EP0644048A2 - Machine d'impression rotative, avec des cylindres porte-blanchet et porte-clichés réunisen groupes de cylindres par paires - Google Patents

Machine d'impression rotative, avec des cylindres porte-blanchet et porte-clichés réunisen groupes de cylindres par paires Download PDF

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Publication number
EP0644048A2
EP0644048A2 EP94810752A EP94810752A EP0644048A2 EP 0644048 A2 EP0644048 A2 EP 0644048A2 EP 94810752 A EP94810752 A EP 94810752A EP 94810752 A EP94810752 A EP 94810752A EP 0644048 A2 EP0644048 A2 EP 0644048A2
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EP
European Patent Office
Prior art keywords
cylinder
rotary printing
printing machine
motor
machine according
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP94810752A
Other languages
German (de)
English (en)
Other versions
EP0644048B2 (fr
EP0644048A3 (fr
EP0644048B1 (fr
Inventor
Felix Schneider
Andreas Miescher, Iii.
Andreas Zahnd
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wifag Maschinenfabrik AG
Original Assignee
Wifag Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Priority claimed from DE4344896A external-priority patent/DE4344896C5/de
Priority claimed from DE19934344912 external-priority patent/DE4344912C5/de
Priority claimed from DE4405658A external-priority patent/DE4405658C5/de
Priority to EP01116647A priority Critical patent/EP1155826B1/fr
Priority to EP99106201A priority patent/EP0930160B1/fr
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Priority to EP99106200A priority patent/EP0930159B1/fr
Publication of EP0644048A2 publication Critical patent/EP0644048A2/fr
Publication of EP0644048A3 publication Critical patent/EP0644048A3/fr
Publication of EP0644048B1 publication Critical patent/EP0644048B1/fr
Application granted granted Critical
Publication of EP0644048B2 publication Critical patent/EP0644048B2/fr
Anticipated expiration legal-status Critical
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/008—Mechanical features of drives, e.g. gears, clutches
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/004—Electric or hydraulic features of drives
    • B41F13/0045—Electric driving devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41P—INDEXING SCHEME RELATING TO PRINTING, LINING MACHINES, TYPEWRITERS, AND TO STAMPS
    • B41P2213/00—Arrangements for actuating or driving printing presses; Auxiliary devices or processes
    • B41P2213/70—Driving devices associated with particular installations or situations
    • B41P2213/73—Driving devices for multicolour presses
    • B41P2213/734—Driving devices for multicolour presses each printing unit being driven by its own electric motor, i.e. electric shaft
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2557/00—Means for control not provided for in groups B65H2551/00 - B65H2555/00
    • B65H2557/20—Calculating means; Controlling methods
    • B65H2557/264—Calculating means; Controlling methods with key characteristics based on closed loop control
    • B65H2557/2644—Calculating means; Controlling methods with key characteristics based on closed loop control characterised by PID control

Definitions

  • the present invention relates to the combination of cylinders of a rotary printing press into individual cylinder groups and a drive control therefor.
  • DE 41 38 479 A1 proposes to drive the cylinders of the printing press by means of an electric motor each.
  • DE 42 14 394 A1 discloses a control system for such a printing press, each with individually driven cylinders.
  • the individual drives of the cylinders and their drive controllers can be combined to form pressure point groups.
  • the printing point groups are assigned to folders from which they obtain their position reference.
  • the proposed control system essentially consists of a fast BUS system for the individual drives and the drive controllers of a pressure point group and a superordinate control system for managing the pressure point groups.
  • the present invention has set itself the task of creating a highly flexible, yet economical rotary printing press.
  • the blanket cylinder and plate cylinder of a rotary printing press form a cylinder group in pairs, in each of which a blanket cylinder and a plate cylinder are mechanically coupled to one another and are driven together by a separate drive motor per cylinder group.
  • This grouping of the two cylinders and their equipment with a single drive for at least one pair of cylinders significantly reduces the number of drive motors required; at least halved compared to the individual drive concepts.
  • the mechanical coupling of these two cylinders which are assigned to one another in terms of printing technology, preferably a gearwheel coupling with straight or helical toothed gears, offers significant price advantages over the concept of the individually driven cylinders.
  • versatility there are no major drawbacks compared to the single drive concept.
  • both the circumferential register and the side register adjustment of each blanket cylinder can be carried out individually and, if necessary, matched to any other blanket cylinder become.
  • printing points are understood to be the cylinder pairs between which a paper web to be printed runs and is printed on one or both sides. Accordingly, a cylinder group and a corresponding counter-pressure cylinder, which can belong to the cylinder group, but need not, belong to a pressure point formed according to the invention. In the latter case, a pressure point is formed by two cylinder groups assigned to one another. In terms of drive technology, however, the printing points of the printing press are mechanically independent in both cases, ie the printing points of the printing press are electrically coupled to one another.
  • the blanket cylinder is preferably driven, which in turn drives the mechanical coupling onto the plate cylinder of the same cylinder group.
  • the drive can also drive the plate cylinder shaft, so that the blanket cylinder is only driven by the plate cylinder via the mechanical coupling. While the drive on the plate cylinder advantageously requires little effort for turning the blanket cylinder on and off, the blanket cylinder on the other hand is decisive for the positional accuracy or circumferential register setting.
  • the first-mentioned solution has the advantage that the cylinder, which ultimately comes into direct contact with a paper web to be printed, does not first have to be driven via a transmission element which may be free of play.
  • One cylinder group is on one pressure side, and two cylinder groups are on the opposite pressure side of one passing between them Paper web arranged.
  • the rubber cylinder of the cylinder group arranged on one printing side of the paper web preferably forms the impression cylinder for the two other rubber cylinders of the cylinder groups arranged on the opposite printing side of the paper web, which advantageously can both be operated alternately.
  • This configuration offers the greatest versatility for a rubber / rubber production, since with continuous production the two mutually usable rubber cylinders can be configured to change the pressure. This is done by changing the plate of a plate cylinder assigned to the non-employed rubber cylinder.
  • Each cylinder group can be stored in a single frame.
  • the two cylinder groups lying horizontally opposite one printing side of the paper web are preferably combined to form a cylinder unit mounted in a frame.
  • a cylinder group can be expanded according to the invention by an impression cylinder for the blanket cylinder.
  • This third cylinder of the cylinder group formed in this way is mechanically coupled to the blanket cylinder, preferably by a further gear coupling.
  • the impression cylinder can be a steel or another blanket cylinder for double-sided printing.
  • Such an impression cylinder can in particular also be a central cylinder of a cylinder unit with, for example, nine or ten cylinders. In an alternative, likewise preferred embodiment of the invention, such a central cylinder is driven by its own drive motor.
  • This type of grouping provides the greatest versatility for a cylinder unit. In this case, each of the cylinder groups of blanket and plate cylinders assigned to the central cylinder can be reversed individually and independently of the other cylinder groups, as is required, for example, for alternating pressure or for the flying plate change.
  • the drive from a drive motor to the respective cylinder group is preferably carried out by means of a toothed belt.
  • a toothed belt has a high elasticity.
  • the possibility of high damping of the mechanical system consisting of a drive motor and the driven cylinders, which is provided by the use of a toothed belt is of great value, as will be explained below.
  • the invention also permits direct drive, which can even be advantageous in the case of small cylinders.
  • a toothed belt has the advantage of a play-free run and a gear ratio that is not absolutely fixed
  • gears are provided for the mechanical coupling between the cylinders within a cylinder group, although other transmission elements are also conceivable.
  • the meshing gears can be spur or helical.
  • the blanket cylinder is shifted longitudinally to adjust the side register, while its drive and / or driven gears remain stationary according to the invention. Otherwise, a circumferential register adjustment would also be necessary with the side register.
  • the rubber blanket cylinder is simply moved longitudinally together with its fixed gear or gears.
  • the inking roller or the inking rollers or dampening rollers of an inking unit or an inking and dampening unit which is assigned to a cylinder group can, according to the invention, be mechanically coupled to this cylinder group, so that the inking roller or inking rollers are driven by this cylinder group's drive motor are driven.
  • the technical control effort can be kept low.
  • the mechanical coupling of the inking unit in the sense of the modular principle pursued by the invention is not quite as ideal as the more preferred self-drive for the roller or the rollers of the inking unit.
  • each inking unit has its own drive motor for its inking rollers.
  • Such a drive motor also preferably drives the inking roller via a backlash-free toothed belt with high damping and optionally via a reduction gear drive, or in the case of several inking rollers, the inking roller closest to the plate cylinder of the corresponding cylinder group.
  • the peripheral speed of this ink roller is advantageously adjustable, in particular with a negative slip relative to the plate cylinder, the peripheral speed of the ink roller preferably being somewhat lower than that of the corresponding plate cylinder.
  • the position or speed of a cylinder are regulated known in which a mechanical encoder on the motor side for detecting the motor speed or the rotor angular position of the motor is used for a target / actual comparison of the motor control.
  • this known regulation increasingly reaches its dynamic limits with increasing inertia ratios from the load to the motor. If the actual position is measured on the motor shaft, both the coupling and the mechanical load lie outside the actual control loop. However, you can influence this via the acceleration torques that affect the motor shaft.
  • the motor which in this case has a much smaller mass than the coupling and the cylinder, is significantly influenced by this.
  • the load torque is heavily frequency-dependent, which ultimately determines the dynamic behavior of the system.
  • the springs closest to the motor are tensioned first.
  • the engine torque caused by the controller accelerates parts of the coupling and subsequently the cylinder or the driven roller.
  • energy is stored in the springs as well as in the mass movement, the distribution of which is constantly changing.
  • the motor may have assumed the correct position within a short time, but is again deflected by the inertial forces that occur, which leads to a further control process.
  • the system must be stabilized by a relatively slow controller.
  • the present invention has therefore also set itself the task of providing a control with which the position and / or the speed of a cylinder or a roller, which is driven by a motor, is optimized in a rotary printing press and with a sufficiently high control quality, ie with regard to the dynamics and the speed or positional accuracy, can be regulated
  • the regulation should be inexpensive and not too high demands on the coupling of motor and load, in particular on the torsional stiffness and freedom from play of the Make coupling.
  • At least the drive motors of the cylinder groups of a cylinder unit working on the same pressure side of a paper web are preferably position-controlled.
  • So-called ideal position control is preferred, i.e. a delay-free position control with following error.
  • this complex type of position control which is desired for technical reasons, can also be dispensed with.
  • a simple position control also represents a preferred, in particular cheaper, embodiment of the invention.
  • the control of the position and / or the speed of the cylinder to be controlled of a cylinder group or a roller of an inking unit takes place according to the invention by means of a controller for the drive motor by comparing the target / actual values of the output signals of a target value transmitter and an actual value transmitter, the latter Actual value encoder detects the position and / or the speed of the cylinder or roller.
  • a load encoder is therefore used for the regulation.
  • a mechanical encoder on the motor side was previously used in printing press construction to record the motor speed or the rotor angular position of the motor for the target / actual comparison of the motor control.
  • the drive motor can even be disregarded in the dual mass oscillator according to the invention.
  • the load acting as a low-pass filter is insensitive to the vibrations of the motor, which is much smaller in comparison.
  • the repercussions of the load on the drive motor can be neglected.
  • the control according to the invention offers the further advantage that it also simply accommodates the wide range of inertia ratios between the load and the motor and parameters that change during operation , such as the elasticity of a coupling, can be adjusted.
  • the mechanical replacement system consisting of the drive motor, a coupling and the load is to be regarded as a low-pass filter.
  • the low-pass filter of the motor coupling-load-distance system is used to avoid shocks and vibrations that occur in the controlled system. to filter. Such impacts and vibrations are thus returned to the controller to a reduced extent. This reduces the risk of rocking.
  • the dynamics of the control and thus also the control quality can be significantly increased compared to the conventional control described with identical coupling.
  • the actual value transmitter figuratively speaking, moved from the motor side to the load side forms the main controlled variable for the controller of the motor, ie the motor is guided from the load side by its actual value.
  • no mechanical actual value transmitter is required for the detection of the position or the speed of the motor as part of the regulation of the motor. Any actual value detection integrated in the motor can advantageously be used for pure drive monitoring, if necessary for an engine emergency shutdown.
  • the actual value transmitter for the control is attached to the torque-free shaft end of the driven cylinder of a cylinder group or the driven roller of an inking unit.
  • Electric asynchronous motors are used particularly advantageously as the drive motors.
  • an asynchronous motor has only been used when a small load had to be driven by means of a large motor.
  • a drive motor drives a cylinder group or also the rollers of an inking unit, in which the driven load therefore has a comparatively high mass moment of inertia compared to the drive motor
  • Asynchronous motors are particularly suitable for the purposes of the regulation according to the invention with a load sensor instead of a motor sensor.
  • asynchronous motors have a higher field stiffness, so that their use improves the dynamics and control quality of the system to be controlled.
  • the use of other motor types for example DC motors, is not fundamentally excluded.
  • the stability of the control is further improved by the preferred use of a backlash-free toothed belt with high damping as a coupling between the motor and the load.
  • the drive motor can even with the two-mass oscillator in question be disregarded.
  • the load acting as a low-pass filter is insensitive to the vibrations of the motor, which is much smaller in comparison.
  • the effects of the load on the drive motor can be neglected.
  • a printing press is known, the cylinders and Rolls are driven by a main motor via a toothed belt. The motor is controlled on the basis of actual values tapped on the load side.
  • the cylinders and rollers of the printing press are coupled to one another via a drive wheel train.
  • the control described makes it difficult to keep vibrations in the drive wheel train low or with great technical effort. Since the moment of inertia on the load side is rather large, this known control is slow and at most has a low control dynamics.
  • a paper web 1 to be printed is passed between the two opposing blanket cylinders 2 of two cylinder groups 10.
  • the two cylinder groups 10 are each formed by the blanket cylinder 2 and an associated plate cylinder 3, which are mechanically coupled to one another for the common drive.
  • the mechanical coupling is indicated schematically by a connecting line between the centers of the two cylinders 2 and 3.
  • the blanket cylinders 2 of each cylinder group 10 are driven by a three-phase motor 5.
  • the configuration according to FIG. 1, in which only one blanket cylinder 2 and one plate cylinder 3 are combined to form a cylinder group 10 by mechanical coupling, is characterized by its simple construction and the highest possible degree of configuration freedom in the formation of pressure points or pressure point groups out.
  • Fig. 2 shows a variant for forming a pressure point in which an impression cylinder 4 for the blanket cylinder 2 is mechanically coupled to this blanket cylinder 2.
  • the cylinder group 10 is composed of the blanket cylinder 2, its impression cylinder 4 and the plate cylinder 3 and their mechanical coupling, so that the pressure point is formed by a single cylinder group 10.
  • the blanket cylinder 2 in contrast to that of FIG. 1, not the blanket cylinder 2, but rather the plate cylinder 3 assigned to this cylinder is driven by a three-phase motor 5.
  • the advantage of this variant for the combination of cylinders into a cylinder group is their constant delivery behavior because of the mechanical coupling of the blanket cylinder 2 with its impression cylinder 4 and that Because of this mechanical coupling, there is no direct interference between cylinders 2 and 4.
  • the impression cylinder 4 can be a second blanket cylinder or a steel cylinder, for example a central cylinder of a nine or ten cylinder unit.
  • the assignment of the motors 5 to the blanket cylinders 2 or the plate cylinders 3 can in principle be interchanged in both exemplary embodiments.
  • the drive of the plate cylinder 3 has the advantage that the cylinder group 10 can be reversed more easily, while in the other case, when the blanket cylinder 2 is driven, the cylinder printing directly on the paper web 1 is driven, and thereby a drive free of play-related transmission elements, such as gears, for example. is possible.
  • FIG. 3 shows a cylinder unit 20, consisting of a central steel cylinder 6 and four cylinder groups 10 assigned to this central cylinder 6.
  • a blanket cylinder 2 and a plate cylinder 3 are combined to form a cylinder group 10.
  • a separate three-phase motor 5 is provided for driving the central cylinder 6.
  • the central cylinder 6 could likewise form a cylinder group in accordance with the variant shown in FIG. 2 with one of the four cylinder groups 10. This would save the own motor 5 for the central cylinder 6.
  • the summary in FIG. 3 of the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to form a cylinder unit 20 offers the greatest possible flexibility with regard to the configuration options.
  • This configuration of a cylinder unit 20 derived from the basic variants described above has the advantage in terms of printing technology that the so-called fan-out effect is very limited.
  • Each of the blanket cylinders 2 is also easily reversible to rubber / rubber production.
  • the possibilities to switch to different types of alternating pressure are also not limited.
  • a cylinder group 10 formed from cylinder pairs is equal in terms of its configurability to a concept with individually driven cylinders.
  • the inking roller 7 has its own drive by a motor 5, which can be identical to the motor 5 for the cylinder group 10, but need not be.
  • the motor 5 for the inking roller 7 drives the inking roller 7 via a toothed belt 15 and a pair of gearwheels 16, 17, the gearwheel 17 being seated on the shaft of the inking roller 7.
  • the different moments of inertia of the motor 5 and the inking roller 7 are mitigated by a suitable choice of the gear ratios during the output via the toothed belt 15 and the gear pair 16, 17.
  • the peripheral speed of the inking roller 7 is adjustable with a slightly negative slip relative to the plate cylinder 3. This can counteract the risk that the mechanical coupling formed by a pair of gears 12, 13 between the blanket cylinder 2 and the plate cylinder 3 will be lifted out of meshing.
  • the cylinder group 10 is driven by the motor 5 via the toothed belt 11 onto the blanket cylinder 2.
  • the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 of the same cylinder group 10 form the two gear wheels 12 and 13.
  • the speed of the motor 5 is reduced accordingly via the toothed belt 11.
  • This toothed belt 11 is the elastic coupling member between the Engine 5 and the driven cylinder group 10. Compared to a direct coupling or a gear coupling that is also suitable in principle, the toothed belt 11 achieves very high damping of the motor / load system 5, 10.
  • the motors 5 for the cylinder group 10 and the inking roller 7 are three-phase motors with a high field rigidity.
  • the modular principle of forming cylinder groups or roller groups with toothed belt coupling to the drive motor also comes into play here, since with fewer motor output sizes the entire variety of cylinder or roller lengths and diameters can be equipped with correspondingly different mass moments of inertia.
  • the two gears 12 and 13, which form the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3, can be helical or straight toothed gears.
  • the blanket cylinder 2 is shifted longitudinally when the side register is adjusted, while the gear 12 and the corresponding gear for the toothed belt 11 remain stationary, i.e. these two gears are mounted on the cylinder shaft 14 so as to be longitudinally displaceable.
  • the gear wheel 12 and the gear wheel for the toothed belt 11 are firmly seated on the shaft 14 and, together with the blanket cylinder 2 and the motor 5 for the cylinder group 10, are longitudinally displaced together.
  • the motor / load system 5, 10 is guided by an actual value which is generated by a mechanical load transmitter 21 attached to the load side, namely to the torque-free end of the shaft 14 of the blanket cylinder 2.
  • the same kind of Control namely with a load sensor 27 attached to the load-free shaft end of the inking roller 7, is selected for the control of the speed of this inking roller 7.
  • FIG. 5 A control known in printing press construction is shown schematically in FIG. 5.
  • the load 25 is a heavy roller or a heavy cylinder or a corresponding roller or cylinder system, the mass moment of inertia of which is typically more than five times as high as that of the engine 5. Nevertheless, the control of this motor / load system should be optimized for performance and controlled with a sufficiently high control quality for the number of revolutions or the angular position and the speed of the load 25. In this case, the coupling 24 of the motor and the load should not be subject to too high demands with regard to their torsional rigidity and freedom from play.
  • a mechanical actual value transmitter 21 for generating an electrical signal characteristic of the position or the speed and the position of the rotor of the motor 5 is attached to this rotor.
  • the load 25 is attached to the coupling 24, which has an elasticity and possibly some play, on the motor shaft end.
  • the coupling and the load lie outside the actual control loop. However, you can influence this via the acceleration torques that affect the motor shaft.
  • This system quickly reaches its dynamic limits with large mass inertia from load to motor. If the control becomes unstable, the motor in particular swings while the load remains relatively calm.
  • FIG. 6 shows a control in which, as already shown in FIG. 4, the reference variable for the control is generated by an encoder 21 which is attached to the load 25 and not to the motor 5.
  • This actual value transmitter 21 is free Shaft end of the load, in the exemplary embodiment attached to the free shaft end of the blanket cylinder 2 of a cylinder group 10.
  • This actual value transmitter 21 is therefore called load transmitter in the following.
  • the coupling 24 is formed by the already described toothed belt 11 with high elasticity but also high damping compared to a direct coupling or a gear coupling. In addition, this coupling 24 is free of play with a toothed belt.
  • the actual value required for the control generated by the load sensor 21, which represents the angular position of the rubber blanket cylinder 2 or its speed and the angular position thereof, is fed back to the controller 23.
  • a computer-generated setpoint from the setpoint generator 22 is compared with this actual value and used to form a control signal for the motor 5.
  • the coupling 24 and the load 25 lie within the actual control loop.
  • the load and the coupling 24 form a low-pass filter for the shocks and vibrations occurring in the controlled system, which are therefore only returned to the controller 23 to a reduced extent and therefore cannot lead to undesired excitations of the control.
  • the system consisting of controller, motor, clutch and cylinder, is itself much more damped. Resonance increases therefore do not occur to the same extent.
  • the controller can therefore be set more quickly without leaving the stable work area.
  • An actual value detection which is optionally attached to the motor 5 and is shown in the exemplary embodiment according to FIG. 6, can be used for an additional monitoring of the motor 5, for example if the motor 5 has a desired emergency shutdown option.
  • FIGS. 7 and 8 compare the dynamic behavior of the two controls according to FIGS. 5 and 6.
  • the reciprocal Wen of the reset time T i of the drive is selected as a measure of the dynamics of the control.
  • FIG. 7 shows the dynamics as a function of the mass inertia ratio from load to motor with identical coupling and identical phase reserve. This clearly shows that the control according to FIG. 6 with the actual value detection on the load is clearly superior to the actual value detection on the motor in accordance with FIG. 5, especially in the case of larger inertia conditions.
  • FIG. 8 shows the dynamics as a function of the torsional rigidity of the coupling 24 with a constant mass inertia ratio and an identical phase reserve.
  • the control according to FIG. 6 is superior to the conventional control according to FIG. 5, especially when the coupling has low torsional rigidity.
  • the setpoint and the actual value in the exemplary embodiment the setpoint or actual center position of a blanket cylinder 2, are fed to a first differential amplifier 31 to form the difference between the setpoint and actual value.
  • the difference D 1 formed there is fed to a first proportional amplifier 34 and given as a proportional amplified signal K 1 XD 1 to a second differential amplifier 35.
  • the setpoint and the actual value are each fed to a differentiating element 32 or 33, differentiated and the corresponding output signals S s and S i are fed to the second differential amplifier 35.
  • the sum formed there k1 D1 + S s - p i is amplified in a second proportional amplifier 36 and supplied to a current regulator for the motor 5 via an integrating element 37.
  • FIG. 10 shows a pressure point which is formed by three cylinder groups 10.
  • a first cylinder group 10 is on one printing side of the paper web 1, and a second and a third cylinder group 10 are on the opposite printing side this paper web 1 arranged.
  • the two cylinder groups 10 arranged on the same printing side of the paper web 1 can be mutually adjusted to the rubber cylinder 2 of the first cylinder group 10. This is indicated by two straight arrows W.
  • the two upper cylinder groups 10, which lie approximately horizontally opposite one another, are combined to form a cylinder unit 21 and as such are mounted in the machine frame independently of the lower cylinder group 10.
  • Each cylinder group 10 is again individually driven by a motor 5, as has already been the case with the two cylinder groups 10 in FIG.
  • This arrangement enables the production to be changed on the fly while the paper web 1 is continuously running.
  • one of the two swiveling rubber cylinders 2 is swiveled away, while the other is in the printing position with respect to the opposite rubber cylinder 2 of the first cylinder group 10 the plate cylinder 3 assigned to the pivoted blanket cylinder 2.
  • FIG. 11 shows an alternative pressure point also with three cylinder groups 10. What has been said about the arrangement of FIG. 10 basically also applies to the arrangement of FIG. 11. While the three cylinder groups 10 of the arrangement according to FIG. 10 each form the legs of a "Y", the cylinder groups form 10 of FIG. 11 is an upside down "Y” or a "Lambda”. In the arrangement according to FIG. 11, the two lower, horizontally opposite cylinder groups 10 are mounted in the machine frame independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the assembly or cylinder unit 21.
  • FIGS. 10 and 11 show the high flexibility of the formation of cylinder groups according to the invention and the regulation of each cylinder group according to the invention.
  • the most varied can be done in a particularly simple manner Form pressure points, for example by arranging cylinder units 21 with cylinder groups 10 (FIGS. 10 and 11) or a plurality of cylinder units 21 one above the other (FIG. 1).
  • the cylinders of the arrangements according to FIGS. 10 and 11 can also be coupled in a different way than that according to FIGS. 1 to 4, for example via a single gear.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Screen Printers (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Impact Printers (AREA)
  • Soil Working Implements (AREA)
  • Glass Compositions (AREA)
  • Printing Plates And Materials Therefor (AREA)
  • Soft Magnetic Materials (AREA)
  • Fixed Capacitors And Capacitor Manufacturing Machines (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Switches With Compound Operations (AREA)
  • Holding Or Fastening Of Disk On Rotational Shaft (AREA)
EP94810752A 1993-12-29 1994-12-27 Machine d'impression rotative, avec des cylindres porte-blanchet et porte-clichés réunisen groupes de cylindres par paires Expired - Lifetime EP0644048B2 (fr)

Priority Applications (3)

Application Number Priority Date Filing Date Title
EP99106200A EP0930159B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP01116647A EP1155826B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP99106201A EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative

Applications Claiming Priority (6)

Application Number Priority Date Filing Date Title
DE4344896A DE4344896C5 (de) 1993-12-29 1993-12-29 Antrieb für Zylinder einer Rollenrotationsdruckmaschine
DE4344912 1993-12-29
DE4344896 1993-12-29
DE19934344912 DE4344912C5 (de) 1993-12-29 1993-12-29 Antrieb eines farbübertragenden Druckzylinders einer Rollenrotationsdruckmaschine
DE4405658 1994-02-22
DE4405658A DE4405658C5 (de) 1993-12-29 1994-02-22 Antrieb für Zylinder einer Rollenrotationsdruckmaschine

Related Child Applications (2)

Application Number Title Priority Date Filing Date
EP99106201A Division EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative
EP99106200A Division EP0930159B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression

Publications (4)

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EP0644048A2 true EP0644048A2 (fr) 1995-03-22
EP0644048A3 EP0644048A3 (fr) 1995-06-28
EP0644048B1 EP0644048B1 (fr) 1999-07-07
EP0644048B2 EP0644048B2 (fr) 2005-03-23

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EP99106200A Expired - Lifetime EP0930159B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP01116647A Expired - Lifetime EP1155826B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP99106201A Expired - Lifetime EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative
EP94810752A Expired - Lifetime EP0644048B2 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative, avec des cylindres porte-blanchet et porte-clichés réunisen groupes de cylindres par paires

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EP99106200A Expired - Lifetime EP0930159B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP01116647A Expired - Lifetime EP1155826B1 (fr) 1993-12-29 1994-12-27 Machine rotative d'impression
EP99106201A Expired - Lifetime EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative

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EP (4) EP0930159B1 (fr)
JP (2) JP3424999B2 (fr)
CN (1) CN1061301C (fr)
AT (4) ATE216317T1 (fr)
DE (3) DE59410108D1 (fr)
DK (3) DK0644048T4 (fr)
ES (3) ES2157676T3 (fr)
RU (1) RU2127668C1 (fr)

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EP0788879A1 (fr) * 1996-02-09 1997-08-13 Bobst S.A. Machine d'impression rotative
DE19629605A1 (de) * 1996-07-23 1998-01-29 Koenig & Bauer Albert Ag Druckeinheit
EP0812682A3 (fr) * 1996-06-11 1998-06-10 MAN Roland Druckmaschinen AG Entraínement pour une machine à imprimer
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DE19732330A1 (de) * 1997-07-28 1999-02-04 Koenig & Bauer Albert Ag Druckeinheit
EP0860273A3 (fr) * 1997-02-19 1999-03-10 Maschinenfabrik Wifag Disposition des cylindres pour une presse rotative
EP0862999A3 (fr) * 1997-03-04 1999-04-14 MAN Roland Druckmaschinen AG Presse à bobines pour un changement de production rapide
EP0919372A1 (fr) * 1997-11-26 1999-06-02 Heidelberger Druckmaschinen Aktiengesellschaft Groupe imprimant pour une rotative
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RU2161561C1 (ru) * 1997-05-28 2001-01-10 Кениг Унд Бауер Акциенгезельшафт Привод цилиндра ротационной печатной машины
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EP1155825A3 (fr) * 2000-05-17 2002-04-10 Heidelberger Druckmaschinen Aktiengesellschaft Arrengement des groupes imprimants dans une presse rotative pour bandes
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EP1048460A3 (fr) * 1999-04-22 2002-10-09 Maschinenfabrik Wifag Influence de la déformation en éventail dans l'impression en offset humide rotative
WO2002024452A3 (fr) * 2000-09-20 2002-10-17 Koenig & Bauer Ag Unite d'impression
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WO2005056195A1 (fr) * 2003-12-12 2005-06-23 Maschinenfabrik Wifag Dispositif d'entrainement a rotor exterieur
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EP0693374B2 (fr) † 1993-07-08 2009-11-18 Baumüller Nürnberg Gmbh Dispositif d'entraînement électrique en particulier pour machines à imprimer
EP0916486B2 (fr) † 1993-07-08 2007-01-17 Baumüller Nürnberg Gmbh Système d'entrainement électrique pour le positionnemnt d'un ou plusieurs éléments dans des machines ; dispositif d'entrainement avec un indicateur d'angle et machine d'impression
EP1110722A1 (fr) * 1994-08-30 2001-06-27 MAN Roland Druckmaschinen AG Presse d'impression offset
EP1493563A3 (fr) * 1994-08-30 2009-11-25 manroland AG Machine d'impression offset
US7000539B2 (en) 1994-08-30 2006-02-21 Man Roland Druckmaschinen Ag Offset printing machine
EP0699524A3 (fr) * 1994-08-30 1997-02-05 Roland Man Druckmasch Machine d'impression offset
EP1493564A1 (fr) * 1994-08-30 2005-01-05 MAN Roland Druckmaschinen AG Machine d'impression offset
US7146908B2 (en) 1994-08-30 2006-12-12 Man Roland Druckmaschinen Ag Offset printing machine
US7159513B2 (en) 1994-08-30 2007-01-09 Man Roland Druckmaschinen Ag Offset printing machine
EP1277575A1 (fr) * 1994-08-30 2003-01-22 MAN Roland Druckmaschinen AG Presse d'impression offset
DE19603663A1 (de) * 1996-02-02 1997-08-07 Roland Man Druckmasch Druckwerk für den fliegenden Druckplattenwechsel
EP0788879A1 (fr) * 1996-02-09 1997-08-13 Bobst S.A. Machine d'impression rotative
EP0812682A3 (fr) * 1996-06-11 1998-06-10 MAN Roland Druckmaschinen AG Entraínement pour une machine à imprimer
DE19629605C2 (de) * 1996-07-23 2000-02-03 Koenig & Bauer Ag Antrieb einer Druckeinheit
DE19629605A1 (de) * 1996-07-23 1998-01-29 Koenig & Bauer Albert Ag Druckeinheit
EP0860273A3 (fr) * 1997-02-19 1999-03-10 Maschinenfabrik Wifag Disposition des cylindres pour une presse rotative
EP0862999A3 (fr) * 1997-03-04 1999-04-14 MAN Roland Druckmaschinen AG Presse à bobines pour un changement de production rapide
US6019039A (en) * 1997-03-04 2000-02-01 Man Roland Druckmaschinen Ag Web-fed rotary printing press for rapid change in production
US6935234B2 (en) * 1997-04-18 2005-08-30 Heidelberger Druckmaschinen Ag Lithographic newspaper printing press
RU2161561C1 (ru) * 1997-05-28 2001-01-10 Кениг Унд Бауер Акциенгезельшафт Привод цилиндра ротационной печатной машины
US6202555B1 (en) 1997-05-28 2001-03-20 Koenig & Bauer Aktiengesellschaft Driving mechanism for a cylinder of a rotary printing machine
EP0882588A1 (fr) * 1997-06-02 1998-12-09 Maschinenfabrik Wifag ContrÔle du repérage des cylindres dans une machine à imprimer rotative pour bandes
DE19723043C2 (de) * 1997-06-02 2002-08-01 Wifag Maschf Verfahren und Vorrichtung zur Regelung eines Umfangregisters von auf eine Bahn druckenden Zylindern einer Rollenrotationsdruckmaschine
DE19723059A1 (de) * 1997-06-02 1998-12-03 Wifag Maschf Registerhaltige Abstimmung von Druckzylindern einer Rollenrotationsmaschine
EP0882587A1 (fr) * 1997-06-02 1998-12-09 Maschinenfabrik Wifag ContrÔle du repérage des cylindres dans une machine à imprimer rotative pour bandes
FR2764545A1 (fr) * 1997-06-12 1998-12-18 Roland Man Druckmasch Dispositif d'entrainement pour une unite d'impression d'une presse rotative a imprimer
DE19724765A1 (de) * 1997-06-12 1998-12-17 Roland Man Druckmasch Antrieb für ein Druckwerk einer Rotationsdruckmaschine
RU2176599C2 (ru) * 1997-07-28 2001-12-10 Кениг Унд Бауер Акциенгезельшафт Печатная секция офсетной печатной машины (варианты)
WO1999006211A1 (fr) * 1997-07-28 1999-02-11 Koenig & Bauer Ag Unite d'impression
US6332397B1 (en) 1997-07-28 2001-12-25 Koenig & Bauer Aktiengesellschaft Print unit
EP1052092A3 (fr) * 1997-07-28 2002-03-27 Koenig & Bauer Aktiengesellschaft Unité d'impression
DE19732330C2 (de) * 1997-07-28 2001-04-19 Koenig & Bauer Ag Antrieb für eine Druckeinheit
CN1089684C (zh) * 1997-07-28 2002-08-28 柯尼格及包尔公开股份有限公司 印刷装置
DE19732330A1 (de) * 1997-07-28 1999-02-04 Koenig & Bauer Albert Ag Druckeinheit
DE19820271C2 (de) * 1997-11-14 2000-05-25 Baumueller Nuernberg Gmbh Antriebsanordnung mit einem oder mehreren Elektromotoren
US6032579A (en) * 1997-11-26 2000-03-07 Heidelberger Druckmaschinen Ag Printing unit for a web-fed rotary printing press
EP0919372A1 (fr) * 1997-11-26 1999-06-02 Heidelberger Druckmaschinen Aktiengesellschaft Groupe imprimant pour une rotative
US6050185A (en) * 1997-11-26 2000-04-18 Heidelberger Druckmaschinen Ag Printing unit for a web-fed rotary printing press
CN1098160C (zh) * 1997-11-26 2003-01-08 海德堡印刷机械股份公司 用于卷筒纸轮转印刷机的印刷组件
WO1999030906A1 (fr) * 1997-12-12 1999-06-24 Koenig & Bauer Aktiengesellschaft Systeme d'entrainement pour cylindres d'une machine a imprimer
CN1099960C (zh) * 1997-12-12 2003-01-29 柯尼格及包尔公开股份有限公司 印刷机滚筒驱动机构
DE19755316A1 (de) * 1997-12-12 1999-06-17 Koenig & Bauer Ag Antrieb für Zylinder einer Druckeinheit
DE19755316C2 (de) * 1997-12-12 1999-10-07 Koenig & Bauer Ag Antrieb für Zylinder einer Druckeinheit
DE19860540A1 (de) * 1998-12-30 2000-07-20 Koenig & Bauer Ag Mehrfarben-Rollenrotationsdruckmaschine
EP1048460A3 (fr) * 1999-04-22 2002-10-09 Maschinenfabrik Wifag Influence de la déformation en éventail dans l'impression en offset humide rotative
EP1457330A3 (fr) * 2000-05-17 2007-06-13 Koenig & Bauer Aktiengesellschaft L'entraînement indépendent de deuxième cylindre à lames de pliage
EP1457329A3 (fr) * 2000-05-17 2007-06-13 Koenig & Bauer Aktiengesellschaft Cylindre déplacable à lames de pliage
EP1155825A3 (fr) * 2000-05-17 2002-04-10 Heidelberger Druckmaschinen Aktiengesellschaft Arrengement des groupes imprimants dans une presse rotative pour bandes
DE10046375B4 (de) * 2000-09-20 2005-04-07 Koenig & Bauer Ag Antrieb einer Druckeinheit
EP1598187A3 (fr) * 2000-09-20 2007-10-03 Koenig & Bauer Aktiengesellschaft Unité d'impression
WO2002024457A1 (fr) * 2000-09-20 2002-03-28 Koenig & Bauer Aktiengesellschaft Entrainement d'une unite d'impression
WO2002024453A1 (fr) * 2000-09-20 2002-03-28 Koenig & Bauer Aktiengesellschaft Unites d'impression a ensemble d'entrainement et accouplement
DE10046367B4 (de) * 2000-09-20 2005-10-13 Koenig & Bauer Ag Antrieb einer Druckeinheit
WO2002024452A3 (fr) * 2000-09-20 2002-10-17 Koenig & Bauer Ag Unite d'impression
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Also Published As

Publication number Publication date
JPH11268249A (ja) 1999-10-05
EP0644048B2 (fr) 2005-03-23
ATE200449T1 (de) 2001-04-15
DK0930160T3 (da) 2002-07-29
RU2127668C1 (ru) 1999-03-20
EP0930159B1 (fr) 2001-04-11
ATE181879T1 (de) 1999-07-15
DK0644048T4 (da) 2005-05-02
EP1155826A2 (fr) 2001-11-21
ES2157676T3 (es) 2001-08-16
ES2135557T3 (es) 1999-11-01
DE59410108D1 (de) 2002-05-23
EP0930160B1 (fr) 2002-04-17
RU94045261A (ru) 1996-12-10
DE59409732D1 (de) 2001-05-17
EP0644048A3 (fr) 1995-06-28
ES2175867T3 (es) 2002-11-16
EP1155826B1 (fr) 2011-09-14
JP3424999B2 (ja) 2003-07-07
EP0930159A1 (fr) 1999-07-21
EP1155826A3 (fr) 2002-06-26
JP3415469B2 (ja) 2003-06-09
ATE216317T1 (de) 2002-05-15
DK0644048T3 (da) 2000-01-31
DE59408463D1 (de) 1999-08-12
ATE524311T1 (de) 2011-09-15
CN1122279A (zh) 1996-05-15
JPH0834108A (ja) 1996-02-06
DK0930159T3 (da) 2001-08-13
ES2135557T5 (es) 2005-09-01
CN1061301C (zh) 2001-01-31
EP0930160A1 (fr) 1999-07-21
EP0644048B1 (fr) 1999-07-07

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