EP1155826A2 - Rotary printing machine - Google Patents

Abstract

The machine has rubber pad cylinders (2) forming print positions with counter printing cylinders or a common counter printing cylinder and plate cylinders (3) combined with rubber pad cylinders in pairs to form cylinder groups (10) with dedicated drives. For each cylinder group the rubber pad cylinder or plate cylinder is driven by the group motor (5) via a toothed belt or gear wheel drive and this cylinder drives the other cylinder in the group.

Description

The present invention relates to the combination of cylinders Rotary printing machine for individual cylinder groups and a drive control therefor.

Conventional rotary printing machines are powered by a main drive mechanical longitudinal shaft, also called the king shaft, driven. One disadvantage of this Printing machines is the mechanical effort to compensate for the torsion of the longitudinal shaft occurring during the run. This creates a mechanical Circumference register adjustment of printing points of the printing press during the run necessary.

From DE 38 28 638 C1 a printing press is known, its cylinders and rollers are driven by a main motor via a toothed belt. The engine will regulated on the basis of actual values tapped on the load side. The cylinders and rollers of the Printing presses are coupled to one another via a drive wheel train. Through the described regulation, vibrations in the drive wheel train are difficult or keep low with great technical effort. Because the load moment of inertia is very large, this known regulation is slow and at most has a low one Control dynamics.

It is also trying to find the mechanical longitudinal shaft between each Replace pressure units with an electrical longitudinal shaft. Each printing unit receives a separate electric drive. To the high mechanical effort that due to the complexity of the individual printing units with multiple printing points In this case, as in the previous steps, there is still a high level of control technology Effort added because the synchronous operation of the individually driven printing units among themselves must also be ensured.

To avoid the problems mentioned, DE 41 38 479 A1 proposes to drive the cylinders of the printing press by one electric motor each.

From DE 42 14 394 A1 a control system for such a printing press is included known individually driven cylinders. The individual drives of the Cylinders and their drive controllers combined into pressure point groups as desired become. The pressure point groups are assigned to folders, from which they receive theirs Get position reference. The proposed control system essentially consists of a fast BUS system for the individual drives and the drive controllers Pressure point group and a superordinate control system for the administration of the Pressure point groups.

From the document "Electronic shaft with digital intelligent drives for Druckmaschinen "from Mannesmann Rexroth, HMI / 04.93 drives are known at each of which a cylinder is driven by a motor that is directly on the Cylinder shaft sits. The motor is either only based on an actual motor value or based on two actual rotation angle positions, namely the rotation angle position of the motor and the angular position of the cylinder.

The concept of individually driven cylinders pursued in these three documents allows a high degree of flexibility, but at the same time requires a very high level Number of drive motors and, as DE 42 14 394 A1 shows, a high Regulation effort for this large number of individual drives. In addition, a Variety of engines can be used. When using only a few motor sizes would otherwise be oversized motors for different applications to use. Both drive the price of such a printing press.

A printing machine known from JP-A 63-236651 has printing units which are individually driven by their own drive motors. The printing units comprise mechanically coupled in pairs for their common drive Blanket cylinder and plate cylinder. The motors drive on each Plate cylinders of the printing units. From the plate cylinders is over Gear couplings driven on the blanket cylinders. The engines are sitting directly on the shafts of the plate cylinders. Regulators of the motors Machine control signals as setpoint signals and engine speed and Motor speed signals supplied as actual value signals. The regulation of the engines takes place depending on a comparison between the setpoint signals and the Actual value signals, i.e. based on the difference between the setpoint signals and the Actual value signals on the motor side.

The present invention has set itself the task of being highly flexible create usable, yet economical rotary printing press.

This object is solved by the subject matter of claim 1.

According to the invention, blanket cylinder and plate cylinder form one Rotary printing machine in pairs a cylinder group, in each case one Blanket cylinder and a plate cylinder are mechanically coupled and are driven together by a separate drive motor for each cylinder group.

Through this grouping of the two cylinders and their equipment with a single drive for at least one pair of cylinders, the number of required drive motors significantly reduced; at least halved compared to the Individual drive concepts. The mechanical coupling of these two to each other Cylinder associated with printing technology, preferably with a gear coupling straight or helical gears, offers compared to the concept of each individually driven cylinders offer significant price advantages. In terms of versatility there are no major drawbacks compared to the single drive concept do. So both the circumferential register and the side register adjustment can each Blanket cylinder individually and for any other blanket cylinder, if necessary, coordinated. Through the cylinder groups according to the invention, each with its own drive motors can be at a Rotary printing machine optimal in technical and economic terms Pressure points are formed. As pressure points in this context each understood the pairs of cylinders, between which a paper web to be printed runs through and is printed on one or both sides. Accordingly belong to one Pressure point formed according to the invention in each case one cylinder group and one corresponding impression cylinder, which may belong to the cylinder group, but not got to. In the latter case, one printing point is assigned to two by one Cylinder groups formed. In terms of drive technology, however, the pressure points are Printing press mechanically independent in both cases, d. H. the pressure points the printing press are electrically coupled together.

In the cylinder groups according to the invention, the Blanket cylinder driven, which in turn via the mechanical coupling on the Drives plate cylinders of the same cylinder group. In another embodiment the invention, however, the drive can also drive the plate cylinder shaft, so that the blanket cylinder only via the mechanical coupling of the plate cylinder is driven. During the drive on the plate cylinder advantageously one requires little effort for turning the blanket cylinder on and off, is the Blanket cylinders, on the other hand, are decisive for the positional accuracy or Circumference register setting. The first solution has the advantage that the Cylinder that ultimately comes into direct contact with a paper web to be printed comes, not only via a transmission element that may be subject to play must be driven.

It is advantageous to have three cylinder groups work on one pressure point each. One cylinder group is on one side of the pressure and two cylinder groups are on the one Opposite pressure side of a paper web running between them. The rubber cylinder preferably forms the one on the printing side of the paper web arranged cylinder group the impression cylinder for the other two Rubber cylinder arranged on the opposite printing side of the paper web Cylinder groups, both of which are advantageously operated alternately can. This configuration offers the greatest versatility for a rubber / rubber production, because with continuous production the two mutually rubber cylinder can be configured for a change in pressure can. This is done by changing the plate of a rubber cylinder that is not in use assigned plate cylinder. Each cylinder group can be stored in a single frame his. Preferably, the two one printing side of the paper web are horizontal opposite groups of cylinders to a stored in a frame Cylinder unit summarized.

A cylinder group can according to the invention around an impression cylinder for the Blanket cylinders are expanded. This third cylinder of the so formed Cylinder group can be mechanically coupled to the blanket cylinder, preferably by a further gear coupling. Such a cylinder group represents already represents a printing point, between the blanket and impression cylinder which too printing paper web is passed through. The impression cylinder can be a steel or can also be another blanket cylinder for double-sided printing. Such a An impression cylinder can in particular also be a central cylinder of a cylinder unit with, for example, nine or ten cylinders. In an alternative, too preferred embodiment of the invention is such a central cylinder of one own drive motor driven. This type of summary grants the maximum versatility for a cylinder unit. In this case, each of the Central cylinder assigned cylinder groups from blanket and plate cylinders can be reversed individually and independently of the other cylinder groups, like this for example for alternating pressure or for flying plate changes.

The output from a drive motor takes place on the respective cylinder group preferably by means of a toothed belt. Compared to the known solution of the the drive shaft of the driven cylinder seated rotor of the electric motor such a timing belt has a high elasticity. For the control concept of the drive one However, the cylinder group is that given by the use of a toothed belt Possibility of high damping of a drive motor and the driven cylinders existing mechanical system of great value, as yet is explained. In principle, however, the invention also permits direct drive, which can even be advantageous for small cylinders. Opposite a gear drive between the drive motor and the driven cylinder of a cylinder group, such as it can also be used, a toothed belt has the advantage of a backlash-free running and a not absolutely fixed gear ratio.

In contrast, are for the mechanical coupling between the cylinders inside a group of cylinders preferably provided gears, although others Transmission links are also conceivable. The intermeshing Gears can be spur or helical. With helical gears for the side register adjustment the blanket cylinder is shifted lengthways while his drive and / or driven gears remain stationary according to the invention. Otherwise, with the side register would also be a circumferential register adjustment required. When using straight toothed gears the blanket cylinder along with its fixed gear or gears postponed.

The inking roller or the inking rollers or dampening rollers of an inking unit or one Ink and dampening units that are assigned to a cylinder group can or can According to the invention mechanically coupled to this cylinder group, so that the Ink roller or the ink rollers from the drive motor of this cylinder group with are driven. With this solution, the technical control effort can be low being held. On the other hand, the mechanical coupling of the inking unit is in mind of the modular principle pursued by the invention is not quite as ideal as the stronger one preferred self-drive for the roller or the rollers of the inking unit. After this likewise preferred embodiment of the invention, each inking unit has one own drive motor for his ink rollers. Such a drive motor also drives preferably via a backlash-free toothed belt with high damping and if necessary via a reduction gear transmission, the inking roller or in the case several ink rollers on the plate cylinder of the corresponding cylinder group next lying ink roller. The peripheral speed of this ink roller advantageously adjustable, especially with negative slip compared to Plate cylinder, the peripheral speed of the ink roller preferably something is less than that of the corresponding plate cylinder.

The regulation of a motor / load system with one poses particular problems Drive motor for a cylinder or a roller of a rotary printing machine. In In individual cases, with small loads, a large, i.e. H. powerful motor with one used a comparatively high moment of inertia compared to the load. Such Systems don't throw too much at controlling vibrations and shocks major problems, since the load is forcibly carried by the motor. With larger increasing moment of inertia of the driven loads, their Mass moments of inertia are often more than five times greater than those of the driving motors vibration problems increase. Accordingly more complex become the regulations of these motor / load systems. The elasticity of a coupling between the motor and the load further exacerbates the problems.

In printing press construction, the position or speed of a cylinder are regulated known in which a mechanical encoder on the motor side for detecting the Motor speed or the rotor angular position of the motor for a target / actual comparison of the Motor control is used. However, this known regulation comes up with larger increasing inertia from the load to the motor to their dynamic limits. If the actual position is measured on the motor shaft, then lie both coupling and mechanical load outside the actual control loop. she can, however, react on the motor shaft Influence acceleration torques. The engine, which in this case is an essential one This means that the mass is smaller than the coupling and the cylinder influenced. Because the resulting engine load is made up of a mechanical structure Masses, springs and damping, the load torque is heavily frequency-dependent, which ultimately determines the dynamic behavior of the system. When suggested by a Setpoint changes are first tensioned to the springs that are closest to the motor are located. The engine torque caused by the controller accelerates parts of the Coupling and subsequently the cylinder or the driven roller. Energy is stored in the springs as well as in the mass movement at this time, whose division is constantly changing. The engine likes it within a short time have taken the correct position, but is due to the occurring mass forces distracted again, which leads to another control process. The system must go through controlled, stabilized a relatively slow controller.

The present invention therefore also has the task of regulating to create, with the position and / or the speed of a rotary printing press a cylinder or a roller that is driven by a motor, performance-optimized and with sufficiently high control quality, d. H. in terms of dynamics and the speed or position accuracy can be controlled. The scheme is supposed to be inexpensive and not too high demands on the coupling of motor and Place the load, in particular on the torsional rigidity and freedom from play of the coupling.

At least the drive motors are preferably on the same pressure side cylinder groups of a cylinder unit working in a paper web, position-controlled. So-called ideal position control is preferred, i.e. a delay free Position control with following error. On this, for technical reasons However, the desired, complex type of position control can also be dispensed with become. A simple position control is also a preferred, in particular cheaper, embodiment of the invention.

The regulation of the position and / or the speed of the cylinder to be regulated one Cylinder group or a roller of an inking unit takes place according to the invention by means of a controller for the drive motor through the target / actual comparison of the output signals a setpoint transmitter and an actual value transmitter, this actual value transmitter the position and / or the speed of the cylinder or the roller is detected. In contrast to the Known regulations in rotary printing presses is thus a load generator for Scheme used. In contrast, has so far been used in printing press construction mechanical encoder on the motor side to record the motor speed or the Rotor angular position of the motor used for the target / actual comparison of the motor control. With this conventional regulation, one encounters large inertia ratios from the load to the engine quickly to the dynamic limits. If the regulation becomes unstable, especially the engine starts to swing while the load remains relatively calm.

In control engineering are for so-called dual mass transducers Differential connections, control cascades and active filters are known, but all are one require great control engineering effort. For those described above Load / motor systems, d. H. the self-propelled cylinder groups, it has Surprisingly, the regulation was found to be completely sufficient by means of an actual value to be carried out by one on the load, namely on one of the Cylinder of a cylinder group, attached actual value transmitter has been determined. This Actual value - angular position and / or speed of the relevant cylinder - is sufficient to achieve this a high dynamic and control quality even alone.

The drive motor can even in the dual-mass oscillator according to the invention be careful. The load acting as a low pass filter is insensitive to the Vibrations of the much smaller motor. On the other hand, they can Effects of the load on the drive motor are neglected. The inventive, not least because of their simplicity cheap regulation offers the Another advantage that they are simply the wide range of Mass inertia between load and motor and on itself during operation changing parameters, such as the elasticity of a coupling, can be set can.

By taking the actual value to be controlled according to the invention from the load also measured what has to run exactly, namely the load, not the motor. The end the drive motor, a coupling and the load existing mechanical replacement system is to be regarded as a low-pass filter. With this type of control, the low-pass filter of the Motor coupling load spacing system exploited to avoid shocks and vibrations the controlled system arise to filter. Such shocks and vibrations are thus in reduced to the controller. The risk of rocking will thereby diminished. The dynamics of the control and thus the control quality can thereby compared to the described conventional regulation with identical coupling, be significantly increased.

The actual value transmitter, figuratively speaking, moved from the motor side to the load side forms the main controlled variable for the controller of the motor, d. H. the engine is powered by the Load side guided by their actual value. According to a particularly preferred Embodiment of the invention is not a mechanical actual value transmitter for the detection the position or the speed of the motor required for the regulation of the motor. Any actual value detection integrated in the motor can be advantageous for the pure one Drive monitoring, may be used for an engine emergency shutdown.

The actual value transmitter for the control is according to the invention on torque-free shaft end of the driven cylinder of a cylinder group or attached roller of an inking unit.

Electric asynchronous motors are particularly advantageous as the drive motors used. So far, an asynchronous motor has only been used when using a large motor had to drive a small load. For the present case, where a Drive motor drives a cylinder group or the rollers of an inking unit the driven load has a comparatively high mass moment of inertia compared to the drive motor, the use of asynchronous motors is not known. For the purposes of the regulation according to the invention instead of a load transmitter of a motor encoder, asynchronous motors are particularly suitable. Opposite to that for the have been used in the relevant applications DC motors Asynchronous motors have a higher field stiffness, so that their use is dynamic and Control quality of the system to be controlled improved. The use of others Motor types, for example DC motors, are not, however, fundamental locked out.

The stability of the scheme is due to the preferred use of a backlash-free Toothed belt with high damping as a coupling between the motor and the load improved.

The drive motor can even in the case of the dual-mass oscillator in question be careful. The load acting as a low pass filter is insensitive to the Vibrations of the much smaller motor. On the other hand, they can Effects of the load on the drive motor are neglected.

With the concept of paired blanket and Plate cylinders to groups of cylinders, possibly by another Impression cylinders are expanded, maximum flexibility is obtained, while the price of such a printing press compared to one Printing press with individually driven cylinders can be significantly reduced. For a printing machine composed of such cylinder groups Drive motors in only two, possibly three performance classes, while at directly and individually driven cylinders basically separate motors for each Cylinders of various lengths and diameters are required. Means of the toothed belt drive used according to the invention can possibly in wide limits fluctuating moments of inertia between the load and the engine caught by appropriate choice of gear ratio and on top of each other be coordinated. Reducing the number of drive motors along with the advantage that motors are only available in a few performance classes already offers considerable price advantages. This advantage is due to the Use of the simple control according to the invention, which also changes Mass inertia is flexibly adaptable, reinforced. They come with me advantages of the invention with increasing printing presses, i. H. With increasing number of printing units and printing points per machine, more and more Validity. In particular, the invention is used in the construction of offset rotary printing presses Use; but it is not limited to this type of machine.

Fig. 1

eine Druckstelle mit zwei Zylindergruppen;

Fig. 2

eine Druckstelle mit einer Zylindergruppe;

Fig. 3

eine Zylindereinheit mit einem eigenangetriebenen Zentralzylinder und vier Zylindergruppen;

Fig. 4

eine Zylindergruppe mit einer zugeordneten, eigenangetriebenen Farbwalze;

Fig. 5

eine Regelung des Antriebs für eine Zylindergruppe entsprechend dem Stand der Technik;

Fig. 6

eine Regelung für den Antrieb einer Zylindergruppe nach der Erfindung;

Fig.7

einen Vergleich des dynamischen Verhaltens einer herkömmlichen Regelung und einer Regelung nach der Erfindung in Abhängigkeit vom Massenträgheitsmomentenverhältnis von Motor und Last;

Fig. 8

einen Vergleich des dynamischen Verhaltens einer herkömmlichen Regelung und einer Regelung nach der Erfindung in Abhängigkeit von der Drehsteifigkeit der Kopplung zwischen dem Motor und der Last;

Fig. 9

ein Regeldiagramm des Reglers;

Fig. 10

eine aus drei Zylindergruppen gebildete Druckstelle in Y-Stellung;

Fig. 11

eine aus drei Zylindergruppen gebildete Druckstelle in Lambda-Stellung.

Preferred exemplary embodiments of the present invention are explained below with reference to the figures. Further features and advantages of the invention are disclosed. Show it:

Fig. 1

a pressure point with two cylinder groups;

Fig. 2

a pressure point with a group of cylinders;

Fig. 3

a cylinder unit with a self-propelled central cylinder and four cylinder groups;

Fig. 4

a cylinder group with an associated, self-propelled ink roller;

Fig. 5

a control of the drive for a cylinder group according to the prior art;

Fig. 6

a control for driving a group of cylinders according to the invention;

Fig. 7

a comparison of the dynamic behavior of a conventional control and a control according to the invention depending on the moment of inertia ratio of the motor and load;

Fig. 8

a comparison of the dynamic behavior of a conventional control and a control according to the invention depending on the torsional stiffness of the coupling between the motor and the load;

Fig. 9

a control diagram of the controller;

Fig. 10

a pressure point formed from three cylinder groups in the Y position;

Fig. 11

a pressure point formed from three cylinder groups in the lambda position.

At a printing point shown in FIG. 1, a paper web 1 to be printed becomes between the two opposing blanket cylinders 2 two Cylinder groups 10 passed. The two cylinder groups 10 are each formed by the blanket cylinder 2 and an associated plate cylinder 3, the are mechanically coupled to each other for the common drive. The mechanical Coupling is shown schematically by a line between the center points of the two cylinders 2 and 3 indicated. 1 in the embodiment each of the blanket cylinders 2 of each cylinder group 10 by a three-phase motor 5 driven. The configuration according to FIG. 1, in each case only one Blanket cylinder 2 and a plate cylinder 3 by a mechanical coupling a cylinder group 10 are summarized, is characterized by its simple Construction and the highest possible degree of configuration freedom in the formation of Pressure points or pressure point groups.

Fig. 2 shows a variant for the formation of a pressure point, in which an impression cylinder 4 mechanically coupled for the blanket cylinder 2 with this blanket cylinder 2 is. In this embodiment, the cylinder group 10 is made up of the Blanket cylinder 2, its impression cylinder 4 and the plate cylinder 3 and their mechanical coupling together, so that the pressure point by a single Cylinder group 10 is formed. In the embodiment of FIG. 2 is in contrast 1 of the blanket cylinder 2, but of this cylinder assigned plate cylinder 3 driven by a three-phase motor 5. Advantage of this The variant for combining cylinders into a cylinder group is hers constant delivery behavior due to the mechanical coupling of the blanket cylinder 2 with its impression cylinder 4 and that because of this mechanical coupling there is no direct interference between cylinders 2 and 4. The Impression cylinder 4 can be a second blanket cylinder or a steel cylinder, for example, a central cylinder of a nine or ten cylinder unit.

The assignment of the motors 5 to the blanket cylinders 2 and the plate cylinders 3 can be interchanged in both exemplary embodiments. The drive of the Plate cylinder 3 has the advantage that the cylinder group 10 reversed more easily can be while in the other case when driving the blanket cylinder 2 on the paper web 1 directly printing cylinder is driven and thereby a drive free of playful transmission elements, such as gears, possible is.

In Fig. 3, a cylinder unit 20 is shown, consisting of a central Steel cylinders 6 and four cylinder groups 10 assigned to this central cylinder 6. In each case a blanket cylinder 2 and a plate cylinder 3 are in this Embodiment combined into a cylinder group 10. For driving the Central cylinder 6, a separate three-phase motor 5 is provided. Likewise, however the central cylinder 6 with one of the four cylinder groups 10 a cylinder group form according to the variant shown in Fig. 2. This would make your own Motor 5 for the central cylinder 6 can be saved. On the other hand, the in 3 shows a summary of the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to a cylinder unit 20 the highest possible Flexibility in terms of configuration options. These of the above described basic variants derived configuration of a cylinder unit 20 The advantage in terms of printing technology is that the so-called fan-out effect is very limited holds. Each of the blanket cylinders 2 is also easy on rubber / rubber production reversible. The possibilities in different types of alternating pressure reversal are also not restricted.

As this embodiment shows, one is formed from pairs of cylinders Cylinder group 10 in terms of their configurability, a concept with each individually driven cylinders equal.

4, the interaction is one of a pair of blankets / plate cylinders 2, 3 existing cylinder group 10 shown with an ink roller 7. Here, the Ink roller 7 via its own drive by a motor 5, which to the motor 5 for the cylinder group 10 may be identical, but need not be. The engine 5 for the Ink roller 7 drives via a toothed belt 15 and a pair of gears 16, 17, which Gear 17 sits on the shaft of the ink roller 7, the ink roller 7. The different moments of inertia of the motor 5 and the inking roller 7 through a suitable choice of gear ratios for the output via the toothed belt 15 and the gear pair 16, 17 disarmed.

The peripheral speed of the ink roller 7 is adjustable with a slightly negative Slip against the plate cylinder 3. This can counteract the danger be that the mechanical coupling formed by a pair of gears 12, 13 between the blanket cylinder 2 and the plate cylinder 3 from the meshing is lifted.

The cylinder group 10 is driven by the engine 5 via the toothed belt 11 on the blanket cylinder 2. The mechanical coupling between the Blanket cylinder 2 and the plate cylinder 3 of the same cylinder group 10 form the two gears 12 and 13. To defuse a high ratio of Mass moments of inertia of load and drive, namely cylinder group 10 and motor 5, the speed of the motor 5 is reduced accordingly via the toothed belt 11. This toothed belt 11 is the elastic coupling member between the motor 5 and the driven cylinder group 10. Compared to a basically also suitable Direct coupling or a gear coupling with the toothed belt 11 is a very high damping of the motor / load system 5, 10 achieved. The same applies in principle also for driving the inking roller 7 and its coupling member, the toothed belt 15. Furthermore, by choosing a toothed belt drive because of the continuously variable Translation created a great deal of constructive freedom. The engines 5 for the Cylinder group 10 and the inking roller 7 are each three-phase motors with a high Field rigidity. The modular principle of forming cylinder groups also comes here or roller groups with toothed belt coupling to the drive motor to carry because fewer engine output sizes the entire variety of cylinder or Roll lengths and diameters with correspondingly different Mass moments of inertia can be equipped.

The two gears 12 and 13, which the mechanical coupling between the Form blanket cylinder 2 and the plate cylinder 3 can be helical or be straight toothed gears. In the case of helical gears, the Blanket cylinder 2 longitudinally shifted during the side register adjustment, while the Gear 12 and the corresponding gear for timing belt 11 remain stationary, i.e. these two gears are mounted on the cylinder shaft 14 so as to be longitudinally displaceable. in the In the case of a straight toothing of the two gears 12 and 13, the gear 12 and the gear for the toothed belt 11 firmly on the shaft 14 and are together with the blanket cylinder 2 and the motor 5 for the cylinder group 10 together longitudinally shifted.

In contrast to the regulations known in rotary printing press construction, this will be Motor / load system 5, 10 guided by an actual value, which is from one on the load side, namely attached to the torque-free end of the shaft 14 of the blanket cylinder 2 mechanical load generator 21 is generated. The same type of scheme, namely with A load sensor 27 attached to the load-free shaft end of the inking roller 7 is used for the Regulation of the speed of this ink roller 7 selected.

A control known in printing press construction is shown schematically in FIG. 5. The Regulation of the motor 5, which drives a load 25 via an elastic coupling 24, takes place by means of a controller 23. The load 25 is a heavy roller or a heavy one Cylinder or a corresponding roller or cylinder system, the Mass moment of inertia typically more than five times that of motor 5 is. Nevertheless, the control of this motor / load system should be optimized for performance and with sufficiently high control quality for the speed or the angular position and the speed of the Load 25 are regulated. There should be no connection to the coupling 24 of the motor and the load high demands are made with regard to their torsional rigidity and Freedom of play.

In the known systems, such as one shown in Fig. 5, is a mechanical one Actual value transmitter 21 for generating one for the position or the speed and the position of the Rotor of the motor 5 characteristic electrical signal attached to this rotor. The load 25 is with the coupling 24, which has an elasticity and possibly some play has attached to the motor shaft end. The coupling and the load are outside the actual control loop. You can, however, use this on the motor shaft affect retroactive acceleration moments.

This system runs from the load to the motor in large mass inertia conditions quickly to its dynamic limits. If the control becomes unstable, it vibrates above all the engine while the load remains relatively calm.

6, on the other hand, shows a control in which, as already shown in FIG. 4, the Reference variable for the control is generated by an encoder 21 which is connected to the load 25 and is not attached to the engine 5. This actual value transmitter 21 is at the free shaft end the load, in the embodiment at the free shaft end of the blanket cylinder 2 one Cylinder group 10 attached. This actual value transmitter 21 is therefore in the following Called loader. The coupling 24 is through the toothed belt already described 11 with high elasticity compared to a direct coupling or a gear coupling but also high damping. In addition, this coupling 24 with one Timing belt without play.

The actual value required for the control, generated by the load transmitter 21, which is the angular position the blanket cylinder 2 or its speed and its angular position, is returned to the controller 23. A computer generated setpoint from that Setpoint generator 22 is compared with this actual value and to form a control signal used for the engine 5.

In this regulation, the coupling 24 and the load 25 lie within the actual one Control loop. The load and the coupling 24 form a low-pass filter for those in the Control system creates shocks and vibrations, which are therefore only reduced Dimensions are returned in the controller 23 and therefore not too undesirable Can lead suggestions of the scheme. This is the dynamic and also the Control quality compared to conventional systems even with otherwise the same Coupling significantly increased. The system consisting of controller, motor, clutch and Cylinder is already much more damped. Exaggerated resonance occurs therefore not to the same extent. The controller can therefore be set more quickly without leaving the stable work area.

A possibly attached to the motor 5, in the exemplary embodiment according to FIG. 6 The actual value detection shown can be used for additional monitoring of the motor 5 Example can be used with a desired emergency shutdown option of the engine 5.

The diagrams in FIGS. 7 and 8 compare the dynamic behavior of the two controls according to FIGS. 5 and 6. The reciprocal value of the reset time T _{i of} the drive is selected as a measure of the dynamics of the control. FIG. 7 shows the dynamics as a function of the mass inertia ratio from load to motor with identical coupling and identical phase reserve. This clearly shows that the control according to FIG. 6 with the actual value detection on the load is clearly superior to the actual value detection on the motor, in accordance with FIG.

8 shows the dynamics as a function of the torsional rigidity of the coupling 24 constant mass inertia ratio and identical phase reserve. Here 6 is particularly evident when the coupling has low torsional stiffness superior to the conventional control according to FIG. 5.

9 finally shows the control diagram of the controller 23. The setpoint and the actual value, in the exemplary embodiment the setpoint or actual center position of a blanket cylinder 2, are fed to a first differential amplifier 31 to form the difference between the setpoint and actual value. The difference D ₁ formed there is fed to a first proportional amplifier 34 and applied to a second differential amplifier 35 as a proportionally amplified signal K ₁ XD ₁ . In parallel, the setpoint and the actual value are each fed to a differentiating element 32 or 33, differentiated and the corresponding output signals S _s and S _{i are} fed to the second differential amplifier 35. The sum k ₁ D ₁ + S _s - S _{i formed there} is amplified in a second proportional amplifier 36 and fed to a current regulator for the motor 5 via an integrating element 37.

FIG. 10 shows a pressure point which is formed by three cylinder groups 10. A first cylinder group 10 is on one printing side of the paper web 1, and a second and a third cylinder group 10 are on the opposite pressure side thereof Paper web 1 arranged. The two on the same print side of paper web 1 arranged cylinder groups 10 are mutually on the rubber cylinder 2 of the first Cylinder group 10 adjustable. This is indicated by two straight arrows W. there are the two upper cylinder groups 10, which are approximately horizontally opposite each other a cylinder unit 20 summarized and as such independent in the machine frame supported by the lower cylinder group 10. Each cylinder group 10 is again from an engine 5, as is already the case with the two cylinder groups 10 of FIG. 1 has been individually driven.

This arrangement enables the on-the-fly change of production at continuous Continuous paper web 1. One of the two swiveling rubber cylinders 2 is pivoted away while the other is in the pressure position to the opposite Rubber cylinder 2 of the first cylinder group 10 stands. The production change takes place in known way by changing the plates of the pivoted Blanket cylinder 2 assigned plate cylinder 3rd

Figure 11 shows an alternative pressure point also with three cylinder groups 10. Das for the arrangement of FIG. 10, what has been said in principle also applies to the arrangement of FIG 11. While the three cylinder groups 10 of the arrangement of Figure 10 each Form legs of a "Y", the cylinder groups 10 of Figure 11 form an upside down standing "Y" or a "Lambda". In the arrangement according to FIG. 11, the two are lower, horizontally opposite cylinder groups 10 in the Machine frame stored independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the assembly or cylinder unit 20.

The arrangements of Figures 10 and 11 show the high flexibility of the invention Formation of cylinder groups and the regulation of each according to the invention Cylinder group. The most varied can be done in a particularly simple manner Form pressure points by, for example, cylinder units 20 with cylinder groups 10 (Fig. 10 and 11) or a plurality of cylinder units 20 are arranged one above the other (Fig. 1). In principle, the cylinders of the arrangements according to FIGS. 10 and 11 can also be coupled in a different way than that according to FIGS. 1 to 4, for example via a single gear.

Claims (14)

Rotary printing press a) with blanket cylinders (2), which form pressure points with impression cylinders (2; 4) or a common impression cylinder (6), and b) with plate cylinders (3), which are combined with the rubber blanket cylinders (2) in pairs by mechanical coupling for their drive to form cylinder groups (10), c) the cylinder groups (10) each being driven by a separate drive motor (5) during printing,
characterized in that d) in each of the cylinder groups (10) the blanket cylinder (2) or the plate cylinder (3) by means of a toothed belt (11) or gear drive from the drive motor (5) of the cylinder group (10) and driven by this cylinder (2) on the another of the cylinders (3) of the cylinder group (10) is driven off. Rotary printing machine according to claim 1, characterized in that the common impression cylinder is a central cylinder (6) of a cylinder unit (20) with a plurality of cylinder groups (10), which is provided with its own drive motor (5) or mechanically connected to one of the blanket cylinders (2 ) is coupled with which it forms pressure points. Rotary printing machine according to claim 1, characterized in that a cylinder unit (20) with a plurality of cylinder groups (10) has two central cylinders (6), each of which is provided with its own drive motor (5). Rotary printing machine according to one of the preceding claims, characterized in that the rotary printing machine is a wet offset rotary printing machine. Rotary printing machine according to one of the preceding claims, characterized in that the drive motors are electrical asynchronous motors. Rotary printing machine according to one of the preceding claims, characterized in that at least one inking roller (7) of an inking unit or of an inking and dampening unit which is assigned to a cylinder group (10) is mechanically coupled to this cylinder group (10) or that at least for the drive an inking roller (7) of such an inking unit has its own drive motor (5). Rotary printing machine according to the preceding claim, characterized in that a toothed belt (15) is used for the coupling between the drive motor (5) and the driven inking roller (7). Rotary printing machine according to one of the preceding claims with a control of the position and / or the speed of a cylinder group (10) driven by the drive motor (5) with a setpoint value transmitter (22), an actual value transmitter (21) and one Controller (23) for the drive motor (5), characterized in that the actual value transmitter (21) detects the position and / or the speed of a cylinder (2, 3) of the cylinder group (10). Rotary printing machine according to the preceding claim, characterized in that an actual value output by the actual value transmitter (21) forms the main control variable for the controller (23). Rotary printing machine according to claim 8 or 9, characterized in that no mechanical actual value transmitter, preferably no mechanical actual value transmitter for detecting the position or the speed of the drive motor (5) is provided for the control. Rotary printing machine according to one of claims 8 to 10, characterized in that a mechanical transmitter is provided on the drive motor (5), the output signal of which is used as an input signal for an emergency shutdown of the drive motor (5). Rotary printing machine according to one of claims 8 to 11, characterized in that the actual value transmitter (21) of the control is attached to the torque-free shaft end of the cylinder (2; 3) driven by the drive motor (5). Rotary printing machine according to one of the preceding claims, characterized in that three cylinder groups (10) form a printing point, one of the three cylinder groups (10) being arranged on one printing side and the other two cylinder groups (10) being arranged on the opposite printing side of a paper web (1) are. Rotary printing machine according to the preceding claim, characterized in that two horizontally opposite cylinder groups (10) of the three cylinder groups (10) are combined to form a cylinder unit (21) and as such are mounted in a machine frame independently of the third cylinder group (10).

Images