dependent on the structural conditions of the closures and the narrowing is done in stages of the same size and the narrowing not only partial webs of the largest paper web width b includes), the register stops according to the invention 52 ; 53 the closer to the machine longitudinal axis L arranged printing plates 56B ; 56C offset by a measure to the machine center, which is smaller by half than the dimension a, which characterizes the smallest paper web narrowing, see. 34 ,

To deal with this configuration of register stops 51 ; 52 ; 53 ; 54 To print different paper web widths, is also a different punching 57 ( 57.1 ; 57.2 ; 57.3 ) of the printing plates 56 necessary, whose width is also the narrowing of the paper web 02 is adjusted, wherein the plate width is reduced by a quarter of the dimension a. In prepress, the narrower printing plates are 56 Can be processed with the existing slabs and exposure systems with the same stop system. The following are the printing plates 56 in its original, maximum width 56.1 , in contrast, in their respective reduced by the amount a / 4 width 56.2 and in their opposite to the original width each by the amount a / 2 reduced width 56.3 designated.

For production with the largest paper web width b, therefore, the printing plates must 56.1 with three punched out 57.1 symmetrical to the center of the printing plate 56 be provided whose center distance is offset from one another by the amount a.

In production with a paper web 02 , which is narrowed by the dimension a, become the printing plates 56.2 , whose width was reduced by a / 4, with two punched out 57.2 symmetrical to the center of the printing plate 56.2 provided, wherein the center distance is offset from each other by 3/4 of the dimension a.

In production with a paper web 02 , which is narrowed by twice the dimension a, become the printing plates 56.3 , whose width was reduced by a / 2, with four punched out 57.3 symmetrical to the center of the printing plate 56.3 verse hen, wherein the center distance to each other by half of the dimension a is offset.

The main advantages of the process are that on all printing plates 56 the printed image is placed the same relative to the center of the plate and thus in the prepress no consideration of the final position of the printing plate 56 must be taken in the machine that the plate consumption by the use of narrower printing plates 56.2 ; 56.3 It is minimized that the existing exposure systems and slabs can continue to be used, and that the direct succession of productions can be done with different paper web widths without additional retooling in combination with motorized hoppers.

01

printing tower

02

printing material, paper web

03

Printing unit Flexographic printing unit, satellite printing unit

04

Printing, flexo

05

Cylinder, Impression cylinder, satellite cylinder

06

Cylinder, form cylinder

06.1

Form cylinder, first

06.2

Form cylinder, second

07

Cylinder, Anilox roller, component

08

component Einfärbeeinrichtung, chambered doctor blade

09

10

11

side frame

12

side frame

13

14

storage unit

15

linear bearing

16

linear guide

17

traverse (08)

18

holder

19

actuator, Cylinder-piston means

20

21

cylinder

22

piston

23

piston rod

24

Return spring

25.1

Drying device, dryer

25.2

Drying device, dryer

26

guide roll

27

Printing plate, flexographic printing plate

27a

Section, printing, printing plate

27b

Section, printing, printing plate

27c

Section, printing, printing plate

27d

Section, printing, printing plate

28

Carrier material ( 27 )

29

Printed image ( 27 )

30

Section, not printing ( 06 )

31

Measuring ring ( 06 )

32

Sensor, potentiometer

33

servomotor

34

Form cylinder channel

35

36

Supporting part, plate

37A

Partial print image

37B

Partial print image

37C

Partial print image

37D

Partial print image

38

suction

39

casing

40

41

side, seal

42

suction

43

suction

44

paint tank

45

46

Filtration circuit, filtering device

47

48

49

50

51

Register element, Register stop, form cylinder side

52

Register element, Register stop, form cylinder side

53

Register element, Register stop, form cylinder side

54

Register element, Register stop, form cylinder side

55

56

printing plate

56A

printing plate

56B

printing plate

56C

printing plate

56D

printing plate

56.1

Printing plate, maximum width

56.2

Printing plate, reduced width

56.3

Printing plate, reduced width

57

Register element, Punched out, pressure plate side

57.1

Register element, Punched out, pressure plate side

57.2

Register element, Punched out, pressure plate side

57.3

Register element, Punched out, pressure plate side

58

59

60

61

62

63

Cones ( 06 )

64

Cones ( 07 )

65

rolling elements

66

clamper

67

68

69

cover

70

Linear guide, linear bearing

71

Camp, Radial bearings, cylindrical roller bearings

72

Bearing means Bearing element, linear element

72.1

guide surface

72.2

guide surface

73

Bearing means Bearing element, linear element

73.1

guide surface

73.2

guide surface

74

Pillow Block carriage

75

Connection, clamping element

76

Carrier, carrier plate

77

recess

78

Wave, drive shaft

79

Medium, Stop, wedge, stopwedge

80

cylinder unit

81

Element, spring element

82

actuator, force-controlled, adjusting means, pistons, hydraulic pistons

83

stop surface

84

Regulators, Actuator, piston, pressure actuated

85

Transmission member piston rod

86

Return spring

87

88

Stop, overload protection, spring element

89

Mounting aid, dowel

90

91

Holding means, screw

92

Medium, clamping screw

93

Valve, taxable

94

cover

95

96

attack

97 to 120

121

Drive motor, Electric motor, synchronous motor, motor, permanent magnet excited

122

123

folding

124

pair of drawing rollers

125

126

Cutting roller pair

127

Bands section, acceleration belt

128

Cylinder, Collection cylinder, folding knife cylinder

129

jaw cylinder

130

131

Electric motor, servomotor

132

Clutch, multi-plate clutch

133 to 265

266

Runner, rotor

267

permanent magnets

268

winding

269

stator

270

271

guide

272

Management, electrical

273

274

Rotation angle sensor

275

276

signal line

277

Camp, Radial bearings, roller bearings

278

permanent magnets

279

winding

280

281

signal line

a

Measure of the least Papierbahnverschmälerung

b

Web width, greatest

F

force

L

machine longitudinal axis

P

print

S

setting direction

E1

level

E2

level

Δ71

bearing clearance

Claims (22)

Flexographic printing machine with at least one by a drive motor ( 121 ) driven rotary body ( 06 ; 07 ), wherein the rotational body ( 06 ; 07 ) in on side frames ( 11 ; 12 ) arranged linear bearings ( 70 ) and is movable perpendicular to its axis of rotation, wherein a stator ( 267 ) of the drive motor ( 121 ) with the linear bearing ( 70 ) or the rotational body ( 06 ; 07 ) is jointly movable, characterized in that the drive motor ( 121 ) as a synchronous motor ( 121 ) is formed with permanent magnet excitation that the rotational body ( 06 ; 07 ) with its cones ( 63 ; 64 ) the side frames ( 11 ; 12 ) does not penetrate, that the rotation body ( 06 ) as a form cylinder ( 06 ) is formed and a plurality of forme cylinder ( 06 ) with a satellite cylinder ( 05 ) are arranged cooperatively. Flexographic printing machine according to claim 1, characterized in that the synchronous motor ( 121 ) can be used in generator mode as a braking device. Flexographic printing machine according to claim 1, characterized in that the synchronous motor ( 121 ) as field weakenable synchronous motor ( 121 ) is trained. Flexographic printing machine according to claim 3, characterized in that the field weakening of the synchronous motor ( 121 ) is provided to a ratio of 1:10. Flexographic printing machine according to claim 1, characterized in that the synchronous motor ( 121 ) has six poles. Flexographic printing machine according to one of claims 1 to 5, characterized in that in a housing of a storage unit ( 14 ) a radial bearing ( 71 ) of the forme cylinder ( 06 ), the linear bearing ( 70 ) and at least one actuator ( 82 ) are arranged. Flexographic printing machine according to one of claims 1 to 6, characterized in that the rotor ( 266 ) or runners ( 266 ) of the synchronous motor ( 121 ) Poles of permanent magnets ( 267 ) having. Flexographic printing machine according to one of claims 1 to 7, characterized in that the synchronous motor ( 121 ) has a creep torque in the range of 100 Nm to 200 Nm. Flexographic printing machine according to one of claims 1 to 8, characterized in that the synchronous motor ( 121 ) has a maximum torque in the range of 600 to 800 Nm, in particular about 700 Nm. Flexographic printing machine according to one of claims 1 to 9, characterized in that the synchronous motor ( 121 ) has a theoretical idling speed in the range of 500 U / min to 600 U / min. Flexographic printing machine according to one of claims 1 to 10, characterized in that the synchronous motor ( 121 ) is preceded by a frequency converter for speed control. Flexographic printing machine according to one of claims 1 to 11, characterized in that the synchronous motor ( 121 ) a rotation angle sensor ( 274 ) is provided. Flexographic printing machine according to one of claims 1 to 12, characterized in that the synchronous motor ( 121 ) a cooling device, in particular a fan or a liquid coolant circuit, is provided. Flexographic printing machine according to claim 1, characterized in that a rotation axis of a rotation angle sensor ( 274 ) coaxial with the axis of rotation of a rotor ( 266 ) of the drive motor ( 121 ) or to the axis of rotation of the rotating body to be driven ( 06 ; 07 ) is arranged. Flexographic printing machine according to one of claims 1 to 14, characterized in that the rotational body ( 06 ; 07 ) in a linear bearing ( 15 ) is mounted and linearly movable. Flexographic printing machine according to claim 1 or 15, characterized in that the rotary body together with permanent magnets ( 267 ) is formed preassembled in the region of its circumference. Flexographic printing machine according to claim 16, characterized in that a windings ( 268 ) stator ( 269 ) inside the body of revolution ( 06 ; 07 ) is arranged. Flexographic printing machine according to claim 16, characterized in that a windings ( 268 ) stator ( 269 ) outside the body of revolution ( 06 ; 07 ) is arranged. Flexographic printing machine according to claim 1, characterized in that the drive motor ( 121 ) from a signal line carrying a virtual master axis ( 226 ) Receives signals to the target angular position and / or angular velocity and / or Leitachsposition. Flexographic printing machine according to one of claims 1 to 19, characterized in that the permanent magnets ( 267 ) Have rare earth materials. Flexographic printing machine according to claim 1, characterized in that the linear bearing ( 70 ) in a storage unit ( 14 ) and that the storage unit ( 14 ) the side frames ( 11 ; 12 ) does not penetrate. Flexographic printing machine according to claim 6 or 21, characterized in that the bearing unit ( 14 ) each on the inner walls of the side frames ( 11 ; 12 ) is arranged.