EP1155826A2 - Machine rotative d'impression - Google Patents

Machine rotative d'impression Download PDF

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Publication number
EP1155826A2
EP1155826A2 EP01116647A EP01116647A EP1155826A2 EP 1155826 A2 EP1155826 A2 EP 1155826A2 EP 01116647 A EP01116647 A EP 01116647A EP 01116647 A EP01116647 A EP 01116647A EP 1155826 A2 EP1155826 A2 EP 1155826A2
Authority
EP
European Patent Office
Prior art keywords
cylinder
rotary printing
printing machine
cylinders
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
EP01116647A
Other languages
German (de)
English (en)
Other versions
EP1155826B1 (fr
EP1155826A3 (fr
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 DE4344896A external-priority patent/DE4344896C5/de
Priority claimed from DE19934344912 external-priority patent/DE4344912C5/de
Priority claimed from DE4405658A external-priority patent/DE4405658C5/de
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Publication of EP1155826A2 publication Critical patent/EP1155826A2/fr
Publication of EP1155826A3 publication Critical patent/EP1155826A3/fr
Application granted granted Critical
Publication of EP1155826B1 publication Critical patent/EP1155826B1/fr
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 From DE 38 28 638 C1 a printing press is known, its cylinders and rollers are driven by a main motor via a toothed belt.
  • the engine will regulated on the basis of actual values tapped on the load side.
  • the cylinders and rollers of the Printing presses are coupled to one another via a drive wheel train. Through the described regulation, vibrations in the drive wheel train are difficult or keep low with great technical effort. Because the load moment of inertia is very large, this known regulation is slow and at most has a low one Control dynamics.
  • 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 pressure point groups are assigned to folders, from which they receive theirs Get position reference.
  • the proposed control system essentially consists of a fast BUS system for the individual drives and the drive controllers Pressure point group and a superordinate control system for the administration of the 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 coupled in pairs for their common drive Blanket cylinder and plate cylinder.
  • the motors drive on each 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 Motor 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 cylinder and plate cylinder form one Rotary printing machine in pairs a cylinder group, in each case one Blanket cylinder and a plate cylinder are mechanically coupled and are driven together by a separate drive motor for each cylinder group.
  • each with its own drive motors can be at a Rotary printing machine optimal in technical and economic terms Pressure points are formed.
  • Pressure points in this context each understood the pairs of cylinders, between which a paper web to be printed runs through and is printed on one or both sides. Accordingly belong to one Pressure point formed according to the invention in each case one cylinder group and one corresponding impression cylinder, which may belong to the cylinder group, but not got to. In the latter case, one printing point is assigned to two by one Cylinder groups formed.
  • the pressure points are Printing press mechanically independent in both cases, d. H. the pressure points the printing press are electrically coupled together.
  • the Blanket cylinder driven, which in turn via the mechanical coupling on the Drives plate cylinders of the same cylinder group.
  • the drive can also drive the plate cylinder shaft, so that the blanket cylinder only via the mechanical coupling of the plate cylinder is driven.
  • the Blanket cylinders are decisive for the positional accuracy or Circumference register setting.
  • the first solution has the advantage that the Cylinder that ultimately comes into direct contact with a paper web to be printed comes, not only via a transmission element that may be subject to play must be driven.
  • One cylinder group is on one side of the pressure and two cylinder groups are on the one Opposite pressure side of a paper web running between them.
  • the rubber cylinder preferably forms the one on the printing side of the paper web arranged cylinder group the impression cylinder for the other two Rubber cylinder arranged on the opposite printing side of the paper web Cylinder groups, both of which are advantageously operated alternately can.
  • This configuration offers the greatest versatility for a rubber / rubber production, because with continuous production the two mutually rubber cylinder can be configured for a change in pressure can. This is done by changing the plate of a rubber cylinder that is not in use assigned plate cylinder.
  • Each cylinder group can be stored in a single frame his.
  • the two one printing side of the paper web are horizontal opposite groups of cylinders to a stored in a frame Cylinder unit summarized.
  • a cylinder group can according to the invention around an impression cylinder for the Blanket cylinders are expanded.
  • This third cylinder of the so formed Cylinder group can be mechanically coupled to the blanket cylinder, preferably by a further gear coupling.
  • Such a cylinder group represents already represents a printing point, between the blanket and impression cylinder which too printing paper web is passed through.
  • the impression cylinder can be a steel or can also be another blanket cylinder for double-sided printing.
  • Such a An impression cylinder can in particular also be a central cylinder of a cylinder unit with, for example, 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 assigned cylinder groups from blanket and plate cylinders can be reversed individually and independently of the other cylinder groups, like this for example for alternating pressure or for flying plate changes.
  • the output from a drive motor takes place on the respective cylinder group preferably by means of a toothed belt.
  • a toothed belt Possibility of high damping of a drive motor and the driven cylinders existing mechanical system of great value, as yet is explained.
  • the invention also permits direct drive, which can even be advantageous for small cylinders.
  • a toothed belt has the advantage of a backlash-free running and a not absolutely fixed gear ratio.
  • gears for the mechanical coupling between the cylinders inside a group of cylinders preferably provided gears, although others Transmission links are also conceivable.
  • the intermeshing Gears can be spur or helical. With helical gears for the side register adjustment the blanket cylinder is shifted lengthways while his drive and / or driven gears remain stationary according to the invention. Otherwise, with the side register would also be a circumferential register adjustment required. When using straight toothed gears the blanket cylinder along with its fixed gear or gears postponed.
  • 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 According to the invention mechanically coupled to this cylinder group, so that the Ink roller or the ink rollers from the drive motor of this cylinder group with are driven. With this solution, the technical control effort can be low being held.
  • the mechanical coupling of the inking unit is in mind of the modular principle pursued by the invention is not quite as ideal as the stronger one preferred self-drive for the roller or the rollers of the inking unit. After this likewise preferred embodiment of the invention, each inking unit has one own drive motor for his ink rollers.
  • Such a drive motor also drives preferably via a backlash-free toothed belt with high damping and if necessary via a reduction gear transmission, the inking roller or in the case several ink rollers on the plate cylinder of the corresponding cylinder group next lying ink roller.
  • the peripheral speed of this ink roller advantageously adjustable, especially with negative slip compared to Plate cylinder, the peripheral speed of the ink roller preferably something is less 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 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. she can, however, react on the motor shaft Influence acceleration torques.
  • the engine which in this case is an essential one This means that the mass is smaller than the coupling and the cylinder influenced.
  • the load torque is heavily frequency-dependent, which ultimately determines the dynamic behavior of the system.
  • a Setpoint changes are first tensioned to the springs that are closest to the motor are located.
  • 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 at this time, whose division is constantly changing.
  • the engine likes it within a short time have taken the correct position, but is due to the occurring mass forces distracted again, which leads to another control process.
  • the system must go through controlled, stabilized a relatively slow controller.
  • the present invention therefore also has the task of regulating to create, with the position and / or the speed of a rotary printing press a cylinder or a roller that is driven by a motor, performance-optimized and with sufficiently high control quality, d. H. in terms of dynamics and the speed or position accuracy can be controlled.
  • the scheme is supposed to be inexpensive and not too high demands on the coupling of motor and Place the load, in particular on the torsional rigidity and freedom from play of the coupling.
  • At least the drive motors are preferably on the same pressure side cylinder groups of a cylinder unit working in a paper web, position-controlled. So-called ideal position control is preferred, i.e. a delay free Position control with following error. On this, for technical reasons However, the desired, complex type of position control can also be dispensed with become. A simple position control is also a preferred, in particular cheaper, embodiment of the invention.
  • the drive motor can even in the dual-mass oscillator according to the invention be careful.
  • the load acting as a low pass filter is insensitive to the Vibrations of the much smaller motor.
  • they can Effects of the load on the drive motor are neglected.
  • the inventive, not least because of their simplicity cheap regulation offers the Another advantage that they are simply the wide range of Mass inertia between load and motor and on itself during operation changing parameters, such as the elasticity of a coupling, can be set can.
  • 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 engine is powered by the Load side guided by their actual value.
  • a particularly preferred Embodiment of the invention is not a mechanical actual value transmitter for the detection the position or the speed of the motor required for the regulation of the motor. Any actual value detection integrated in the motor can be advantageous for the pure one Drive monitoring, may be used for an engine emergency shutdown.
  • the actual value transmitter for the control is according to the invention on 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 a large motor had to drive a small load. For the present case, where a Drive motor drives a cylinder group or the rollers of an inking unit the driven load has a comparatively high mass moment of inertia compared to the drive motor, the use of asynchronous motors is not known. For the purposes of the regulation according to the invention instead of a load transmitter of a motor encoder, asynchronous motors are particularly suitable. Opposite to that for the have been used in the relevant applications DC motors Asynchronous motors have a higher field stiffness, so that their use is dynamic and Control quality of the system to be controlled improved. The use of others Motor types, for example DC motors, are not, however, fundamental locked out.
  • 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 in the case of the dual-mass oscillator in question be careful.
  • the load acting as a low pass filter is insensitive to the Vibrations of the much smaller motor. On the other hand, they can Effects of the load on the drive motor are neglected.
  • a paper web 1 to be printed becomes between the two opposing blanket cylinders 2 two Cylinder groups 10 passed.
  • the two cylinder groups 10 are each formed by the blanket cylinder 2 and an associated plate cylinder 3, the are mechanically coupled to each other for the common drive.
  • the mechanical Coupling is shown schematically by a line between the center points of the two cylinders 2 and 3 indicated. 1 in the embodiment each of the blanket cylinders 2 of each cylinder group 10 by a three-phase motor 5 driven.
  • the configuration according to FIG. 1, in each case only one Blanket cylinder 2 and a plate cylinder 3 by a mechanical coupling a cylinder group 10 are summarized, is characterized by its simple Construction 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 4 mechanically coupled for the blanket cylinder 2 with this blanket cylinder 2 is.
  • the cylinder group 10 is made up of the Blanket cylinder 2, its impression cylinder 4 and the plate cylinder 3 and their mechanical coupling together, so that the pressure point by a single Cylinder group 10 is formed.
  • FIG. 2 is in contrast 1 of the blanket cylinder 2, but of this cylinder assigned plate cylinder 3 driven by a three-phase motor 5.
  • the variant for combining cylinders into a cylinder group is hers constant delivery behavior due to 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 and the plate cylinders 3 can be interchanged in both exemplary embodiments.
  • 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 a drive free of playful transmission elements, such as gears, possible is.
  • 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 in this Embodiment combined into a cylinder group 10.
  • a separate three-phase motor 5 is provided for driving the Central cylinder 6, .
  • the central cylinder 6 with one of the four cylinder groups 10 a cylinder group form according to the variant shown in Fig. 2. This would make your own Motor 5 for the central cylinder 6 can be saved.
  • the in 3 shows a summary of the smallest possible cylinder groups 10 and self-propelled central cylinder 6 to a cylinder unit 20 the highest possible Flexibility in terms of configuration options.
  • one is formed from pairs of cylinders Cylinder group 10 in terms of their configurability, a concept with each individually driven cylinders equal.
  • the interaction is one of a pair of blankets / plate cylinders 2, 3 existing cylinder group 10 shown with an ink roller 7.
  • the Ink roller 7 via its own drive by a motor 5, which to the motor 5 for the cylinder group 10 may be identical, but need not be.
  • the engine 5 for the Ink roller 7 drives via a toothed belt 15 and a pair of gears 16, 17, which Gear 17 sits on the shaft of the ink roller 7, the ink roller 7.
  • the different moments of inertia of the motor 5 and the inking roller 7 through a suitable choice of gear ratios for the output via the toothed belt 15 and the gear pair 16, 17 disarmed.
  • the peripheral speed of the ink roller 7 is adjustable with a slightly negative Slip against the plate cylinder 3. This can counteract the danger be that the mechanical coupling formed by a pair of gears 12, 13 between the blanket cylinder 2 and the plate cylinder 3 from the meshing is lifted.
  • the cylinder group 10 is driven by the engine 5 via the toothed belt 11 on 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 gears 12 and 13.
  • This toothed belt 11 is the elastic coupling member between the motor 5 and the driven cylinder group 10.
  • Direct coupling or a gear coupling with the toothed belt 11 is a very high damping of the motor / load system 5, 10 achieved.
  • the engines 5 for the Cylinder group 10 and the inking roller 7 are each three-phase motors with a high Field rigidity.
  • the modular principle of forming cylinder groups also comes here or roller groups with toothed belt coupling to the drive motor to carry because fewer engine output sizes the entire variety of cylinder or Roll lengths and diameters with correspondingly different Mass moments of inertia can be equipped.
  • 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 be 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 mounted on the cylinder shaft 14 so as to be longitudinally displaceable.
  • the gear 12 and the gear for the toothed belt 11 firmly on the shaft 14 and are together with the blanket cylinder 2 and the motor 5 for the cylinder group 10 together longitudinally shifted.
  • 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 one Cylinder or a corresponding roller or cylinder system, the Mass moment of inertia typically more than five times that of motor 5 is. Nevertheless, the control of this motor / load system should be optimized for performance and with sufficiently high control quality for the speed or the angular position and the speed of the Load 25 are regulated. There should be no connection to the coupling 24 of the motor and the load high demands are made with regard to their torsional rigidity and Freedom of play.
  • This system runs from the load to the motor in large mass inertia conditions quickly to its dynamic limits. If the control becomes unstable, it vibrates above all 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 at the free shaft end the load, in the embodiment at the free shaft end of the blanket cylinder 2 one Cylinder group 10 attached.
  • This actual value transmitter 21 is therefore in the following Called loader.
  • the coupling 24 is through the toothed belt already described 11 with high elasticity compared to a direct coupling or a gear coupling but also high damping. In addition, this coupling 24 with one Timing belt without play.
  • the actual value required for the control generated by the load transmitter 21, which is the angular position the blanket cylinder 2 or its speed and its angular position, is returned to the controller 23.
  • a computer generated setpoint from that Setpoint generator 22 is compared with this actual value and to form a control signal used for the engine 5.
  • 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 those in the Control system creates shocks and vibrations, which are therefore only reduced Dimensions are returned in the controller 23 and therefore not too undesirable Can lead suggestions of the scheme.
  • This is the dynamic and also the Control quality compared to conventional systems even with otherwise the same Coupling significantly increased.
  • the system consisting of controller, motor, clutch and Cylinder is already much more damped. Exaggerated resonance occurs therefore not to the same extent. The controller can therefore be set more quickly without leaving the stable work area.
  • a possibly attached to the motor 5, in the exemplary embodiment according to FIG. 6 The actual value detection shown can be used for additional monitoring of the motor 5 Example can be used with a desired emergency shutdown option of the engine 5.
  • 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 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 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.
  • 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 pressure side thereof Paper web 1 arranged.
  • the two on the same print side of paper web 1 arranged cylinder groups 10 are mutually on the rubber cylinder 2 of the first Cylinder group 10 adjustable. This is indicated by two straight arrows W.
  • Each cylinder group 10 is again from an engine 5, as is already the case with the two cylinder groups 10 of FIG. 1 has been individually driven.
  • This arrangement enables the on-the-fly change of production at continuous Continuous paper web 1.
  • One of the two swiveling rubber cylinders 2 is pivoted away while the other is in the pressure position to the opposite Rubber cylinder 2 of the first cylinder group 10 stands.
  • the production change takes place in known way by changing the plates of the pivoted Blanket cylinder 2 assigned plate cylinder 3rd
  • Figure 11 shows an alternative pressure point also with three cylinder groups 10. Das for the arrangement of FIG. 10, what has been said in principle also applies to the arrangement of FIG 11. While the three cylinder groups 10 of the arrangement of Figure 10 each Form legs of a "Y", the cylinder groups 10 of Figure 11 form an upside down standing "Y" or a "Lambda”. In the arrangement according to FIG. 11, the two are lower, horizontally opposite cylinder groups 10 in the Machine frame stored independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the assembly or cylinder unit 20.
  • Figures 10 and 11 show the high flexibility of the invention Formation of cylinder groups and the regulation of each according to the invention Cylinder group. The most varied can be done in a particularly simple manner Form pressure points by, for example, cylinder units 20 with cylinder groups 10 (Fig. 10 and 11) or a plurality of cylinder units 20 are arranged 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)
EP01116647A 1993-12-29 1994-12-27 Machine rotative d'impression Expired - Lifetime EP1155826B1 (fr)

Applications Claiming Priority (8)

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
EP94810752A 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
EP99106201A EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP94810752.9 Division 1994-12-27
EP99106201A Division EP0930160B1 (fr) 1993-12-29 1994-12-27 Machine d'impression rotative
EP99106201.9 Division 1999-04-09

Publications (3)

Publication Number Publication Date
EP1155826A2 true EP1155826A2 (fr) 2001-11-21
EP1155826A3 EP1155826A3 (fr) 2002-06-26
EP1155826B1 EP1155826B1 (fr) 2011-09-14

Family

ID=27205938

Family Applications (4)

Application Number Title Priority Date Filing Date
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

Family Applications Before (1)

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

Family Applications After (2)

Application Number Title Priority Date Filing Date
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

Country Status (8)

Country Link
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)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP2153992A1 (fr) * 2008-08-13 2010-02-17 Komori Corporation Procédé et dispositif pour commander une imprimante
EP2177358A1 (fr) * 2008-10-15 2010-04-21 Komori Corporation Procédé et dispositif pour comander une machine

Families Citing this family (62)

* Cited by examiner, † Cited by third party
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DE20221927U1 (de) 1991-01-23 2009-04-23 Koenig & Bauer Aktiengesellschaft Rollenrotationsdruckmaschine
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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
EP0644048A2 (fr) 1995-03-22
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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