EP0930160B1 - Rotationsdruckmaschine - Google Patents

Rotationsdruckmaschine Download PDF

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Publication number
EP0930160B1
EP0930160B1 EP99106201A EP99106201A EP0930160B1 EP 0930160 B1 EP0930160 B1 EP 0930160B1 EP 99106201 A EP99106201 A EP 99106201A EP 99106201 A EP99106201 A EP 99106201A EP 0930160 B1 EP0930160 B1 EP 0930160B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
cylinders
drive motor
motor
driven
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.)
Expired - Lifetime
Application number
EP99106201A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP0930160A1 (de
Inventor
Felix Schneider
Dieter Koch
Andreas Miescher
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 DE19934344912 external-priority patent/DE4344912C5/de
Priority claimed from DE19934344896 external-priority patent/DE4344896C5/de
Priority claimed from DE4405658A external-priority patent/DE4405658C5/de
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Priority to EP01116647A priority Critical patent/EP1155826B1/de
Publication of EP0930160A1 publication Critical patent/EP0930160A1/de
Application granted granted Critical
Publication of EP0930160B1 publication Critical patent/EP0930160B1/de
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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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 Rotary printing machine for individual cylinder groups and a drive control therefor.
  • a printing press is known, the cylinders and Rolls are driven by a main motor via a toothed belt.
  • the 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 allows vibrations in the drive wheel train only difficult to keep low or with great technical effort. Since the load side Moment of inertia is very large, this known scheme is slow and points at most a low control dynamic.
  • DE 41 38 479 A1 proposes to drive the cylinders of the printing press by one electric motor each.
  • a control system for such a printing press is included known individually driven cylinders.
  • the individual drives can the cylinder and its drive controller can be combined into pressure point groups as required become.
  • the pressure point groups are assigned to folders, by to whom they get their position reference.
  • the proposed guidance system consists of essentially from a fast BUS system for the individual drives and Drive controller of a pressure point group and a higher-level control system for Administration of pressure point groups.
  • a printing machine known from JP-A 63-236651 has printing units which are individually driven by their own drive motors.
  • the printing units comprise mechanically in pairs for driving them together coupled blanket cylinders and plate cylinders.
  • the motors drive up the plate cylinders of the printing units. From the plate cylinders is over Gear couplings driven on the blanket cylinders.
  • the engines are sitting directly on the shafts of the plate cylinders. Regulators of the motors Machine control signals as setpoint signals and engine speed and engine speed signals supplied as actual value signals. The regulation of the engines takes place depending on a comparison between the setpoint signals and the Actual value signals, i.e. based on the difference between the setpoint signals and the Actual value signals on the motor side.
  • the present invention has set itself the task of being highly flexible create usable, yet economical rotary printing press.
  • blanket cylinders and plate cylinders form a rotary printing press in pairs a cylinder group, each with a blanket cylinder and a plate cylinder are mechanically coupled together and together are driven by a separate drive motor for each cylinder group.
  • each with its own Drive motors can be more technical and economical in a rotary printing press
  • Optimal pressure points are formed.
  • pressure points in this context understood the pairs of cylinders, between which one paper web to be printed runs through and is printed on one or both sides. Accordingly, there is one for each printing point Cylinder group and a corresponding impression cylinder.
  • Drive technology are, however the printing points of the printing press are mechanically independent, d. H. the printing points of the printing press are electrically coupled to one another.
  • the blanket cylinder is preferred for the cylinder groups driven, which in turn via the mechanical coupling to the Drives plate cylinders of the same cylinder group.
  • the drive can also the plate cylinder shaft drive so that the blanket cylinder only from the mechanical coupling Plate cylinder is driven.
  • the blanket cylinder on the other hand is decisive for the Positional accuracy or circumferential register setting.
  • the first solution has the advantage that the cylinder, ultimately with a paper web to be printed comes into direct contact, not only with a game that may be affected Transmission link must be driven.
  • a cylinder group can be around an impression cylinder for the Blanket cylinders are expanded.
  • This third cylinder of the so formed Cylinder group is mechanically coupled to the blanket cylinder, preferably through another gear coupling.
  • Such a cylinder group already provides represents a printing point, between whose blanket and impression cylinder the one to be printed Paper web is passed through.
  • the impression cylinder is a Central cylinder of a cylinder unit with several cylinder groups, for example a cylinder unit with nine or ten cylinders.
  • too preferred embodiment of the invention is such a central cylinder of one own drive motor driven.
  • This type of summary grants the maximum versatility for a cylinder unit.
  • each of the central cylinder associated cylinder groups from blanket and Plate cylinders reversed individually and independently of the other cylinder groups be like this for example for alternating pressure or for the flying Plate change is required.
  • the output from a drive motor takes place on the respective cylinder group by means of a toothed belt.
  • a timing belt has a high elasticity.
  • One group of cylinders is through the use of a timing belt given possibility of a high damping of a drive motor and the driven cylinders existing mechanical system of great value, such as will be explained later.
  • Opposite one Gear drive between the drive motor and the driven cylinder one Cylinder group has a toothed belt Advantage of a game-free run and a not absolutely firm run Transmission ratio.
  • the intermeshing Gears can be spur or helical. With helical gears for the side register adjustment the blanket cylinder is shifted lengthways while its drive and / or driven gears remain stationary. Otherwise, with the side register would also be a circumferential register adjustment required. When using straight toothed gears the blanket cylinder together with its fixed gear or gears simply moved lengthways.
  • the inking roller or the inking rollers or dampening rollers of an inking unit or one Ink and dampening units that are assigned to a cylinder group can or can be mechanically coupled to this cylinder group, so that the Ink roller or the ink rollers from the drive motor of this cylinder group with are driven.
  • the technical control effort can be low being held.
  • the mechanical coupling of the inking unit in the In terms of the modular principle pursued by the invention not quite as ideal as that more preferred self-drive for the roller or the rollers of the inking unit.
  • each has Inking unit has its own drive motor for its inking rollers.
  • Such a drive motor also drives preferably over a backlash-free toothed belt with high Damping and, if necessary, the inking roller via a reduction gear or in the case of several inking rollers, the one corresponding to the plate cylinder Ink roller closest to the cylinder group.
  • the peripheral speed this ink roller advantageously adjustable, especially with negative slip against the plate cylinder, the peripheral speed the inking roller is preferably slightly less than that of the corresponding plate cylinder is.
  • the position or speed of a cylinder are regulated known in which a mechanical encoder on the motor side for detecting the Motor speed or the rotor angular position of the motor for a target / actual comparison of the Motor control is used.
  • this known regulation comes up with larger increasing inertia from the load to the motor to their dynamic limits. If the actual position is measured on the motor shaft, then lie both coupling and mechanical load outside the actual control loop. However, you can do this via the acceleration torques that affect the motor shaft influence.
  • the engine which in this case is an essential one This means that the mass is smaller than the coupling and the cylinder affected.
  • the load torque is heavily frequency-dependent, which ultimately determines the dynamic behavior of the system.
  • the set springs are tensioned first by the motor are closest.
  • the engine torque caused by the controller accelerates parts of the coupling and subsequently the cylinder or the driven roller.
  • Energy is in the springs as well at this time stored in the mass movement, the division of which is constantly changing.
  • the motor may have assumed the correct position within a short time, but is again distracted by the occurring mass forces, resulting in a leads further control process.
  • the system must go through a relatively slow controller controlled, stabilized.
  • the present invention has therefore also set itself the task of To create regulation with which the position and / or in a rotary printing press the speed of a cylinder or roller driven by a motor is optimized for performance and with a sufficiently high control quality, d. H. with regard to the Dynamics and the speed or position accuracy can be regulated.
  • the Regulation should be inexpensive and not too high demands on the coupling of engine and load, especially the torsional stiffness and zero backlash of the Make coupling.
  • At least the drive motors are preferably the same Printing side of a paper web working cylinder groups of a cylinder unit position control. So-called ideal position control is preferred, i.e. a instantaneous position control with following error. On this, out However, technical, desirable, complex type of position control can also be dispensed with. A simple position control also provides one preferred, in particular cheaper, embodiment of the invention.
  • the regulation of the position and / or the speed of the cylinder to be regulated one Cylinder group or a roller of an inking unit is carried out by means of a controller for the drive motor through the target / actual comparison of the output signals a setpoint transmitter and an actual value transmitter, this actual value transmitter Position and / or the speed of the cylinder or the roller detected.
  • a controller for the drive motor through the target / actual comparison of the output signals a setpoint transmitter and an actual value transmitter, this actual value transmitter Position and / or the speed of the cylinder or the roller detected.
  • the known regulations for rotary printing presses thus become a load generator used for the regulation.
  • a mechanical encoder on the motor side to record the motor speed or the rotor angular position of the motor for the target / actual comparison of the motor control used.
  • the drive motor can even with the dual mass transducer be disregarded.
  • the load acting as a low-pass filter is insensitive against the vibrations of the much smaller motor. on the other hand the effects of the load on the drive motor can be neglected become.
  • the last but not least because of their simplicity Regulation has the further advantage that it is simply the large bandwidth of the Mass inertia between the load and the motor and on itself in the course of Operating parameters, such as the elasticity of a coupling, can be adjusted.
  • the actual value transmitter figuratively speaking, moved from the motor side to the load side forms the main controlled variable for the controller of the motor, d. H. the engine is powered by the Load side guided by their actual value.
  • the invention is not a mechanical actual value transmitter for the detection the position or speed of the engine in the context of the regulation of the engine needed.
  • Actual value detection which may be integrated in the motor, can be advantageous for pure drive monitoring, if necessary for an engine emergency shutdown be used.
  • the actual value encoder for the control is torque-free Shaft end of the driven cylinder of a cylinder group or attached roller of an inking unit.
  • Electric asynchronous motors are particularly advantageous as the drive motors used. So far, an asynchronous motor has only been used when using of a large engine had to drive a small load. For the present case, in which a drive motor is a cylinder group or the rollers of a Inking unit drives, so the driven load is comparatively high Has moment of inertia compared to the drive motor is the use not known from asynchronous motors. For the purposes of Control with a load encoder instead of a motor encoder are asynchronous motors particularly suitable. Compared to that for the applications in question DC motors used so far have higher asynchronous motors Field stiffness on, so that their use the dynamics and quality of control to be controlled Systems improved. The use of other types of motor, for example DC motors, is however not fundamentally excluded.
  • the stability of the scheme is due to the preferred use of a backlash-free Toothed belt with high damping as a coupling between the motor and the load improved.
  • the drive motor can even with the two-mass oscillator in question be disregarded.
  • the load acting as a low-pass filter is insensitive against the vibrations of the much smaller motor. on the other hand the effects of the load on the drive motor can be neglected become.
  • a pressure point shown in Fig. 1 which as such is not the subject of Claims are heard, but their explanation serves to be a printable Paper web 1 between the two opposing blanket cylinders 2 passed through two cylinder groups 10.
  • the two cylinder groups 10 will each by the blanket cylinder 2 and an associated plate cylinder 3rd formed, which are mechanically coupled to each other for the common drive.
  • the mechanical coupling is shown schematically by a dash between the centers of the two cylinders 2 and 3 indicated.
  • the blanket cylinders 2 of each cylinder group 10 are through a three-phase motor 5 driven.
  • the configuration according to Fig. 1, at of only one blanket cylinder 2 and one plate cylinder 3 by one mechanical coupling are combined to form a cylinder group 10 through their simple design and the highest possible degree of configuration freedom in the formation of pressure points or pressure point groups.
  • Fig. 2 shows a variant for the formation of a pressure point, in which an impression cylinder 6 for the blanket cylinder 2 with this blanket cylinder 2 mechanically is coupled.
  • the cylinder group 10 is made up of the Blanket cylinder 2, its impression cylinder 6 and the plate cylinder 3 and their mechanical coupling together, so that the pressure point by a single Cylinder group 10 is formed.
  • this Plate cylinder 3 assigned to cylinders is driven by a three-phase motor 5.
  • a cylinder group is its constant delivery behavior because of the mechanical Coupling the blanket cylinder 2 with its impression cylinder 6 and that due to this mechanical coupling, there is no direct interference between the Cylinder 2 and 6 takes place.
  • the impression cylinder 6 is a steel cylinder, for example a central cylinder of a nine or ten cylinder unit.
  • the assignment of the motors 5 to the blanket cylinders 2 and the plate cylinders 3 can be interchanged in both print point examples.
  • the drive of the Plate cylinder 3 has the advantage that the cylinder group 10 reversed more easily can be while in the other case when driving the blanket cylinder 2 on the paper web 1 directly printing cylinder is driven and thereby Drive free of playful transmission elements, such as gears, is possible.
  • a cylinder unit 20 is shown, consisting of a central Steel cylinders 6 and four cylinder groups 10 assigned to this central cylinder 6.
  • a blanket cylinder 2 and a plate cylinder 3 are each in this embodiment combined into a cylinder group 10.
  • the central cylinder 6 with one of the four cylinder groups 10 is a cylinder group form according to the variant shown in Fig. 2. This would make the own engine 5 can be saved for the central cylinder 6.
  • Cylinder unit 20 has the advantage in terms of printing technology that the so-called fan-out effect very limited.
  • Each of the blanket cylinders 2 is also easily switchable to rubber / rubber production. The possibilities Different types of alternating pressure will not be reversed either limited.
  • a cylinder group formed from pairs of cylinders 10 in terms of their configurability, a concept with each individually driven cylinders equal.
  • the interaction is one of a pair of blanket / plate cylinders 2, 3 existing cylinder group 10 shown with an ink roller 7.
  • the inking roller 7 has its own drive by a motor 5, which too the engine 5 for the cylinder group 10 may be identical, but need not be.
  • the motor 5 for the inking roller 7 drives via a toothed belt 15 and a pair of gearwheels 16, 17, wherein the gear 17 sits on the shaft of the ink roller 7, the Ink roller 7 on.
  • the different moments of inertia of the motor 5 and the inking roller 7 are at a suitable choice of gear ratios Output via the toothed belt 15 and the gear pair 16, 17 disarmed.
  • the peripheral speed of the ink roller 7 is easily adjustable negative slip compared to the plate cylinder 3. This can increase the risk counteracted that the mechanical formed by a pair of gears 12, 13 Coupling between the blanket cylinder 2 and the plate cylinder 3 the tooth mesh is lifted.
  • the cylinder group 10 is driven by the motor 5 via the toothed belt 11 on the blanket cylinder 2.
  • the mechanical coupling between the Form blanket cylinder 2 and plate cylinder 3 of the same cylinder group 10 the two gears 12 and 13.
  • This toothed belt 11 is the elastic coupling member between the Engine 5 and the driven cylinder group 10.
  • the Timing belt 11 achieved a very high damping of the motor / load system 5, 10.
  • the motors 5 for the cylinder group 10 or the inking roller 7 are three-phase motors with high field stiffness.
  • the two gears 12 and 13, which the mechanical coupling between the Form blanket cylinder 2 and the plate cylinder 3 can be helical or straight toothed gears.
  • the Blanket cylinder 2 longitudinally shifted during the side register adjustment, while the Gear 12 and the corresponding gear for timing belt 11 remain stationary, i.e. these two gears are longitudinally displaceable on the cylinder shaft 14 stored.
  • 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 typically more than five times that of the Motors 5 is. Nevertheless, the regulation of this motor / load system should optimize performance and with a sufficiently high control quality for the number of revolutions or the angular position and the speed of the load 25 are regulated.
  • the coupling 24 of The engine and load are not too high in terms of their requirements Torsional rigidity and freedom from play.
  • This system pushes from load to load at high inertia Engine quickly to its dynamic limits. If the control becomes unstable, it vibrates especially the engine, while the load remains relatively calm.
  • 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 connected to the load 25 and is not attached to the engine 5.
  • This actual value transmitter 21 is free Shaft end of the load, in the exemplary embodiment at the free shaft end of the blanket cylinder 2 of a cylinder group 10 attached.
  • This actual value transmitter 21 is in therefore called the following loader.
  • the coupling 24 is already through the described toothed belt 11 with compared to a direct coupling or Gear coupling of high elasticity but also high damping. In addition is this coupling 24 with a toothed belt without play.
  • a computer generated setpoint from the setpoint generator 22 is compared with this actual value and for formation a control signal for the motor 5 used.
  • the coupling 24 and the load 25 lie within the actual one Control loop.
  • the load and the coupling 24 form a low-pass filter for the in
  • the controlled system creates shocks and vibrations, which are therefore only in are reduced in the controller 23 and therefore not too unwanted suggestions of the regulation can lead.
  • This creates the dynamic and also the control quality compared to conventional systems, even with otherwise same coupling significantly increased.
  • the system consisting of controller, motor, The clutch and cylinder are already much more damped. resonance increases therefore do not occur to the same extent.
  • the controller can therefore set faster without leaving the stable work area.
  • a possibly attached to the motor 5, in the exemplary embodiment according to FIG. 6 The actual value acquisition shown can be used for additional monitoring of the motor 5. used for example in a desired emergency shutdown option of the engine 5 become.
  • FIGS. 7 and 8 compare the dynamic behavior of the two controls according to FIGS. 5 and 6.
  • the reciprocal value of the reset time T i of the drive is selected as a measure of the dynamics of the control.
  • FIG. 7 shows the dynamics as a function of the mass inertia ratio from load to motor with identical coupling and identical phase reserve. This clearly shows that the control according to FIG. 6 with the actual value detection on the load is clearly superior to the actual value detection on the motor, in accordance with FIG.
  • the setpoint and actual value in the exemplary embodiment the setpoint or actual center position of a blanket cylinder 2, are fed to a first differential amplifier 31 to form the difference between the setpoint and actual value.
  • the difference D 1 formed there is fed to a first proportional amplifier 34 and applied to a second differential amplifier 35 as a proportionally amplified signal K 1 XD 1 .
  • the setpoint and the actual value are each fed to a differentiating element 32 or 33, differentiated and the corresponding output signals S s and S i are fed to the second differential amplifier 35.
  • the sum k 1 D 1 + S s - S i formed there is amplified in a second proportional amplifier 36 and fed to a current regulator for the motor 5 via an integrating element 37.

Landscapes

  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Rotary Presses (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Screen Printers (AREA)
  • Soil Working Implements (AREA)
  • Impact Printers (AREA)
  • Glass Compositions (AREA)
  • Printing Plates And Materials Therefor (AREA)
  • Treatment Of Fiber Materials (AREA)
  • Holding Or Fastening Of Disk On Rotational Shaft (AREA)
  • Switches With Compound Operations (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Soft Magnetic Materials (AREA)
  • Fixed Capacitors And Capacitor Manufacturing Machines (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)
EP99106201A 1993-12-29 1994-12-27 Rotationsdruckmaschine Expired - Lifetime EP0930160B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP01116647A EP1155826B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE19934344912 DE4344912C5 (de) 1993-12-29 1993-12-29 Antrieb eines farbübertragenden Druckzylinders einer Rollenrotationsdruckmaschine
DE4344912 1993-12-29
DE19934344896 DE4344896C5 (de) 1993-12-29 1993-12-29 Antrieb für Zylinder einer Rollenrotationsdruckmaschine
DE4344896 1993-12-29
DE4405658A DE4405658C5 (de) 1993-12-29 1994-02-22 Antrieb für Zylinder einer Rollenrotationsdruckmaschine
DE4405658 1994-02-22
EP94810752A EP0644048B2 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine mit paarweise zu Zylindergruppen zusammengefassten Gummituch- und Platten- bzw. Formzylinder

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP94810752A Division EP0644048B2 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine mit paarweise zu Zylindergruppen zusammengefassten Gummituch- und Platten- bzw. Formzylinder

Related Child Applications (1)

Application Number Title Priority Date Filing Date
EP01116647A Division EP1155826B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine

Publications (2)

Publication Number Publication Date
EP0930160A1 EP0930160A1 (de) 1999-07-21
EP0930160B1 true EP0930160B1 (de) 2002-04-17

Family

ID=27205938

Family Applications (4)

Application Number Title Priority Date Filing Date
EP94810752A Expired - Lifetime EP0644048B2 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine mit paarweise zu Zylindergruppen zusammengefassten Gummituch- und Platten- bzw. Formzylinder
EP99106200A Expired - Lifetime EP0930159B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine
EP01116647A Expired - Lifetime EP1155826B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine
EP99106201A Expired - Lifetime EP0930160B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine

Family Applications Before (3)

Application Number Title Priority Date Filing Date
EP94810752A Expired - Lifetime EP0644048B2 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine mit paarweise zu Zylindergruppen zusammengefassten Gummituch- und Platten- bzw. Formzylinder
EP99106200A Expired - Lifetime EP0930159B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine
EP01116647A Expired - Lifetime EP1155826B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine

Country Status (8)

Country Link
EP (4) EP0644048B2 (es)
JP (2) JP3424999B2 (es)
CN (1) CN1061301C (es)
AT (4) ATE200449T1 (es)
DE (3) DE59410108D1 (es)
DK (3) DK0644048T4 (es)
ES (3) ES2135557T5 (es)
RU (1) RU2127668C1 (es)

Families Citing this family (61)

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Publication number Priority date Publication date Assignee Title
DE4322744C2 (de) † 1993-07-08 1998-08-27 Baumueller Nuernberg Gmbh Elektrisches Antriebssystem und Positionierverfahren zur synchronen Verstellung mehrerer dreh- und/oder verschwenkbarer Funktionsteile in Geräten und Maschinen, Antriebsanordnung mit einem Winkellagegeber und Druckmaschine
DE4430693B4 (de) * 1994-08-30 2005-12-22 Man Roland Druckmaschinen Ag Antriebe für eine Rollenrotations-Offsetdruckmaschine
US6644184B1 (en) 1995-02-09 2003-11-11 Man Roland Druckmaschinen Ag Offset printing machine
EP1110722B1 (de) * 1994-08-30 2003-04-09 MAN Roland Druckmaschinen AG Offsetdruckmaschine
DE19603663A1 (de) * 1996-02-02 1997-08-07 Roland Man Druckmasch Druckwerk für den fliegenden Druckplattenwechsel
CH691225A8 (fr) * 1996-02-09 2001-08-15 Bobst Sa Machine d'impression rotative.
DE19623223C2 (de) * 1996-06-11 2001-05-17 Roland Man Druckmasch Antrieb für eine Druckmaschine
DE19629605C2 (de) * 1996-07-23 2000-02-03 Koenig & Bauer Ag Antrieb einer Druckeinheit
DE29702923U1 (de) * 1997-02-19 1997-03-27 Maschinenfabrik Wifag, Bern Zylindereinheit für eine Rollenrotationsdruckmaschine
DE59802993D1 (de) * 1997-03-04 2002-03-21 Roland Man Druckmasch Offsetdruckmaschine für schnellen Produktionswechsel
US6374731B1 (en) * 1997-04-18 2002-04-23 Heidelberger Druckmaschinen Ag Lithographic newspaper printing press
US6050185A (en) * 1997-11-26 2000-04-18 Heidelberger Druckmaschinen Ag Printing unit for a web-fed rotary printing press
EP1157831B1 (de) 1997-05-28 2003-01-08 Koenig & Bauer Aktiengesellschaft Antrieb für einen Zylinder einer Rotationsdruckmaschine
DE19723059A1 (de) * 1997-06-02 1998-12-03 Wifag Maschf Registerhaltige Abstimmung von Druckzylindern einer Rollenrotationsmaschine
EP0882588B1 (de) 1997-06-02 2001-11-07 Maschinenfabrik Wifag Registerhaltige Abstimmung von Druckzylindern einer Rollenrotationsmaschine
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
DE19724765A1 (de) * 1997-06-12 1998-12-17 Roland Man Druckmasch Antrieb für ein Druckwerk einer Rotationsdruckmaschine
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EP0644048A2 (de) 1995-03-22
ES2135557T5 (es) 2005-09-01
ATE524311T1 (de) 2011-09-15
DK0644048T3 (da) 2000-01-31
EP0644048B1 (de) 1999-07-07
EP0930160A1 (de) 1999-07-21
DK0644048T4 (da) 2005-05-02
ES2175867T3 (es) 2002-11-16
RU94045261A (ru) 1996-12-10
EP1155826A2 (de) 2001-11-21
RU2127668C1 (ru) 1999-03-20
CN1122279A (zh) 1996-05-15
DK0930159T3 (da) 2001-08-13
EP0930159B1 (de) 2001-04-11
EP0644048A3 (de) 1995-06-28
EP0930159A1 (de) 1999-07-21
EP1155826A3 (de) 2002-06-26
DE59408463D1 (de) 1999-08-12
ATE200449T1 (de) 2001-04-15
ES2157676T3 (es) 2001-08-16
JPH0834108A (ja) 1996-02-06
JP3415469B2 (ja) 2003-06-09
DE59409732D1 (de) 2001-05-17
JPH11268249A (ja) 1999-10-05
ATE181879T1 (de) 1999-07-15
EP1155826B1 (de) 2011-09-14
DE59410108D1 (de) 2002-05-23
EP0644048B2 (de) 2005-03-23
JP3424999B2 (ja) 2003-07-07
DK0930160T3 (da) 2002-07-29
ES2135557T3 (es) 1999-11-01
CN1061301C (zh) 2001-01-31
ATE216317T1 (de) 2002-05-15

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