JPH0834108A - Rotary press with a blanket cylinder and a plate cylinder integrated in a pair of cylinders - Google Patents

Abstract

(57) [Abstract] [Purpose] The present invention relates to a rotary printing press in which cylinders are integrated into individual cylinder groups and a drive adjusting mechanism of an assembly thereof. The rotary printing press of the present invention comprises a blanket cylinder and a plate cylinder which are integrated in pairs in a cylinder group by mechanical connection to a common drive. This cylinder group is individually driven by its own drive motor. Further, according to the present invention, there is provided an adjusting mechanism including a load transmitter on the load side. According to these configurations of the present invention, simplification of the driving mechanism is achieved, and at the same time, an adjusting mechanism that can control the cylinder or the roller with high adjusting quality with respect to dynamics, rotational speed and positional accuracy is provided.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rotary printing press in which cylinders are integrated into individual cylinder groups and a drive adjusting mechanism for an assembly thereof.

[0002]

BACKGROUND OF THE INVENTION A conventional rotary printing press is driven from a main drive through a mechanical longitudinal axis, also called the king axis. A drawback of this printing machine is the mechanical waste that must be spent to compensate for the twisting that occurs during operation of the longitudinal axis. As such, a mechanical perimeter alignment adjustment is required from the print area of the printing press during operation. It has also been envisaged to replace the mechanical longitudinal axis between the individual printing units with an electrical longitudinal axis. In this case, each printing unit contains a separate electrical drive. Due to the complexity of the printing unit, which has a large number of printing areas, a great amount of mechanical waste is still incurred, but in this case, in addition to this a higher adjustment waste. This is because it is necessary to ensure synchronous operation between the printing units that are individually driven.

In order to avoid the problems mentioned above, the German patent DE
41 38 479 Al, it is proposed to drive each cylinder of the printing machine with one electronic motor. The individual drives of the cylinders and their drive regulators can then optionally be integrated in the printing zones. The print areas are arranged on the folding device and the print areas are obtained from a reference of their position. This proposed guidance system
In essence, it consists of a rapid BUS system system for the individual drives and drive regulators, and a supervised guidance system for the management of the printing zones.

The method of individually driving the cylinders, which is pursued in both of these printed matters, gives a great eccentricity, but at the same time requires a very large number of driving electric motors,
As shown in DE 4214 394 Al, this large number of individual drives results in the waste of large adjustment mechanisms. Moreover, a wide variety of motors must be used. On the other hand,
When using a small number of motors, it is likely that a huge motor will be installed for various applications. Both raise the price of this type of printing machine.

[0005]

SUMMARY OF THE INVENTION It is an object of the present invention to create an economical rotary printing machine which can be flexibly set.

[0006]

The above-mentioned problems of the present invention are as follows.
According to the present invention, a blanket cylinder and a plate cylinder are coupled to a cylinder group in pairs through a mechanical coupling for driving, and each cylinder group is driven by its own drive motor. .

According to the invention, the blanket cylinder and the plate cylinder of a rotary printing press form a pair of cylinders, and in this cylinder group, one rubber cloth cylinder and one plate cylinder are mutually machined. Are coupled together and driven together by one own drive motor per cylinder group.

By integrating both cylinders and their equipment with a single drive for at least one cylinder pair in this way in groups, the number of drive motors required is significantly reduced. It is at least half that of the individual drive method. The mechanical connection of the two cylinders, which are arranged by means of printing technology, to one another, preferably by means of spur gears or helical gears, offers distinct price advantages compared to the individual cylinder drive. With regard to the eccentricity of installation, it does not cause any significant reduction compared to the individual drive system. Therefore, the peripheral alignment adjustment and the surface alignment adjustment of each blanket cylinder can be performed individually and in tune with any other blanket cylinder as long as necessary.

With the cylinder group according to the invention, each equipped with its own drive motor, in a rotary printing press an optimum printing area is formed from a technical and economic point of view. In the present description, each cylinder pair between which the printed paper web is fed and printed on one side or on both sides is understood as the printing area. Therefore, although the opposing printing cylinders corresponding to one cylinder group belong to the printing area formed according to the present invention, the opposing pressing cylinders may or may not belong to the cylinder group. In the latter case, two mutually deployed cylinders form one printing area. However, in both cases, the printing areas of the printing machine are mechanically independent in terms of drive technology. That is, the printing areas of the printing machine are electrically coupled to each other.

Preferably, in the cylinder group of the present invention, the blanket cylinder is driven, and this cylinder drives the plate cylinder of the same cylinder group via a mechanical connection. However, in another embodiment of the invention, the drive drives the plate cylinder shaft, so that the blanket cylinder is driven subordinately from the plate cylinder via a mechanical connection. The drive of the plate cylinder preferably requires only a little waste of engagement and disengagement of the blanket cylinder, but the drive of the blanket cylinder is advantageous for the other-side position accuracy or perimeter alignment adjustment. The first listed solution is that the cylinder in direct contact with the paper web to be finally printed is
In any case, it has the advantage that it does not have to be driven via a transmission member, which possibly includes play.

It is advantageous to operate each group of three cylinders on one printing area. In this case, one cylinder group is arranged on one printing side of the paper web passing therethrough, and the other two are arranged on the opposite printing side. Preferably, in this case, the blanket cylinders of the pair of cylinders arranged on one printing side of the paper web are opposed pressing cylinders to the other two blanket cylinders of the cylinder group arranged on the opposite printing side of the paper web. It is good to form. Thus, the latter cylinder groups are preferably driven alternately in each case. This configuration gives the rubber / rubber product a very high degree of variability. Because in the case of continuous production,
This is because both rubber cylinders that can be set alternately can be configured to switch printing. This can be done by replacing the plate of the plate cylinder provided on the non-contact rubber cloth cylinder. Each cylinder group may be pivotally supported by a single frame. Preferably, the cylinder groups that are horizontally opposed to each other on one printing side of the paper web are integrated into a cylinder assembly that is axially supported by one frame body.

According to the invention, a group of cylinders can be deployed around one counter-pressing cylinder against the blanket cylinder. This third cylinder of the cylinder group thus formed is mechanically connected to the blanket cylinder, preferably via another gear connection. This type of cylinder group already embodies the printing area, and the paper web to be printed is guided between the blanket cylinder and the counter-press cylinder. The opposed pressing cylinder may be a steel cylinder or another blanket cylinder for double-sided printing. A counter-pressing cylinder of this kind may in particular be the central cylinder of a group of cylinders, for example having 9 or 10 cylinders. In an alternative, likewise preferred embodiment of the invention, a central cylinder of this kind is driven by its own drive motor. Therefore, this kind of integration
Gives the cylinder assembly a very high setting of eccentricity. In this case, each of the group of cylinders consisting of the blanket cylinder and the plate cylinder arranged for the central cylinder, individually,
And it can be reversed regardless of other cylinder groups. This is necessary, for example, in the case of alternating printing or rapid plate changes.

The drive of each cylinder group from the driven motor is
It is preferable to use a toothed belt. Mounting the rotor of the electric motor on the driven cylinder DE 41 38
Contrary to the solution proposed in 479, this kind of toothed belt has a high elasticity. The possibility of applying a high braking force to the mechanical system consisting of the drive motor and the driven cylinders by using a toothed belt as an adjustment method of the cylinder group drive is of great value, as will be further explained. However, the invention allows direct drive in principle, which may even be advantageous for small cylinders. The gear drive between the drive motor and the driven motor of the cylinder group may have applications as well, but compared to that gear drive, the toothed belt is play-free and not absolutely fixed. It has the advantage of providing a transmission relationship.

On the other hand, for the mechanical coupling between the cylinders in the cylinder group, gears are provided, although other transmission members can be sufficiently considered. The gears that mesh with each other may be spur gears or helical gears. In the case of helical gears, the blanket cylinder is moved in the longitudinal direction for surface alignment adjustment, during which its drive and / or drive gear is
According to the invention, it remains stationary. In other cases, perimeter alignment adjustments may be needed as well as surface alignment adjustments. When using spur gears, the blanket cylinder is simply moved longitudinally with its fixed gear (s).

According to the invention, the ink roller or the ink roller or the dampening roller of the inking device or the inking device and the dampening device provided in the cylinder group is mechanically connected to this cylinder group according to the invention. The rollers can be driven together by the drive rollers of this cylinder group. With this approach, a small amount of adjustment technology waste is maintained. On the other hand, the mechanical coupling of the inking device in the sense of the unit assembly approach sought in the present invention is not completely ideal as the more preferred self-driving to the roller (s) of the inking device. In this similarly preferred embodiment of the invention, each inking unit has a self-driving motor for its inking roller. Drive motors of this kind likewise, in the case of the drive of ink rollers or, if desired, multiple ink rollers, preferably via a play-free toothed belt with a high braking force, if necessary via a reduction-gear transmission. It is preferable to drive the ink roller closest to the plate cylinder of the corresponding cylinder group. At this time, the peripheral speed of the ink roller is preferably made adjustable by a negative slip with respect to the plate cylinder. In this case, the peripheral speed of the ink roller is
It is preferably slightly less than the peripheral speed of the corresponding plate cylinder.

A special problem is the adjustment of the motor / load system with the drive motor for one cylinder or one roller of the rotary press. In the individual case, for small loads, large or high-performance motors with a relatively high mass moment of inertia compared to the load are used. This type of system does not pose too much of a problem regarding vibration and shock control. This is because the loads are forced together by the motor. The inertial mass moment of the driven load becomes large, and the mass moment of inertia is often five times larger than that of the driving motor, but in that case, the problem of vibration increases. This motor / load system adjustment is correspondingly complicated. The elasticity of the coupling between the motor and the load contributes to the sharpening of the problem.

As a configuration of the printing machine, a mechanical indicator is used on the motor side for detecting the rotational speed of the motor or the rotor angle of the motor for the purpose value / actual value comparison of the motor adjusting mechanism. Alternatively, a rotation speed adjusting mechanism is known. However, this known adjustment mechanism increasingly hits its dynamic limits as the load-to-motor mass inertia relationship increases. When the actual position is measured on the motor shaft, there are coupling mechanisms and mechanical loads outside the intrinsic regulation circuit. These influence the adjusting circuit via the acceleration moment which acts in a feedback manner on the motor shaft. In this case, the motor, which has a substantially lower mass than the coupling mechanism or the cylinder, is critically affected. Since the resulting motor load consists of a mechanical structure consisting of a mass, a spring and a braking mechanism, the load moment is very frequency dependent, which ultimately determines the dynamic behavior of the system. Upon excitation by changing the target value, the springs closest to the motor are first tensioned. The motor moment caused by the controller accelerates part of the coupling mechanism and subsequently the cylinder or driven roller. Energy up to this point is stored in springs and mass transfers, and its distribution is constantly changing. The motor can take the correct position within a short period of time, but it is changed anew by the resulting inertial mass, which leads to another adjusting stroke. The system must be controlled and stabilized by a relatively slow controller.

The present invention, in a rotary printing press, optimizes the position and the rotational speed of cylinders and rollers driven by a motor, and adjusts the dynamics and rotational speed accuracy or position accuracy to a sufficiently high level. The task is to create an adjusting mechanism that can be adjusted with quality.
The adjustment mechanism must be reasonably priced and must not place too high demands on the coupling of the motor and the load, especially with regard to the torsional stiffness of the coupling or the playlessness.

Preferably, the drive motors of the cylinder groups which are driven at least on the same printing side of the paper web of the cylinder assembly are adjusted. The so-called ideal position adjustment, i.e. the non-delayed position adjustment with lag error control, is given priority. However, the costly position adjustments desired for this technical reason can be dispensed with altogether. With a simple position adjustment mechanism, a preferred, especially affordable embodiment of the invention is implemented.

According to the present invention, the adjustment of the position or the number of revolutions of the cylinder or the roller of the inking unit to be adjusted in the group of cylinders is performed in accordance with the present invention by a target value for detecting the position and / or the number of revolutions of the cylinder or the roller by the controller for the drive motor. This is done by a target / actual value comparison of the output signal of the transmitter or the actual value transmitter. Therefore, the load indicator is used for the adjusting mechanism unlike the known adjusting mechanism in the rotary printing press. On the other hand, in the configuration of the printing press, the mechanical transmitter has been installed on the motor side in order to detect the rotation speed of the motor and the rotor angle of the motor for the purpose of comparing the target value / actual value of the motor adjustment mechanism. Has been used. In this conventional adjusting mechanism, if the mass inertial relationship between the load and the motor was large, the dynamic limit was immediately hit. If the adjustment mechanism is unstable, the motor will start to oscillate first, even though the load is relatively quiet.

Differential control mechanisms, regulating cascades and active filters are known in regulation technology for so-called two-mass pair vibrations, but these all require a great deal of regulation waste. The above-mentioned load / motor system,
In the case of self-driven cylinders, surprisingly,
In essence, it has been found to be entirely sufficient to guide the adjustment to the load, ie to the actual value as sensed by the actual value transmitter mounted on the cylinders of the group of cylinders. This actual value-distance-angle and / or rotational speed of the cylinder concerned is already sufficient only to achieve high dynamics and adjustment quality.

The drive motor can even be disregarded in the case of the two mass-to-vibrator of the present invention. The load acting as a low-pass filter is essentially insensitive to motor vibrations which are essentially smaller. On the other hand, the reaction of the load on the drive motor can be ignored. The adjustment mechanism of the present invention is reasonably priced for its simplicity, of course, but can easily reach a wide bandwidth load and mass-to-motor inertia relationship, and can change during operation, for example the elasticity of the coupling mechanism. It has the advantage that it can be tailored to parameters such as sex.

The actual value to be adjusted in accordance with the invention is taken at the load and therefore must be accurate.
That is, the load is measured, not the motor. Drive motor,
A mechanical compensation system consisting of a coupling mechanism and a load is considered a low pass filter. In the case of this type of adjusting mechanism, a low pass filter of the motor-coupling mechanism-load-distance system is used to filter the shock and vibration that occur during the adjusting process. Such shocks and vibrations are returned to the regulator to a reduced extent. Thereby the risk of rocking is avoided. Thereby, the dynamics of the adjusting mechanism and thus also the adjusting quality are substantially improved compared to the above-mentioned conventional adjusting mechanism with the same coupling mechanism.

The actual value transmitter, which is moved from the motor side to the load side as described above, forms the main adjustment amount for the adjuster of the motor. That is, the motor is guided from the load side by its actual value. In a particularly preferred embodiment of the invention, no mechanical actual value transmitter is required within the framework of the motor's adjusting mechanism for position or speed detection of the motor. Preferably, an actual value detection device integrated in the motor may be used for drive monitoring, and optionally for emergency disconnection.

The actual value transmitter for the adjusting mechanism, according to the invention, is equipped at the momentless shaft end of the driven cylinder of the cylinder group or the driven roller of the inking unit.

Particularly preferably, an asynchronous electric motor is used as the drive motor. Traditionally, asynchronous motors have been used only when large loads should drive small loads. The use of asynchronous motors is not known if the drive motor drives the cylinders or the rollers of the inking unit and the driven load has a relatively high mass moment of inertia with respect to the drive motor. Asynchronous motors are particularly suitable for the purposes of the adjustment according to the invention, which is made by the load transmitter instead of the motor transmitter. Since the asynchronous motor has a higher field tolerance than the DC motors hitherto introduced in the related applications, its entry has the dynamics and the adjusting quality of the adjusted system. However, the use of other types of motors, such as DC motors, is not ruled out in principle. The stability of the adjusting mechanism can be further improved by using a toothed belt with no play and high braking force as the coupling mechanism between the motor and the load.

The drive motor is invisible even in the mentioned two-mass oscillator. The load, which acts as a low-pass filter, is essentially insensitive to motor vibrations which are relatively small. On the other hand, the reaction of the load on the drive motor can be ignored.

According to the method in which the blanket cylinder and the plate movement are integrated in pairs in a cylinder group and, in some cases, it is further spread around another counter-pressing cylinder, the value of the printing machine constructed in this way is , A significant reduction compared to a printing machine with individual driven cylinders. In the case of a printing machine assembled from such a group of cylinders, the drive motor requires only two, and in some cases only three, performances. Each separated motor requires different lengths and diameters. With the toothed belts utilized according to the invention, the mass moment of inertia relationship between the load and the motor, which possibly swings in a wide range, is captured and tuned to one another by a corresponding selection of the transmission machine.
The reduction in the number of drive motors, combined with the advantage that the motors need to be prepared with a small number of types of performance, has already provided significant price advantages. This advantage is further amplified by the use of the simple adjustment mechanism of the present invention, which can be freely adapted to the changing mass inertia relationship. And, the advantages achieved by the present invention become more and more effective as the printing machine becomes larger, that is, the number of printing devices and printing areas per unit machine increases. In particular, the invention has application in the construction of offset printing machines. However, the invention is not limited to this type of machine.

From DE 38 28 638 C1 a printing machine is known in which the cylinder and the roller are driven from one main motor via a toothed belt. The motor is adjusted based on the actual value detected on the load side. The cylinder and the roller are coupled to each other via a drive gear train. Due to the adjusting mechanism described above, the vibrations only remain heavily in the drive gear train or are kept small with great technical waste.
Since the load-side moment of inertia is greater than before, this known adjusting mechanism is slow and possibly has only a small adjusting force.

[0030]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT A preferred embodiment of the present invention will be described below with reference to the drawings. These and other features and advantages of the present invention will be apparent from the description. In the printing area shown in FIG. 1, the paper web to be printed is guided between the two blanket cylinders (cylinders) of the two cylinder groups 10 arranged opposite to each other. The two cylinder groups each consist of a blanket cylinder 2 and a plate cylinder 3 arranged on it, and both cylinders are mechanically connected to one another for a common drive. The mechanical connection is schematically indicated by the connecting line between the midpoints of both cylinders 2 and 3.
In the embodiment of FIG. 1, each blanket cylinder of the cylinder group 10 is driven by a three-phase AC motor. In the structure corresponding to FIG. 1, only one blanket cylinder 2 and one plate cylinder 3 are integrated into one cylinder group by mechanical coupling. It is characterized by its simple construction method and the highest possible degree of freedom in construction.

FIG. 2 shows a modification for forming a printing area. In this modification, the counter pressing cylinder 4 for the rubber cloth copper is mechanically connected to the rubber cloth cylinder 2. In this embodiment, the cylinder group 10 is assembled from the blanket cylinder 2, its counter-pressing cylinder 4 and the plate cylinder 3 and its mechanical connection, the printing area being formed by only one cylinder group 10. In the embodiment of FIG. 2, compared with the embodiment of FIG. 1, not only the blanket cylinder 2,
The plate cylinder 3 provided on the blanket cylinder is also driven by the rotary motor 5. The advantage of this variant for integrating the cylinder groups into one cylinder group is that they have a constant feeding mode for the mechanical connection of the blanket cylinder 2 with the counter-pressing cylinder 4, and because of this mechanical connection. , There is no direct mutual influence of the cylinders 2 and 4. The counter-pressing cylinder 4 may be a second blanket cylinder or a steel cylinder, for example a central cylinder of 9 or 10 cylinder units.

The arrangement of the drive motor 5 on the blanket cylinder 2 or the plate cylinder 3 can in principle be interchanged in both embodiments.
The drive of the plate cylinder 3 has the advantage that the cylinder group 1 can be easily reversed, and in the case of the blanket cylinder 2 the cylinder for printing directly on the paper web 1 is driven, whereby the drive is A transmission member including play, for example a gear wheel, is freely possible.

FIG. 3 shows a cylinder assembly 20 including a central cylinder 6 and four cylinder groups 10 arranged in the central cylinder 6. In this embodiment, one blanket cylinder and one plate cylinder 3 are integrated into one cylinder group. To drive the central cylinder 6, it is equipped with its own drive motor 5. However, the central cylinder 6 has one of the four cylinder groups 10 as shown in FIG.
One cylinder group corresponding to the deformation depicted in FIG. This saves its own motor for the central cylinder 6. On the other hand, as depicted in FIG. 3, the integration of the smallest possible group of cylinders 10 for a cylinder assembly 20 and a self-driven central cylinder gives the highest variability in terms of configuration possibilities. This configuration, which is derived from the above-mentioned basic deformation of the assembly 20, has the advantage that the so-called fan-out effect is largely suppressed in terms of printing technology. Moreover, each of the blanket cylinders 2 can easily be reversed in rubber / rubber manufacturing. The possibility of different alternating prints to be reversed is likewise not suppressed.

As this embodiment shows, the cylinder group 10 made up of a pair of cylinders is equivalent to the idea of having a drive cylinder for each one in terms of its construction possibilities.

FIG. 4 shows the cooperative relationship between the ink roller 7 and the cylinder group 10 composed of the rubber cloth cylinder / plate cylinder pair 2 and 3. Here, the ink roller 7 can be freely used by the motor 5 via its own drive mechanism, but this motor may or may not be the same as the motor 5 for the cylinder group 10. The motor of the ink roller 7 drives the ink roller 7 via the toothed belt 15 and the gears 16 and 17. Then, the gear 17 is mounted on the shaft 17 of the ink roller 7. The various mass moments of inertia of the motor 5 and the ink roller 7 can be mitigated when driven via the toothed belt 15 and the gear pairs 16, 17 by appropriate selection of transmission relationships.

The peripheral speed of the ink roller 7 can be adjusted by a slight negative slip on the plate cylinder 3. This prevents the risk of the mechanical connection formed by the gear pair 12, 13 between the blanket cylinder 2 and the plate cylinder 3 coming out of mesh.

The cylinder 10 is driven by the motor 5 via the toothed belt 11 on the blanket cylinder 2. The mechanical connection between the blanket cylinder 2 and the plate cylinder 3 of the same cylinder group 10 is formed by both gears 12 and 13. The rotational speed of the motor 5 is correspondingly converted via the toothed belt 11 in order to mitigate the high mass moment of inertia coupling between the load and the drive mechanism, ie the cylinder group 10 and the motor 5.
The toothed belt 11 is an elastic coupling member between the motor 5 and the driven cylinder group 11. In principle, a very high braking of the motor / load system is achieved in the case of toothed belts, as compared with a direct connection, which is likewise useful, ie a gear connection. The same applies to the ink roller 7 and its connecting members, i.e. the drive mechanism, i.e. the toothed belt 15. Furthermore, the choice of a toothed belt provides great structural freedom due to its infinitely variable transmission. The motor 5 for the cylinder group 10 or the ink roller 7 is a three-phase AC motor having high field resistance. Again, with a toothed belt connection to the drive motor,
The unit assembly principle applies to the formation of cylinders or rollers. This is because, with a few motor performances, it is possible to equip a wide variety of variants with different cylinder lengths and diameters or roller lengths and diameters with correspondingly different mass moments of inertia.

The gears 12 and 13 forming the mechanical connection between the blanket cylinder 2 and the plate cylinder 3 may be helical gears or spur gears. In the case of a helical gear, the blanket cylinder 2 is moved in the longitudinal direction during the face-alignment adjustment, while the gear 12 and the corresponding gear for the toothed belt 11 are fixed. That is, both gears are axially supported on the cylinder shaft 14 so as to be movable in the longitudinal direction. If the two gears 12 and 13 are spur gears, the gear 12 and the gear for the toothed belt 11 are fixedly mounted on the shaft 14 and together with the motor 5 for the blanket cylinder 2 and the cylinder group 10 in the longitudinal direction. Be moved to.

Unlike known adjustment mechanisms in rotary printing presses, the motor / load systems 5, 10 are guided by actual values, which are on the load side, ie on the momentless side of the shaft 14 of the blanket cylinder 2. Occurs in the mechanical load transmitter 21 installed in the. An adjusting mechanism of the same kind, namely a load transmitter 27 mounted on the unloaded shaft end of the ink roller 7.
It is possible to select an adjusting mechanism having the following for controlling the number of rotations of the ink roller 7.

A well-known adjusting mechanism in a printing mechanism is shown schematically in FIG. Adjustment of the motor driving the load 25 via the elastic coupling mechanism 24 is carried out via the adjuster 23. The load 25 is a heavy roller or cylinder, or a corresponding roller or cylinder system, the mass moment of inertia of which is typically more than five times that of the motor 5. Nevertheless, the adjustment of the motor / load system must be optimized in terms of performance and with a sufficiently high adjustment quality with respect to the speed or angle of the motor and the speed of the load 25. At that time, to connect the motor and load,
Do not place too great demands on its rotation resistance and play-freeness.

In a known system as shown in FIG. 5,
A mechanical actual value transmitter 2 for producing an electrical signal representative of the position or speed of the motor 5 and the position of its rotor.
1 is mounted on the rotor. The load 25, together with the coupling mechanism 24, has some elasticity and possibly some play and is fixed to the end of the motor shaft. The coupling mechanism and load reside outside the self-regulatory system. However, they can influence it via the acceleration moments that counteract the motor shaft.

However, this system immediately hits its dynamic limit when the mass-inertia relationship between the load and the motor is large. If the regulator is unstable, the motor will first vibrate even when the load is relatively blocked.

FIG. 6, on the other hand, shows that, as already shown in FIG. 4, the transmitter 21 mounted on the load 25 rather than on the motor 5 provides a guide value for adjustment. 3 shows the regulatory mechanism that is generated.

This actual value transmitter is mounted on the free shaft end of the load, in this embodiment on the free shaft end of the blanket cylinder 2 of the cylinder group 10. This actual value transmitter 21 is henceforth referred to as a load transmitter. The coupling mechanism 24 is formed by the toothed belt described above with a higher elastic force, but with a higher braking force, compared to a direct coupling mechanism or gear coupling. For this reason, this coupling mechanism 24 on the toothed belt is play-free.

The actual value resulting from the load transmitter necessary for the adjustment, which is representative of the angle of the rubber cloth cylinder 2 and its rotational speed and its angle, is fed back to the regulator 23. The target value generated by the calculation from the target value transmitter 22 is compared with this current position, and the motor 5
Is used for the formation of the regulation signal for.

In this adjusting mechanism, the coupling mechanism 24 and the load 25 are in their own adjusting circuit. The load and coupling mechanism acts as a low-pass filter for the shocks and vibrations that occur during the adjustment process, so that this shock or vibration is returned to the regulator 23 only to a reduced extent, thus resulting in unwanted stimulation of the adjustment mechanism. I don't get it. Thereby, the quality of the dynamics and thus of the regulation is substantially increased compared to conventional systems, even in otherwise identical binding systems. The system consisting of the regulator, the motor, the coupling mechanism and the cylinder is itself strongly dampened. The adjusting device can therefore be adjusted quickly without abandoning the stable operating area.

The actual value detection illustrated in the embodiment of FIG. 6 and optionally equipped in the motor 5 is used for additional monitoring of the motor 5, for example when a possibility of an emergency disconnection of the motor 5 is desired. It

The diagrams of FIGS. 7 and 8 show the dynamics of both adjusting mechanisms according to FIGS. 5 and 6.
As a measure for the dynamics of the adjusting mechanism, the correlation value of the adjusting time T ₁ of the driving device is adopted. In FIG. 7, the dynamics are shown as a function of the load-to-motor mass inertia relationship for the same coupling mechanism and the same phase aspect. In this case, it is clearly shown that the adjusting mechanism of FIG. 6 for detecting the actual load output value is clearly superior to the current position detection by the motor corresponding to the motor 5 when the mass inertia relationship is large. There is.

In FIG. 8, the dynamics are shown as the torsional stiffness of the coupling mechanism 24 in constant mass inertia and in the same phase manner. Here, it is shown that the adjusting mechanism according to FIG. 6 is superior to the conventional adjusting mechanism corresponding to FIG. 5, especially when the torsional rigidity of the coupling mechanism is low.

Finally, FIG. 9 shows an adjustment diagram of the adjuster 23. The setpoint value and the setpoint value, in this example the setpoint value and setpoint value of the blanket cylinder 2, are introduced into the first differential amplifier in order to form the difference between the setpoint value and the setpoint value. The difference D ₁ formed there is guided to the first proportional amplifier 34 and supplied to the second differential amplifier as a proportionally amplified signal S ₁ XD ₁ . The target value and the actual value are respectively introduced in parallel to the differentiating element 32 or 33 and differentiated, and the corresponding output signals S ₂ and S ₁ are introduced into the second differential amplifier. The sum k ₁ D ₁ + S ₂ −S ₁ formed there is amplified by the second proportional amplifier 36 and supplied to the current regulator for the motor 5 via the integrating element 37.

FIG. 10 shows a print area in which three cylinder groups 10 are formed. The first group of cylinders 10 is on one printing side of the paper web 1 and comprises the second and third
Cylinder groups 10 are arranged on opposite printing sides of the paper web. Both cylinder groups 10 arranged on the same printing side of the paper web 1 can engage one another with the blanket cylinder 2 of the first cylinder group 10. This is clearly indicated by the two straight arrows. At that time, both cylinder groups of information 1
0s are assembled substantially horizontally with respect to the cylinder assembly 21 and, as such, are axially supported independently of the lower cylinder group 10 in the machine frame. Each cylinder group 10 is individually driven as it was with both cylinder groups 10 of FIG.

This arrangement makes it possible to quickly replace the product as the paper web 1 continues to run continuously. One of the two rubber cloth cylinders 2 that can be pivotally separated is pivotally separated, but the other is fixed to the opposed rubber cloth cylinder 2 of the first cylinder group 10 at the printing position. Product replacement is performed by the plate cylinder 3 mounted on the pivoted rubber cloth cylinder 2.
This is done in a known manner by exchanging the plates.

FIG. 11 shows an alternative print area which also has three cylinder groups. What has been described for the arrangement of FIG. 10 also applies in principle to the arrangement of FIG. The three cylinder groups 10 arranged according to FIG. 10 each form one side of the letter “Y”, but the cylinder group 10 of FIG. 11 forms an inverted “Y” or letter “lambda”. There is. In the arrangement according to FIG. 11, the lower, horizontally opposed cylinder groups 10 are pivotally supported in the machine frame regardless of the upper cylinder groups 10. Both lower cylinder groups 10 thereby form a structure or cylinder assembly.

The arrangements of FIGS. 10 and 11 show a high degree of variability with respect to the construction of the cylinder groups according to the invention and the adjusting mechanism according to the invention for each cylinder group. For example, the cylinder assembly is arranged together with the cylinder group (FIGS. 10 and 11).
By means of this or by arranging a large number of cylinder assemblies one on top of the other (FIG. 1), a very wide variety of printing areas can be constructed in a particularly simple manner. In principle, the cylinders of the arrangement according to FIGS. 10 and 11 can be connected in a different manner than that of FIGS. 1 to 4, for example via a single transmission.

[Brief description of drawings]

FIG. 1 is a schematic diagram showing a printing area having two cylinder groups.

FIG. 2 is a schematic diagram showing a printing area having one cylinder group.

FIG. 3 is a diagram showing a cylinder assembly having one self-driven central cylinder and four cylinder groups.

FIG. 4 is a schematic diagram showing a group of cylinders having a self-driving ink roller arranged.

FIG. 5 is a block diagram showing an adjusting mechanism of a drive device for a cylinder group corresponding to the current technology.

FIG. 6 is a block diagram of an adjusting mechanism for a cylinder group driving device of the present invention.

FIG. 7 is dependent on the mass inertia relationship of the motor and load,
It is a graph which shows a comparison of the dynamics mode of the conventional adjusting mechanism and the adjusting mechanism of the present invention.

FIG. 8 is a graph showing a comparison of the dynamic aspects of the conventional adjusting mechanism and the adjusting mechanism of the present invention, which depends on the rotational stiffness of the coupling mechanism between the motor and the load.

FIG. 9 is a block diagram of a regulator circuit of the regulator.

FIG. 10 is a schematic diagram showing a print area formed by three cylinder groups in a state of letter Y;

FIG. 11 is a schematic diagram showing a print area formed by three cylinder groups in a state of a character lambda.

[Explanation of symbols]

 1 Paper web 2 Rubber cloth cylinder (cylinder) 3 Plate cylinder (cylinder) 4 Opposing pressing cylinder 5 Drive motor 6 Center cylinder 7 Ink roller 10 Cylinder group 11,15 Toothed belt 12,13 Gears 16,17 Gears 20 Cylinder assembly 21 Load Transmitter 22 Target Value Transmitter 23 Transmitter 24 Coupling Mechanism 25 Load 31 Operational Amplifier 34 Proportional Amplifier 35 Operational Amplifier 32, 33 Differential Element 36 Proportional Amplifier

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[Procedure amendment]

[Submission date] June 6, 1995

[Procedure Amendment 1]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 6

[Correction method] Change

[Correction content]

[Procedure Amendment 2]

[Document name to be amended] Statement

[Name of item to be corrected] Claim 12

[Correction method] Change

[Correction content]

[Procedure 3]

[Document name to be amended] Statement

[Correction target item name] 0016

[Correction method] Change

[Correction content]

A special problem is the adjustment of the motor / load system with the drive motor for one cylinder or one roller of the rotary press. In the individual case, for small loads, large or high-performance motors with a relatively high mass moment of inertia compared to the load are used. This type of system does not pose too much of a problem regarding vibration and shock control. Because the moment of inertia of the load and
This is because the joint rigidity is very high . The inertial mass moment of the driven load becomes large, and the mass moment of inertia is often five times larger than that of the driving motor, but in that case, the problem of vibration increases. This motor /
The load system regulation becomes correspondingly complicated. The elasticity of the coupling between the motor and the load further contributes to the sharpening of the problem.

[Procedure amendment 4]

[Document name to be amended] Statement

[Correction target item name] 0026

[Correction method] Change

[Correction content]

Particularly preferably, an asynchronous electric motor is used as the drive motor. Traditionally, asynchronous motors have been used only when large loads should drive small loads. The use of asynchronous motors is not known if the drive motor drives the cylinders or the rollers of the inking unit and the driven load has a relatively high mass moment of inertia with respect to the drive motor. Asynchronous motors are particularly suitable for the purposes of the adjustment according to the invention, which is made by the load transmitter instead of the motor transmitter. Asynchronous motor as compared with the direct current motor is turned so far when related applications, because have high magnetic rigidity, its turned improves the dynamics and adjustment quality of the regulatory system. However, the use of other types of motors, such as DC motors, is not ruled out in principle. The stability of the adjusting mechanism can be further improved by using a toothed belt with no play and high braking force as the coupling mechanism between the motor and the load.

[Procedure Amendment 5]

[Document name to be amended] Statement

[Correction target item name] 0031

[Correction method] Change

[Correction content]

[0031] Although Figure 2 shows a modification for forming a print region, in this modification, the counter press cylinder 4 against the rubber cloth cylinder 2 is mechanically coupled with the rubber cloth cylinder 2 . In this embodiment, the cylinder group 10 is assembled from the blanket cylinder 2, its counter-pressing cylinder 4 and the plate cylinder 3 and its mechanical connection, the printing area being formed by only one cylinder group 10. In the embodiment of FIG. 2, compared with the embodiment of FIG. 1, not only the blanket cylinder 2,
The plate cylinder 3 provided on the blanket cylinder is also driven by the three-phase AC motor 5. The advantage of this variant for integrating the cylinder groups into one cylinder group is that the opposite pressing cylinder 4 of the blanket cylinder 2 is
It has a constant feed mode due to its mechanical coupling with, and that due to this mechanical coupling, no direct mutual influence of the cylinders 2 and 4 occurs. The counter-pressing cylinder 4 may be a second blanket cylinder or a steel cylinder, for example a central cylinder of 9 or 10 cylinder units.

[Procedure correction 6]

[Document name to be amended] Statement

[Correction target item name] 0033

[Correction method] Change

[Correction content]

FIG. 3 shows a cylinder assembly 20 including a central cylinder 6 and four cylinder groups 10 arranged in the central cylinder 6. In this embodiment, one blanket cylinder 2 and one plate cylinder 3 are integrated into one cylinder group 10 . To drive the central cylinder 6, its own three-phase AC motor 5 is equipped.
However, the central cylinder 6 may form one of the four cylinder groups 10 and one cylinder group corresponding to the deformation depicted in FIG. This saves its own motor for the central cylinder 6. On the other hand, as depicted in FIG. 3, the integration of the smallest possible group of cylinders 10 for a cylinder assembly 20 and a self-driven central cylinder gives the highest variability in terms of configuration possibilities. This configuration, which is derived from the abovementioned basic deformation of the cylinder assembly 20, has the advantage that the so-called fan-out effect is very modest in terms of printing technology. Moreover, each of the blanket cylinders 2 can easily be reversed in rubber / rubber manufacturing. The possibility of different alternating prints to be reversed is likewise not suppressed.

[Procedure Amendment 7]

[Document name to be amended] Statement

[Name of item to be corrected] 0037

[Correction method] Change

[Correction content]

The cylinder 10 is driven by the motor 5 via the toothed belt 11 on the blanket cylinder 2. The mechanical connection between the blanket cylinder 2 and the plate cylinder 3 of the same cylinder group 10 is formed by both gears 12 and 13. The rotational speed of the motor 5 is correspondingly converted via the toothed belt 11 in order to mitigate the high mass moment of inertia coupling between the load and the drive mechanism, ie the cylinder group 10 and the motor 5.
The toothed belt 11 is an elastic coupling member between the motor 5 and the driven cylinder group 11. In principle, a very high braking of the motor / load system 5 , 10 is achieved in the case of toothed belts, as compared with a similarly suitable direct connection, i.e. a gear connection. The same applies to driving the ink roller 7 .
Mechanism and its coupling member also true ie the toothed belt 15. Furthermore, the choice of a toothed belt provides great structural freedom due to its infinitely variable transmission. The motor 5 for the cylinder group 10 or the ink roller 7 is a three-phase AC motor having high magnetic field rigidity . Again, with a toothed belt connection to the drive motor,
The unit assembly principle applies to the formation of cylinders or rollers. This is because, with a few motor performances, it is possible to equip a wide variety of variants with different cylinder lengths and diameters or roller lengths and diameters with correspondingly different mass moments of inertia.

Claims (18)

[Claims] (A) A blanket cylinder (2) and a plate cylinder (3) form a pair of cylinder groups (1) via a mechanical connection for a drive unit.
0), and (b) each cylinder group (10) is driven by its own drive motor (5). 2. The rotary printing machine according to claim 1, wherein the blanket cylinder (2) is driven by a drive motor (5), and the driving force is transmitted from the blanket cylinder (2) onto the plate cylinder (3). 3. The group of cylinders (10) additionally has an opposing pressing cylinder (4) against its blanket cylinder (2), said opposing pressing cylinder being mechanically coupled to the rubber cloth cylinder (2). The rotary printing press according to claim 1 or 2. 4. A cylinder assembly (20) having a number of cylinder groups (10) has a central cylinder (6), which cylinder has its own drive motor (5) or drive. The rotary printing press according to claim 1 or 2, which is mechanically coupled to the blanket cylinder (2) of one cylinder group (10) for this purpose. 5. The rotary printing press as claimed in claim 1, wherein the driving force is transmitted from the drive motor (5) to the cylinders (2, 3) by means of the toothed belt (11). 6. An inking device or at least an inking roller (7) of an inking device and a dampening device arranged in a cylinder group (10) is mechanically connected to this cylinder group (1), or such an inking device. 2. The rotary printing press according to claim 1, further comprising its own drive motor (5) for driving at least the ink roller (7). 7. A control device for controlling the position and / or the rotational speed of a cylinder group (2; 2, 3, 4) driven by a drive motor (5), comprising a target value transmitter (22) and an actual value transmitter. In a rotary printing press with an adjusting mechanism having a regulator (21, 27) and a regulator (23) for the drive motor (5), the actual value transmitter (21, 27) is a cylinder group (10).
A rotary printing machine characterized by detecting the position and / or the number of revolutions of the cylinder (2, 3 or 4) of the. 8. The rotary printing press as claimed in claim 7, wherein the actual value output from the actual value transmitter (21, 27) forms the main control value for the regulator (23). 9. The adjusting mechanism is not provided with another mechanical actual value transmitter, in particular a mechanical actual value transmitter for detecting the position or rotational speed of the drive motor (5). The rotary press described. 10. A mechanical transmitter is provided on the drive motor (5), the output signal of which is used as an output signal for emergency disconnection of the drive motor (5). The rotary press described. 11. The actual value transmitter (21, 2) of the adjusting mechanism.
Cylinder (2) driven by drive motor (5)
8. The method according to claim 7, wherein the momentless shaft end of 3) is mounted.
10. The rotary printing machine according to any one of 10. 12. A drive motor (5) and a cylinder group (1
Rotary press according to any of the preceding claims, wherein a toothed belt (15) is used as a coupling device between the driven cylinder (2) or the driven rollers of (0). 13. A cylinder assembly (20) having a number of cylinder groups (10) has two central cylinders (6), each central cylinder having its own drive motor (5). The rotary printing press according to any one of 1, 2 and 4 to 12. 14. The rotary printing press according to claim 1, wherein the cylinder group (10) forms a printing area. 15. The rotary printing press according to claim 14, wherein the cylinder group (10) is provided on one printing side of the paper web (1), and the two cylinder groups (10) are provided on opposite printing sides. 16. A blanket cylinder (2) of a cylinder group (10) arranged on one printing side of a paper web has alternating cylinder groups (10) arranged on the opposite printing side of a paper web (1). The opposing pressing cylinder is formed for both the blanket cylinders (2) that can be set in the above.
The rotary press described. 17. The rotary printing press according to claim 14, wherein both cylinder groups (10) horizontally opposed to each other on one printing side are integrated into a cylinder assembly (21). 18. The cylinder assembly (21) having a cylinder group (10) is arranged in a Y-type or a λ-type.
7. The rotary printing machine according to 7.