EP0644048B1 - Rotary printing machine with blanket- and plate cylinders arranged in cylinder units in couples - 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.

Conventional rotary printing machines are powered by a main drive mechanical longitudinal shaft, also called the king shaft, driven. A disadvantage this printing press is the mechanical effort to compensate the torsion of the longitudinal shaft that occurs during the run. This will make one mechanical circumferential register adjustment of printing points of the printing press necessary during the run.

In one printing press known from DE 3409194 A1 with several A printing motor is provided for printing units for more than one printing unit. This The motor can drive the drive gear of one of the printing units be directly connected, but the drive gears are the other Mechanical printing units with the drive gear connected to the motor coupled.

An attempt is also made to establish the mechanical longitudinal shaft between the individual printing units to be replaced by an electrical longitudinal shaft. Each printing unit receives a separate electric drive. To the high mechanical effort because of the complexity of the individual printing units with multiple printing points In this case, there is still a high level of control technology to be operated Effort added because the synchronous operation of the individually driven printing units among themselves must also be ensured. Such orders are known from GB-A 2 266 629 and DE-AS 11 46 959.

To avoid the problems mentioned, DE 41 38479 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 machine is included known individually driven cylinders. The individual drives can the cylinder and its drive controller can be combined into pressure point groups as required become. The pressure point groups are assigned to folders, by to whom they get their position reference. The proposed guidance system consists of essentially from a fast BUS system for the individual drives and Drive controller of a pressure point group and a higher-level control system for Administration of pressure point groups.

The individually driven concept pursued in these two publications Cylinder allows a high degree of flexibility, but at the same time requires a very high number of drive motors and, as shown in DE 42 14 394 A1, a high level of regulation for this large number of individual drives. Furthermore a variety of motors must be used. When using only Otherwise, fewer motor sizes would often be the case for different applications use oversized motors. Both drive the price of such a printing press.

A printing machine known from JP-A-63236651 has printing units which are individually driven by their own drive motors. The engines are driving each on the plate cylinders of the printing units, and from the plate cylinders driven on the printing cylinders via gear couplings.

From DE-OS 2134397 is a printing unit for an offset printing press Cylinder pairs are known, each of the cylinder pairs having a plate and one Includes blanket cylinder and the pairs of blanket cylinders in each other Plant can be brought. In addition to at least two such pairs of cylinders a third comprising a plate cylinder and a blanket cylinder Cylinder pair provided, its blanket cylinder to one of the two Blanket cylinder of the aforementioned two pairs of cylinders is arranged to be applied. Nothing is disclosed in this document about the drive of the cylinders.

In contrast, the present invention has set itself the task of a highly flexible, yet economical rotary printing press create.

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

The subclaims are appropriate and not self-evident Embodiments of the subject of claim 1 directed.

According to the invention, blanket cylinders and plate cylinders form a rotary printing press in pairs a cylinder group, each with a blanket cylinder and a plate cylinder are mechanically coupled together and together are driven by a separate drive motor for each cylinder group.

Through this grouping of the two cylinders and their Equipped with a single drive for at least one pair of cylinders Number of drive motors required significantly reduced; at least halved compared to the individual drive concepts. The mechanical coupling of these two cylinders associated with each other in terms of printing technology, preferably a gear coupling with straight or helical toothed gears, offers compared to the concept the individually driven cylinders have significant price advantages. With regard to the Versatility is of no importance compared to the single drive concept to make falling smears. So both the circumferential register and the Lateral register adjustment of each blanket cylinder individually and for each additional one any blanket cylinder, if necessary, made coordinated become. By the cylinder groups according to the invention, each with its own Drive motors can be more technical and economical in a rotary printing press Optimal pressure points are formed. As pressure points in this context understood the pairs of cylinders, between which one Paper web to be printed runs through and printed on one or both sides becomes. Accordingly, each belong to a pressure point formed according to the invention a cylinder group and a corresponding impression cylinder. In the latter case, a Pressure point formed by two cylinder groups assigned to each other. Drive technology However, the printing points of the printing press are inherent mechanically independent, d. H. the printing points of the printing press are electrical coupled with each other.

In the cylinder groups according to the invention, the blanket cylinder driven, which in turn via the mechanical coupling to the Drives plate cylinders of the same cylinder group. The blanket cylinder is decisive for the positional accuracy or circumferential register setting. The drive on the blanket cylinder has the advantage that the cylinder, ultimately with a printable Paper web comes into direct contact, not only with a game affected transmission link must be driven.

It is advantageous to work three cylinder groups at a time on one pressure point to let. A cylinder group is on one pressure side, and two cylinder groups are on the opposite pressure side of a continuous between Paper web arranged. Preferably, the rubber cylinder forms the one Printing side of the paper web arranged cylinder group the impression cylinder for the other two rubber cylinders on the opposite pressure side of the Paper web arranged cylinder groups, both advantageously each can be operated alternately. This configuration offers the highest Flexibility of use for a rubber / rubber production because of continuous production the two mutually usable rubber cylinders for converting the Pressure can be configured. This is done by changing the plate plate cylinder not assigned to non-employed rubber cylinders. Every cylinder group can be stored in a single frame. Preferably the two are one Printing side of the paper web horizontally opposite cylinder groups to one summarized in a frame mounted cylinder unit.

The impression cylinder can a steel or another blanket cylinder for double-sided printing. Such an impression cylinder can in particular also be a central cylinder Be cylinder unit with, for example, nine or ten cylinders. In a preferred embodiment of the invention is such a Central cylinder powered by its own drive motor. That kind of Summary provides the greatest versatility for a cylinder unit. In this case, each of the cylinder groups assigned to the central cylinder can made of blanket and plate cylinders individually and independently of the others Cylinder groups can be reversed, such as for alternating pressure or is required for the flying plate change.

The output from a drive motor takes place on the respective cylinder group by means of a toothed belt. Opposite that in DE 41 38 479 A1 proposed solution of the on the drive shaft of the driven cylinder such a toothed belt has a high elasticity in the seated rotor of the electric motor. For the control concept of the drive of a cylinder group, however, is by the use of a toothed belt gives the possibility of high damping the mechanical consisting of a drive motor and the driven cylinders Systems of great value, as will be explained. Opposite a gear drive between the drive motor and the driven cylinder of a group of cylinders a toothed belt has the advantage of a play-free run and one not absolutely fixed gear ratio

In contrast, are for the mechanical coupling between the cylinders inside A group of cylinders provided gears, although other transmission links are also conceivable. The intermeshing gears can be straight or helical. With helical gears, the Lateral register adjustment of the blanket cylinders moved longitudinally while its Drive and / or driven gears remain stationary according to the invention. Otherwise a circumferential register adjustment would also be necessary with the side register. At Using straight toothed gears, the blanket cylinder is used together with its fixed gear or its gears simply moved longitudinally.

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 be 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 in the In terms of the modular principle pursued by the invention, not quite as ideal as that more preferred self-drive for the roller or the rollers of the inking unit. According to this likewise preferred embodiment of the invention, each has Inking unit has its own drive motor for its inking rollers. Such a drive motor also drives preferably over a backlash-free toothed belt with high Damping and, if necessary, the inking roller via a reduction gear or in the case of several inking rollers, the one corresponding to the plate cylinder Ink roller closest to the cylinder group. Here is the peripheral speed this ink roller advantageously adjustable, especially with negative slip against the plate cylinder, the peripheral speed the inking roller is preferably slightly less than that of the corresponding plate cylinder is.

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 individual cases, a large, i.e. H. powerful motor with a relatively high mass moment of inertia compared to the load. Such systems throw in terms of mastering vibrations and shocks no major problems, since the load is carried by the motor becomes. If the moment of inertia of the driven loads increases, whose moments of inertia are often more than five times greater than those of the driving Vibration problems increase, however, as motors. Accordingly The regulations of these motor / load systems are becoming more complex. The Elasticity of a coupling between the motor and the load further contributes Exacerbating the problems with.

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 their dynamic limits. If the actual position is measured on the motor shaft, so both the coupling and the mechanical load lie outside the actual control loop. However, you can do this via the acceleration torques that affect the motor shaft influence. 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. With suggestion The set springs are tensioned first by the motor are closest. The engine torque caused by the controller accelerates parts of the coupling and subsequently the cylinder or the driven roller. Energy is in the springs as well at this time stored in the mass movement, the division of which is constantly changing. Of the The motor may have assumed the correct position within a short time, but is again distracted by the occurring mass forces, resulting in a leads further control process. The system must go through a relatively slow one Controllers are controlled, stabilized.

The present invention has therefore also set itself the task of To create regulation with which the position and / or in a rotary printing press the speed of a cylinder or roller driven by a motor is optimized for performance and with a sufficiently high control quality, d. H. with regard to the Dynamics and the speed or position accuracy, can be regulated Regulation should be inexpensive and not too high demands on the coupling of engine and load, especially the torsional stiffness and zero backlash of the Make coupling.

At least the drive motors are preferably the same Printing side of a paper web working cylinder groups of a cylinder unit position controlled. So-called ideal position control is preferred, i.e. a instantaneous position control with following error. On this, out However, technical, desirable, complex type of position control can can also be dispensed with. A simple position control also provides one 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 is preferably carried out by means of a controller for the drive motor through the target / actual comparison of the output signals a setpoint generator and an actual value transmitter, this actual value transmitter the Position and / or the speed of the cylinder or the roller detected. In contrast to The known regulations for rotary printing presses thus become a load generator used for the regulation. In contrast, has so far been used in printing press construction a mechanical encoder on the motor side to record the motor speed or the rotor angular position of the motor for the target / actual comparison of the motor control used. With this conventional regulation, one encounters large inertia ratios from the load to the engine quickly to the dynamic limits. If the control becomes unstable, the engine starts to vibrate, while the load remains relatively calm.

In control technology, differential connections for so-called dual-mass oscillators are Regelkaskeden and active filters known, but all 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.

The drive motor can even with the dual mass transducer be disregarded. The load acting as a low-pass filter is insensitive against the vibrations of the much smaller motor. On the other hand the effects of the load on the drive motor can be neglected become. The, not least because of their simplicity inexpensive Regulation has the further advantage that it is simply the large bandwidth of the Mass inertia between the load and the motor and on itself in the course of Operating parameters, such as the elasticity of a coupling, can be adjusted.

By taking the actual value to be regulated from the load also measured what has to run exactly, namely the load, not the motor. The mechanical consisting of the drive motor, a coupling and the load Replacement system is to be regarded as a low-pass filter Low-pass filter of the motor coupling load-distance system exploited to shock and Filter vibrations that occur in the controlled system. Such bumps and Vibrations are thus returned to the controller to a reduced extent. The This reduces the risk of rocking. The dynamics of the scheme and thus the control quality can be compared to the conventional one described Regulation with identical coupling, can be increased significantly.

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 does not become a mechanical actual value transmitter for the acquisition the position or speed of the engine in the context of the regulation of the engine needed. Actual value detection, which may be integrated in the motor, can be advantageous for pure drive monitoring, if necessary for an engine emergency shutdown be used.

The actual value transmitter for the control is preferably 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 So far, an asynchronous motor has only been used when using of a large engine had to drive a small load. For the present case, in which a drive motor is a cylinder group or the rollers of a Inking unit drives, so the driven load is comparatively high Has moment of inertia compared to the drive motor is the use not known from asynchronous motors. For the purposes of Control with a load encoder instead of a motor encoder are asynchronous motors particularly suitable. Compared to that for the applications in question DC motors used so far have higher asynchronous motors Field stiffness on, so that their use the dynamics and quality of control to be controlled Systems improved. The use of other types of motor, for example DC motors, is however not fundamentally excluded.

The stability of the scheme is ensured by the use of a zero backlash Toothed belt with high damping as a coupling between the motor and the load improved.

The drive motor can even with the two-mass oscillator in question be disregarded. The load acting as a low-pass filter is insensitive against the vibrations of the much smaller motor. On the other hand the effects of the load on the drive motor can be neglected become.

With the concept of paired blanket and plate cylinders to cylinder groups will get maximum flexibility during the Price for a printing press organized in this way compared to a printing press can be significantly reduced with individually driven cylinders. For one out Printing presses composed of such cylinder groups become drive motors required in only two, at most three performance classes, while with direct and individually driven cylinders basically separate motors for cylinders with different lengths and diameters are required. By means of the Timing 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 translation and be coordinated. The reduction in the number of drive motors together with the advantage that motors are only available in a few performance classes must be provided already offers considerable price advantages. This advantage is by using the simple scheme, which is also Can be flexibly adapted to changing mass inertia ratios. The advantages achieved with the invention come with increasing Printing machines, d. H. with increasing number of printing units and printing points per machine, more and more to advantage. In particular, the invention is under construction use of offset rotary printing presses; but it is not on this Machine type limited.

Fig. 1

eine Druckstelle mit zwei Zylindergruppen;

Fig. 2

eine Zylindereinheit mit einem eigenangetriebenen Zentralzylinder und vier Zylindergruppen;

Fig. 3

eine Zylindergruppe mit einer zugeordneten, eigenangetriebenen Farbwalze;

Fig. 4

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

Fig. 5

eine bevorzugte Regelung für den Antrieb einer Zylindergruppe;

Fig. 6

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

Fig. 7

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

Fig. 8

ein Regeldiagramm des Reglers;

Fig. 9

eine aus drei Zylindergruppen gebildete Druckstelle in Y-Stellung;

Fig. 10

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

Fig. 3

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

Fig. 4

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

Fig. 5

a preferred control for driving a group of cylinders;

Fig. 6

a comparison of the dynamic behavior of a conventional control and a preferred control as a function of the mass moment of inertia ratio of motor and load;

Fig. 7

a comparison of the dynamic behavior of a conventional control and a preferred control as a function of the torsional rigidity of the coupling between the motor and the load;

Fig. 8

a control diagram of the controller;

Fig. 9

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

Fig. 10

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

At a printing point shown in Fig. 1 is a paper web to be printed 1 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, which are mechanically coupled to each other for the common drive. The mechanical coupling is shown schematically by a dash between the centers of the two cylinders 2 and 3 indicated. In the embodiment 1, the blanket cylinders 2 of each cylinder group 10 are through a three-phase motor 5 driven. The configuration according to Fig. 1, at of only one blanket cylinder 2 and one plate cylinder 3 by one mechanical coupling are combined to form a cylinder group 10 through their simple design and the highest possible degree of configuration freedom in the formation of pressure points or pressure point groups.

When driving the blanket cylinder 2, the cylinder printing directly on the paper web 1 is driven. As a result, a drive is free of transmission elements with play, such as, for example Gears, possible.

2 shows a cylinder unit 20 consisting of a central one Steel cylinders 6 and four cylinder groups 10 assigned to this central cylinder 6. A blanket cylinder 2 and a plate cylinder 3 are each in this embodiment combined into a cylinder group 10. For driving the Central cylinder 6 has its own three-phase motor 5. The summary shown in Fig. 2 on the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to a cylinder unit 20 offers the greatest possible flexibility in terms of configuration options. This configuration derived from the basic variants described above A cylinder unit 20 has the advantage in terms of printing technology that the so-called Fan-out effect very limited. Each of the blanket cylinders 2 is also easily switchable to rubber / rubber production. The possibilities Different types of alternating pressure will not be reversed either limited.

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

In Fig. 3, the interaction is one of a pair of blanket / plate cylinders 2, 3 existing cylinder group 10 shown with an ink roller 7. Here the inking roller 7 has its own drive by a motor 5, which too the engine 5 for the cylinder group 10 may be identical, but need not be. The motor 5 for the inking roller 7 drives via a toothed belt 15 and a pair of gearwheels 16, 17, wherein the gear 17 sits on the shaft of the ink roller 7, the Ink roller 7 on. The different moments of inertia of the motor 5 and the inking roller 7 are at a suitable choice of gear ratios Output via the toothed belt 15 and the gear pair 16, 17 disarmed.

The peripheral speed of the ink roller 7 is easily adjustable negative slip compared to the plate cylinder 3. This can increase the risk counteracted that the mechanical formed by a pair of gears 12, 13 Coupling between the blanket cylinder 2 and the plate cylinder 3 the tooth mesh is lifted.

The cylinder group 10 is driven by the motor 5 via the toothed belt 11 on the blanket cylinder 2. The mechanical coupling between the Form blanket cylinder 2 and plate cylinder 3 of the same cylinder group 10 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 via the toothed belt 11 accordingly stocky. This toothed belt 11 is the elastic coupling member between the Engine 5 and the driven cylinder group 10. Opposite one direct coupling or a gear coupling is with the Timing belt 11 achieved a very high damping of the motor / load system 5, 10. The The same applies in principle to the drive of the inking roller 7 and its coupling member, the toothed belt 15. Furthermore, by choosing a toothed belt drive a great constructive because of the continuously variable translation Free space created. The motors 5 for the cylinder group 10 or the inking roller 7 are three-phase motors with high field stiffness. Here too comes the modular principle of forming cylinder groups or roller groups with Toothed belt coupling to the drive motor to carry, since with fewer motor power sizes the entire variety of cylinder and roller lengths and - diameters equipped with different mass moments of inertia can be.

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 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 the toothed belt 11 stationary stay, i.e. these two gears are longitudinally displaceable on the cylinder shaft 14 stored. 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 sit firmly on the shaft 14 and are together with the blanket cylinder 2 and the motor 5 for the Cylinder group 10 moved longitudinally together.

In contrast to the regulations known in rotary printing press construction the motor / load system 5, 10 is guided by an actual value which is different from one Load side, namely at the torque-free end of the shaft 14 of the blanket cylinder 2 attached mechanical load generator 21 is generated. The same kind of Regulation, namely with an attached to the load-free shaft end of the ink roller 7 Load sensor 27 is selected for controlling the speed of this ink roller 7.

A control known in printing press construction is shown schematically in FIG. 4. The regulation of the motor 5, the load 25 via an elastic coupling 24 drives, takes place by means of a controller 23. The load 25 is a heavy roller or a heavy cylinder or a corresponding roller or cylinder system, the Mass moment of inertia typically more than five times that of the Motors 5 is. Nevertheless, the regulation of this motor / load system should optimize performance and with a sufficiently high control quality for the number of revolutions or the angular position and the speed of the load 25 are regulated. The coupling 24 of The engine and load are not too high in terms of their requirements Torsional rigidity and freedom from play.

In the known systems, such as one shown in Fig. 4, is a mechanical 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 on this rotor appropriate. The 25 is with the coupling 24, which is elastic and possibly has some play, attached to the motor shaft end. The coupling and the Load is outside the actual control loop. However, you can use this influence the acceleration torques acting back on the motor shaft.

This system pushes from load to load at high inertia Engine quickly to its dynamic limits. If the control becomes unstable, it vibrates especially the engine, while the load remains relatively calm.

5, on the other hand, shows a control in which, as already shown in FIG. 3, 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 free Shaft end of the load, in the exemplary embodiment at the free shaft end of the blanket cylinder 2 of a cylinder group 10 attached. This actual value transmitter 21 is in therefore called the following loader. The coupling 24 is already through the described toothed belt 11 with compared to a direct coupling or Gear coupling of high elasticity but also high damping. In addition is this coupling 24 with a toothed 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 represents, is returned to the controller 23. A computer generated setpoint from the setpoint generator 22 is compared with this actual value and for formation a control signal for the motor 5 used.

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 the in The controlled system creates shocks and vibrations, which are therefore only in are reduced in the controller 23 and therefore not can lead to unwanted suggestions of the regulation. This will make the Dynamics and also the control quality compared to conventional systems even with otherwise the same coupling significantly increased. The system, consisting of controller, The engine, clutch and cylinder are already much more damped. Resonance increases therefore do not occur to the same extent. The controller can 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. 5 The actual value acquisition shown can be used for additional monitoring of the motor 5. used for example in a desired emergency shutdown option of the engine 5 become.

The diagrams in FIGS. 6 and 7 compare the dynamic behavior of the two controls according to FIGS. 4 and 5. The reciprocal of the reset time T _{i of} the drive is selected as a measure of the dynamics of the control. 6 shows the dynamics as a function of the mass inertia ratio from load to motor with identical coupling and identical phase reserve. It can be clearly seen here that the control according to FIG. 5 with the actual value acquisition on the load is clearly superior to the actual value acquisition on the motor according to FIG.

7, the dynamics as a function of the torsional rigidity of the coupling 24 are constant mass inertia ratio and identical phase reserve. Here, the control according to FIG. 5 is particularly evident when the torsional stiffness is low Coupling superior to the conventional control according to FIG. 4.

8 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 fed 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 formed there k 1 D 1 + S s - p i is amplified in a second proportional amplifier 36 and supplied to a current regulator for the motor 5 via an integrating element 37.

FIG. 9 shows a pressure point which is formed by three cylinder groups 10. A first cylinder group 10 is on the one printing side of the paper web 1, and one second and third cylinder groups 10 are on the opposite pressure side this paper web 1 arranged. The two on the same printing side of the paper web 1 arranged cylinder groups 10 are mutually attached to the rubber cylinder 2 of the first cylinder group 10 adjustable. This is indicated by two straight arrows W. The two upper cylinder groups 10 are approximately horizontal opposite to form a cylinder unit 20 and as such in the Machine frame stored independently of the lower cylinder group 10. Each Cylinder group 10 is again driven by an engine 5, as is the case with the two Cylinder groups 10 of Figure 1 has been driven individually.

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 printing position to the opposite Rubber cylinder 2 of the first cylinder group 10 stands. The change of production takes place in a known manner by changing the plates of the pivoted Blanket cylinder 2 assigned plate cylinder 3rd

FIG. 10 shows an alternative pressure point also with three cylinder groups 10. The statements made regarding the arrangement of FIG. 9 also apply in principle to the arrangement of Figure 10. While the three cylinder groups 10 of the arrangement of Figure 9 each form the legs of a "Y", form the cylinder groups 10 of FIG. 10 an upside down "Y" or a "Lambda". In the arrangement according to the figure 10 are the two lower, horizontally opposite cylinder groups 10 stored in the machine frame independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the assembly or cylinder unit 20th

The arrangements of Figures 9 and 10 show the high flexibility of the invention Formation of cylinder groups and the preferred regulation each cylinder group. The most varied can be done in a particularly simple manner Form pressure points, for example by cylinder units 20 with cylinder groups 10 (FIGS. 9 and 10) or a plurality of cylinder units 20 arranged one above the other be (Fig. 1).

Claims (15)

1. A rotary printing press

   a) with blanket cylinders (2) which form print positions with counter-impression cylinders (2) or a common counter-impression cylinder (2), and

   b) with plate cylinders (3) which are each combined with the blanket cylinders (2) in pairs to form cylinder groups (10) by a mechanical coupling for driving them,

   c) the cylinder groups (10) each being driven during the printing by a separate drive motor (5) and the counter-impression cylinder (2; 6) for each of the the blanket cylinders (2) of the said cylinder groups (10) being driven by a different drive motor (5),
   characterized in that

   d) in each of the cylinder groups (10) the blanket cylinder (2) is driven by the drive motor (5) of the cylinder group (10) by means of a toothed belt (11), and power is taken off from the blanket cylinder (2) to the plate cylinder (3) of the cylinder group (10).
2. A rotary printing press according to Claim 1, characterized in that the common counter-impression cylinder is a central cylinder (6) of a cylinder unit (20) with a plurality of cylinder groups (10) which is provided with a separate drive motor (5).
3. A rotary printing press according to Claim 1 or 2, characterized in that at least one inking roller (7) of an inking mechanism or of an inking and damping mechanism, which is associated with a cylinder group (10), is coupled mechanically to the said cylinder group (10), or a separate drive motor (5) is provided for driving at least one inking roller (7) of an inking mechanism of this type.
4. A rotary printing press according to Claim 3, characterized in that a toothed belt (15) is used for the coupling between the drive motor (5) and the driven inking roller (7).
5. A rotary printing press according to one of the preceding Claims, with a control of the position and/or the rotational speed of a cylinder group (10) driven by the drive motor (5) and having a set-value transmitter (22), an actual-value transmitter (21) and a controller (23) for the drive motor (5), characterized in that the actual-value transmitter (21) detects the position and/or the rotational speed of a cylinder (2, 3) of the cylinder group (10).
6. A rotary printing press according to Claim 5, characterized in that an actual value emitted by the actual-value transmitter (21) forms the main command variable for the controller (23).
7. A rotary printing press according to Claim 5 or 6, characterized in that no mechanical actual-value transmitter is provided for the control, and preferably no mechanical actual-value transmitter is provided for detecting the position and/or the rotational speed of the drive motor (5).
8. A rotary printing press according to one of Claims 5 to 7, 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 shut-down of the drive motor (5).
9. A rotary printing press according to one of Claims 5 to 8, characterized in that the actual-value transmitter (21) of the control is attached to the moment-free end of the shaft of the blanket cylinder (2) driven by the drive motor (5).
10. A rotary printing press according to one of the preceding Claims, characterized in that a cylinder unit (20) with a plurality of cylinder groups (10) comprises two central cylinders (6) which are provided with one respective separate drive motor (5).
11. A rotary printing press according to one of the preceding Claims, characterized in that three cylinder groups (10) form a print position.
12. A rotary printing press according to Claim 11, characterized in that one cylinder group (10) is arranged on one printing side and two cylinder groups (10) are arranged on the opposite printing side of a web (1).
13. A rotary printing press according to Claim 11 or 12, characterized in that the blanket cylinder (2) of the cylinder group (10) arranged on one printing side of a web (1) forms the counter-impression cylinder for the two blanket cylinders (2) - which can be used alternately - of the cylinder groups (10) arranged on the opposite printing side of the web (1).
14. A rotary printing press according to one of Claims 11 to 13, characterized in that the two cylinder groups (10) horizontally opposite each other are combined to form a cylinder unit (21), and are mounted as such in a machine frame independently of the third cylinder group (10).
15. A rotary printing press according to Claim 14, characterized in that the cylinder unit (21) is arranged in a Y-shape or a Λ-shape with the third cylinder group (10).

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