EP0644048B2 - 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 abstract of cylinders of a rotary printing machine to individual cylinder groups.

Conventional rotary printing machines become from a main drive via a mechanical one Propeller shaft, also known as king shaft, driven. A disadvantage of these printing machines is the one to be operated mechanical effort to compensate for during the run occurring torsion of the longitudinal shaft. This will be a mechanical circumferential register adjustment from pressure points of the printing press during of the run necessary.

In a known from DE 3409194 A1 Printing machine with multiple printing units is a Drive motor provided for more than one printing unit. Although this engine can with the drive gear of a be directly connected to one of the printing units, however, the drive gears are the other printing units with the drive gear connected to the motor mechanically coupled.

It also tries the mechanical Longitudinal shaft between the individual pressure units to be replaced by an electric longitudinal shaft. in this connection each printing unit receives a separate electrical Drive. To the high mechanical effort, the because of the complexity of the individual printing units continue to operate with several pressure points is, comes in this case still a high regulatory technical Added effort, since the synchronous operation of the individually driven Printing units with each other also must be ensured. Such arrangements are made GB-A 2 266 629 and DE-AS 11 46 959.

To avoid the mentioned problems will proposed in DE 41 38479 A1, the cylinder of the Pressing machine to drive by one electric motor.

From DE 42 14 394 A1 is a control system for such a printing machine with each one individually driven cylinders known. The can Single drives of the cylinders and their drive controllers too Groups of pressure groups are summarized as desired. The groups of printing groups become folders from which they refer their position reference. The proposed control system consists in essential from a fast bus system for the Single drives and the drive controllers of a print station group and a superordinate control system for Management of print group groups.

The pursued in these two pamphlets Concept of individually driven cylinders allows Although a high versatility, but requires at the same time a very high number of drive motors and, as DE 42 14 394 A1 shows a high regulatory burden for this large number of individual drives. In addition, a variety of motors must be used become. When using only a few engine sizes otherwise would be different Applications often use oversized motors. Both drive the price of such a printing press.

A printing machine known from JP-A-63236651 has printing units that individually through own drive motors are driven. The motors each drive on the plate cylinders of the printing units, and from the plate cylinders is over Gear coupling on the printing cylinder further driven.

From DE-OS 2134397 a printing unit for an offset printing press with cylinder pairs known wherein each of the pairs of cylinders a plate and a Blanket cylinder covers and the blanket cylinder the pairs are mutually engageable. In addition, at least two such pairs of cylinders a plate cylinder and a blanket cylinder comprehensive third cylinder pair provided its blanket cylinder to one of the two blanket cylinder the aforementioned two pairs of cylinders can be arranged applied. About the drive of the cylinders is not disclosed in this document.

In contrast, the present invention has it the task, a highly flexible usable, nevertheless economical rotary printing machine to accomplish.

This task is accomplished by the subject of claim 1.

The dependent claims are on expedient and not obvious obvious embodiments of the subject matter of claim 1.

According to the invention form blanket cylinder and plate cylinder of a rotary printing machine in pairs a cylinder group, in each case one Blanket cylinder and a plate cylinder mechanically coupled together and together through a separate drive motor per cylinder group driven become.

Through this groupwise summary the two cylinders and their equipment with a single drive for at least one pair of cylinders is the Number of required drive motors significantly reduced; at least halved compared to the single drive concepts. The mechanical coupling of these two each cylinder technically assigned to printing, preferably a gear coupling with straight or helical gears, offers over the Concept of each individually driven cylinder significant price advantages. In terms of deployment flexibility are compared to the single drive concept no ins To make weight falling cuts. So can both the circumferential register and the side register adjustment each blanket cylinder individually and to any other blanket cylinder, if necessary, be made coordinated. By the cylinder groups according to the invention each with their own drive motors can at a rotary printing machine in technical and economic Regard optimal pressure points formed become. As pressure points are in this context each understood the cylinder pairs, between where a paper web to be printed passes and printed on one or both sides. Therefore belong to a pressure point formed according to the invention each one cylinder group and a corresponding one Impression cylinder. In the latter case will a pressure point by two associated with each other Cylinder groups formed. Drive technology are However, the pressure points of the printing machine in itself mechanically independent, d. H. the pressure points of the Printing press are electrically coupled together.

In the cylinder groups according to the invention the blanket cylinder is driven, which in turn via the mechanical coupling to the plate cylinder aborts the same cylinder group. Of the Blanket cylinder is decisive for the positional accuracy or scope register setting. The drive up the blanket cylinder has the advantage that the Cylinder, ultimately with a paper web to be printed comes into direct contact, not just about one possibly game-related transfer element must be driven.

It is advantageous, in each case three cylinder groups to work on a pressure point. A cylinder group is on one pressure side, and two cylinder groups are on the opposite pressure side arranged between a running paper web. Preferably, the blanket cylinder forms the arranged a printing side of the paper web Cylinder group the impression cylinder for the two another blanket cylinder at the opposite Pressure side of the paper web arranged cylinder groups, the two advantageously each can be operated alternately. This configuration offers the highest versatility for one Rubber / rubber production because of continuous production the two mutually usable rubber cylinders configured to change the pressure can be. This is done by plate change one assigned to the unattached blanket cylinder Plate cylinder. Each cylinder group can be in be stored a single frame. Preferably the two of a printing side of the paper web horizontally opposite cylinder groups to one in one Frame mounted cylinder unit summarized.

The impression cylinder can be a steel or also another blanket cylinder for both sides Be pressure. Such an impression cylinder can in particular also a central cylinder of a cylinder unit with, for example, nine or ten cylinders. In a preferred embodiment of the invention becomes such a central cylinder of its own Drive motor driven. This kind of summary grants the highest versatility for one Cylinder unit. So in this case, each of the Central cylinder assigned cylinder groups Blanket and plate cylinder individually and independently be reversed by the other cylinder groups, as for example for alternating pressure or for the flying plate change is required.

The output of a drive motor on the respective cylinder group takes place by means of a toothed belt. Compared to those proposed in DE 41 38 479 A1 Solution of on the drive shaft of the powered cylinder of sitting rotor of the electric motor Such a timing belt has a high elasticity. For the control concept of the drive one Cylinder group, however, is the one through use a belt given possibility of a high Damping of a drive motor and the driven cylinders existing mechanical Systems of great value, as will be explained. Opposite a gear drive between the Drive motor and the driven cylinder one Cylinder group has a toothed belt the advantage a backlash-free run and a not absolutely solid ratio

In contrast, for the mechanical Coupling between the cylinders within a cylinder group Gears are provided, though others Transmission elements are also quite conceivable. The mutually meshing gears can be straightforward or be helical. For helical gears becomes the side register adjustment of the blanket cylinder moved along while his Drive and / or driven gears according to the invention stay stationary. Otherwise, using the page register also a circumferential register adjustment required. When using spur gears the blanket cylinder becomes together with his firmly attached gear or its gears simply moved longitudinally.

The ink roller or the ink rollers or Dampening rollers of an inking unit or a color and Dampening unit, which is assigned to a cylinder group, can or can be mechanical with this cylinder group be coupled so that the ink roller or the Ink rollers from the drive motor of this cylinder group be driven with. Through this solution, the Reguleckchnische effort to be kept low. On the other hand, the mechanical coupling of the inking unit in the sense of the modular principle pursued by the invention not quite as ideal as the stronger one preferred self-propelled for the roller or rollers of the inking unit. After this also preferred Embodiment of the invention has every inking unit its own drive motor for its ink rollers. Such a drive motor also drives preferably about a backlash-free timing belt with high Damping and optionally via a reduction gear transmission the ink roller or in case of several Ink rollers the plate cylinder of the corresponding Cylinder group nearest ink roller at. Here is the peripheral speed of this ink roller advantageously adjustable, in particular with negative slip against the plate cylinder, wherein the peripheral speed of the ink roller preferably slightly lower than that of the corresponding Plate cylinder is.

Special problems prepares the scheme a motor / load system with a drive motor for a cylinder or a roll of a rotary printing machine. In some cases, a small loads great, d. H. powerful engine with one opposite the load comparatively high moment of inertia used. Such systems are concerning the control of vibrations and shocks not too big problems, because the load from the engine forcibly carried. With increasing Moment of inertia of the driven loads, their moments of inertia often more than five times can be larger than those of the driving engines, However, the vibration problems increase. Accordingly the regulations of these become more complex Motor / load systems. The elasticity of a coupling between the engine and the load further contributes to the tightening the problems with.

In printing press construction regulations are the Location or the speed of a cylinder known at which a mechanical encoder on the engine side to Detection of the engine speed or the rotor angle position of the engine for a nominal / actual comparison of the engine control is used. This known control encounters however, with increasing mass inertia ratios from the load to the engine increasingly to her dynamic limits. Is the actual position at the Motor shaft measured, so are both coupling than also mechanical load outside of the actual Control loop. You can do this over the the motor shaft retroacting acceleration torques influence. The engine, which in this case a much smaller mass than the coupling and the Cylinder has, is thereby significantly influenced. There the resulting engine load from a mechanical Structures of masses, springs and damping exists, the load torque is strongly frequency-dependent, ultimately, the dynamic behavior of the system certainly. When excited by a setpoint changes First, the springs are tensioned, which the engine are closest. That caused by the regulator Motor torque accelerates parts of the coupling and subsequently the cylinder or the driven roller. Energy is at this time both in the springs and in the mass movement stored, the distribution of which is constantly changing. Of the Motor likes the correct position within a short time However, it is caused by the occurring Mass forces again distracted, resulting in a further control action leads. The system must, by controlled a relatively slow regulator, stabilized become.

The present invention is therefore also set the task of creating a system with the situation with a rotary printing press and / or the rotational speed of a cylinder or a Roller driven by a motor, performance optimized and with sufficiently high control quality, d. H. in terms of dynamics and speed - or Positional accuracy, can be regulated The scheme should be cheap and not too high requirements to the coupling of engine and load, in particular to the torsional stiffness and backlash of the coupling put.

Preferably, at least the Drive motors on the same pressure side of a Paper web working cylinder groups of a cylinder unit position control. Preference is given to a so-called ideal attitude control, i. a Delay-free position control with following error connection. On this, for technical reasons desired, complex type of position control can but also be waived. A simple one Position control is also a preferred, in particular cheaper, embodiment of the invention represents.

The regulation of the position and / or the speed of the cylinder to be controlled a cylinder group or a roller of an inking unit is preferably carried out by means of a regulator for the drive motor by the Target / actual comparison of the output signals of a setpoint encoder and an actual value encoder, this actual value encoder the position and / or the speed of the cylinder or the roller detected. In contrast to the known ones Regulations with rotary printing machines is thus a loader used for the scheme. In contrast, So far, it has been a mechanical one in press engineering Encoder on the motor side for detecting the Motor speed or the rotor angle position of the motor for used the target / actual comparison of the engine control. at This conventional control can be found at large Mass inertia ratios of the load to the motor quickly to the dynamic limits. Will the scheme unstable, especially the engine starts to swing, while the load stays relatively calm.

In control engineering are for so-called Dual-mass differential switching, Regelkaskeden and active filters known, however all require a great regulatory effort. For the load / motor systems described above, d. H. the self-propelled cylinder groups, Surprisingly, it has been completely sufficient proved the scheme essentially by means of an actual value to be guided by one at the load, namely on one of the cylinders of a cylinder group, attached actual value encoder has been determined.

The drive motor can in the two-mass oscillator even disregarded. As Low-pass filter acting load is insensitive to the Vibrations of contrast, much smaller Engine. On the other hand, the repercussions neglected by the load on the drive motor. The, not least because of their simplicity inexpensive Regulation offers the further advantage that they also simply the wide range of inertia ratios between load and engine and on itself during operation, changing parameters, such as the elasticity of a coupling, set can be.

By the actual value to be controlled at the load is also measured, what exactly must run, namely the load, not the engine. The end the drive motor, a coupling and the load existing mechanical replacement system is as a low-pass filter In this type of regulation, that will be Low pass filter of the motor coupling load distance system exploited to shocks and vibrations that arise in the controlled system to filter. Such shocks and vibrations are thus reduced returned to the controller. The danger of a Aufschaukelung is thereby reduced. The dynamics of Control and thus the control quality can thereby compared to the described conventional Control with identical coupling, significantly increased become.

The figuratively speaking from the engine side to Loaded actual value encoder forms the main controlled variable for the governor of the engine, d. H. the engine becomes from the load side by their actual value. To a particularly preferred embodiment No mechanical actual value encoder for the acquisition of the Position or speed of the engine in the context of Regulation of the engine needed. An optionally in the Motor integrated actual value detection can be beneficial for the pure drive monitoring, if necessary for a motor emergency shutdown can be used.

The actual value encoder for the control is preferably at the torque-free shaft end of the driven Cylinder of a cylinder group or the mounted driven roller of an inking unit.

Particularly advantageous are electrical Asynchronous motors used as the drive motors, So far, an asynchronous motor has only been used if by means of a big engine a small load was to drive. For the present case, in which a Drive motor, a cylinder group or the rollers an inking unit drives, so in which the driven Load a comparatively high mass moment of inertia opposite the drive motor owns, is the use of asynchronous motors not known. For the purposes of the scheme with a Loaders instead of a motor encoder are asynchronous motors particularly suitable. Opposite to those for the applications used so far DC motors have asynchronous motors higher field stiffness, so that their use the momentum and control quality of the system to be controlled improved. The use of other engine types, For example, DC motors, but is not basically excluded.

The stability of the scheme is determined by the use a backlash-free timing belt with high Damping as coupling between motor and load additionally improved.

The drive motor can in the case in question Two-mass oscillator even disregarded become. The load acting as a low-pass filter is insensitive to the vibrations of the other hand much smaller engine. On the other hand the repercussions from the load on the Drive motor are neglected.

With the concept of pairwise summary from blanket and plate cylinders to cylinder groups will be given maximum flexibility, while the price of such an organized printing press opposite a printing press with individually driven cylinders are lowered significantly can. For one composed of such cylinder groups Printing press become drive motors needed in only two, at most three performance classes, while being driven directly and individually Cylinders basically each separate engines for Cylinders with different lengths and diameters required are. By means of the invention used Zahnriemenriebs may possibly within wide limits fluctuating mass moment of inertia between the load and the Engine collected by appropriate choice of translation and be coordinated. The Reduce the number of drive motors together with the advantage that engines only in a few Power classes must be provided already significant price advantages. This advantage will through the use of the simple scheme that also on changing inertia conditions flexibly adaptable even more. Here they come with The invention achieved advantages with increasing Printing machines, d. H. with increasing number of Printing units and pressure points per machine, always more effective. In particular, the invention is in 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 Zylindereinheit mit einem eigenangetriebenen Zentralzylinder und vier Zylinder-gruppen;

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 embodiments of the present invention will be explained below with reference to the figures. In this case, 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 inking roller;

Fig. 4

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

Fig. 5

a preferred control for the drive of a cylinder group;

Fig. 6

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

Fig. 8

a control diagram of the regulator;

Fig. 9

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

Fig. 10

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

In a pressure point shown in Fig. 1 is a paper web 1 to be printed between the two mutually opposite blanket cylinders 2 of two cylinder groups 10 passed. The both cylinder groups 10 are each through the Blanket cylinder 2 and an associated plate cylinder 3 formed for the common drive mechanically coupled together. The mechanical Coupling is schematically represented by a connecting line between the centers of the two Cylinder 2 and 3 indicated. In the embodiment 1, the blanket cylinder 2, respectively Each cylinder group 10 by a three-phase motor. 5 driven. The configuration according to FIG. 1, in each case only a blanket cylinder 2 and a Plate cylinder 3 by a mechanical coupling to a cylinder group 10 are summarized, draws through their simple design and the highest possible Degree of configuration freedom in the Formation of pressure points or pressure point groups out.

When driving the blanket cylinder 2 is the cylinder directly printing on the paper web 1 driven. As a result, a drive is free of play Transmission links, such as gears, possible.

2, a cylinder unit 20 is shown, consisting of a central steel cylinder 6 and four, this central cylinder 6 associated cylinder groups 10. In each case a blanket cylinder 2 and a Plate cylinder 3 are in this embodiment too a cylinder group 10 summarized. For the Drive of the central cylinder 6 is a separate three-phase motor 5 provided. The illustrated in Fig. 2 Summary of the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to a cylinder unit 20 offers the highest possible Flexibility in terms of configuration options. These of the basic variants described above derived configuration of a cylinder unit 20 has the technical advantage that the so-called Fan-out effect is very limited. Everyone who Blanket cylinder 2 is also easy on Rubber / rubber production reversible. The possibilities on different types of alternating pressure to redirect are also not limited.

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

In Fig. 3, the interaction of a a rubber blanket / plate cylinder pair 2, 3 existing Cylinder group 10 shown with a paint roller 7. Here, the ink roller 7 has a own drive by a motor 5 leading to the engine 5 for the cylinder group 10 may be identical, but does not have to be. The motor 5 for the ink roller 7 drives via a toothed belt 15 and a pair of gears 16, 17, wherein the gear 17 on the shaft of the ink roller. 7 sits, the ink roller 7 on. The different mass moments of inertia the motor 5 and the ink roller 7 will be through appropriate choice of gear ratios when driven over the timing belt 15 and the gear pair 16, 17 defused.

The peripheral speed of the ink roller 7 is adjustable with a slight negative slip opposite the plate cylinder 3. This can be the danger be counteracted that by a gear pair 12, 13 formed mechanical coupling between the blanket cylinder 2 and the plate cylinder. 3 is lifted from the tooth mesh.

The drive of the cylinder group 10 is carried out by the engine 5 via the timing belt 11 on the blanket cylinder 2. The mechanical coupling between the blanket cylinder 2 and the plate cylinder. 3 the same cylinder group 10 form the two gears 12 and 13. To defuse a high ratio the moments of inertia of load and Drive, namely cylinder group 10 and engine 5, is the rotational speed of the motor 5 via the toothed belt 11th appropriately stocky. This timing belt 11 is the elastic coupling member between the engine 5 and the driven cylinder group 10. Opposite a direct coupling or a gear coupling is with the timing belt 11 a very high attenuation of Motor / load system 5, 10 scored. The same goes for basically also for the drive of the ink roller 7 and its coupling member, the toothed belt 15. Ferner is determined by the choice of a toothed belt drive because of infinitely variable translation a great constructive Freedom created. The engines 5 for the cylinder group 10 and the ink roller 7 are respectively Three-phase motors with high field stiffness. Also Here comes the modular principle of the formation of cylinder groups or roller groups with toothed belt coupling to the drive motor for carrying, as with less Motor performance variables the entire variety variety of cylinder or roller lengths and diameters with correspondingly different mass moments of inertia can be equipped.

The two gears 12 and 13, the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 can form be helical or spur toothed gears. In the case of helical gears, the blanket cylinder 2 longitudinally displaced in the Seitenregisterverstellung, while the gear 12 and the corresponding gear for the timing belt 11 stationary stay, i. These two gears are on the cylinder shaft 14 mounted longitudinally displaceable. In case of a Straight toothing of the two gears 12 and 13 sit the gear 12 and the gear for the timing belt 11 stuck on the shaft 14 and get together with the blanket cylinder 2 and the motor 5 for the Cylinder group 10 is moved longitudinally together.

In contrast to those in rotary printing machine construction known regulations will that Motor / load system 5, 10 guided by an actual value, that of one on the load side, namely on the torque-free End of the shaft 14 of the blanket cylinder 2 mounted mechanical loader 21 generates becomes. The same kind of regulation, namely with one attached to the load-free shaft end of the ink roller 7 Loader 27 is used to control the speed this ink roller 7 is selected.

A well-known in printing press control is shown schematically in Fig. 4. The regulation of the motor 5, via an elastic coupling 24th a load 25 drives takes place by means of a regulator 23. The load 25 is a heavy roll or a heavy one Cylinder or a corresponding roll or cylinder system, its mass moment of inertia typically more than five times as high as that of the engine 5 is. Nevertheless, the scheme of this engine / load system performance optimized and with sufficiently high Control quality for the number of revolutions or the angular position and the Speed of the load 25 are regulated. It should be the coupling 24 of motor and load is not too high Requirements are made in relation to their Torsional rigidity and backlash.

In the known systems, such as one in FIG. 4 is a mechanical actual value encoder 21 for generating a position or speed and the position of the rotor of the motor 5 characteristic electrical signal attached to this rotor. The is 25 is with the coupling 24, which has an elasticity and possibly a certain play, at the engine shaft end attached. The coupling and the load are outside the actual control loop. You can do this but over the back on the motor shaft Influence acceleration moments.

This system encounters large inertia ratios from the load to the engine quickly his dynamic limits. If the regulation becomes unstable, So above all the engine swings, while the load remains relatively quiet.

On the other hand, FIG. 5 shows a regulation in which as already shown in Fig. 3, the reference variable for the control is generated by a transmitter 21, the the load 25 and not attached to the motor 5. This Actual value encoder 21 is at the free shaft end of the load, in the Embodiment on the free shaft end of the blanket cylinder 2 a cylinder group 10, attached. This actual value encoder 21 will therefore be loader in the following called. The coupling 24 is through the already described timing belt 11 with respect to a direct coupling or a gear coupling higher Elasticity but also high attenuation formed. moreover this coupling 24 is free of play with a toothed belt.

The needed for the control, from the loader 21 generated actual value, the angular position of the blanket cylinder 2 or its speed and its angular position is represented on the controller 23 recycled. A computer generated setpoint of the Setpoint value generator 22 is compared with this actual value and to form a control signal for the motor 5 used.

In this scheme are the coupling 24 and the load 25 within the actual control loop. The load and the coupling 24 form a low-pass filter for the shocks generated in the controlled system and Vibrations, which thus only to a reduced extent be returned to the controller 23 and therefore also not to undesirable suggestions of the scheme being able to lead. This will change the dynamics and also the control quality compared to the conventional ones Systems even with otherwise identical coupling significantly increased. The system, consisting of regulators, Engine, clutch and cylinder is already in itself much more subdued. resonance increases therefore do not occur to the same extent. The regulator can therefore be set faster without the stable Leave workspace.

An optionally attached to the engine 5, In the embodiment of FIG. 5 illustrated actual value detection can for additional monitoring of the Motors 5, for example, at a desired emergency stop option of the motor 5 are used.

In the diagrams of Figures 6 and 7, the dynamic behavior of the two schemes according to Figures 4 and 5 is compared. As a measure of the dynamics of the control, the reciprocal value of the reset time T _{i of} the drive is selected. FIG. 6 shows the dynamics as a function of the mass inertia ratio of load to motor with identical coupling and identical phase reserve. This clearly shows that the control according to FIG. 5 with the actual value detection on the load, especially with larger mass inertia ratios, is clearly superior to the actual value detection on the motor according to FIG.

In Fig. 7, the dynamics as a function of torsional stiffness the coupling 24 at a constant inertia ratio and identical phase reserve displayed. This shows the control of FIG. 5 especially at low torsional stiffness of the coupling compared to the conventional control accordingly Fig. 4 superior.

Finally, FIG. 8 shows the control diagram of the controller 23. The desired value and the actual value, in the exemplary embodiment the desired or actual center position of a blanket cylinder 2, are supplied to a first differential amplifier 31 to form the difference between the nominal value actual value. The difference D ₁ formed there is fed to a first proportional amplifier 34 and applied as a proportionally amplified signal K ₁ XD ₁ to a second differential amplifier 35. In parallel, the setpoint value and the actual value are each supplied to a differentiator 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 via an integrator 37 to a current regulator for the motor 5.

FIG. 9 shows a pressure point which is indicated by three Cylinder groups 10 is formed. A first cylinder group 10 is on the one print side of the paper web 1, and a second and a third cylinder group 10 are on the opposite pressure side of this Paper web 1 arranged. The two on the same Print side of the paper web 1 arranged cylinder groups 10 are mutually attached to the blanket cylinder 2 the first cylinder group 10 adjustable. This is through two straight arrows W indicated. Here are the two upper cylinder groups 10, which are approximately horizontal opposite to a cylinder unit 20th summarized and as such in the machine frame stored independently of the lower cylinder group 10. Each cylinder group 10 is again from a Engine 5, as already with the two cylinder groups 10 of Figure 1 has been the case, driven individually.

This arrangement allows the flying Change of production with continuously ongoing Paper web 1. Each one of the two swing-away Rubber cylinder 2 is pivoted, while the others in print position to the opposite Rubber cylinder 2 of the first cylinder group 10 is. The production change takes place in a known manner by changing the plates of the swung off Blanket cylinder 2 associated plate cylinder Third

FIG. 10 shows an alternative pressure point also with three groups of cylinders 10. That to the arrangement from what is said above also applies in principle to Arrangement of Figure 10. While the three cylinder groups 10 of the arrangement of Figure 9 respectively the Form legs of a "Y" form the cylinder groups 10 of Figure 10 an upside down "Y" or a "Lambda". In the arrangement of Figure 10 are the two lower, horizontally opposite Cylinder groups 10 in the machine frame independently stored by the upper cylinder group 10. These two lower cylinder groups 10 thereby form the Construction or cylinder unit 20.

The arrangements of Figures 9 and 10 show the high flexibility of the formation according to the invention of cylinder groups and the preferred control each cylinder group. It can be on particularly simple Form a variety of pressure points, For example, by having cylinder units 20 with cylinder groups 10 (Figures 9 and 10) or more cylinder units 20 are arranged one above the other (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) wherein the circumferential register adjustment of the blanket cylinders can be performed coordinated one to each other 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 A-shape with the third cylinder group (10).

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