EP1155826B1 - Rotationsdruckmaschine - Google Patents

Rotationsdruckmaschine Download PDF

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Publication number
EP1155826B1
EP1155826B1 EP01116647A EP01116647A EP1155826B1 EP 1155826 B1 EP1155826 B1 EP 1155826B1 EP 01116647 A EP01116647 A EP 01116647A EP 01116647 A EP01116647 A EP 01116647A EP 1155826 B1 EP1155826 B1 EP 1155826B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
printing machine
rotary printing
drive 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.)
Expired - Lifetime
Application number
EP01116647A
Other languages
German (de)
English (en)
French (fr)
Other versions
EP1155826A3 (de
EP1155826A2 (de
Inventor
Felix Schneider
Dieter Koch
Andres 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
Publication of EP1155826A2 publication Critical patent/EP1155826A2/de
Publication of EP1155826A3 publication Critical patent/EP1155826A3/de
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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 to individual cylinder groups and a drive control for this purpose.
  • a Regelelleitsystem for such a printing machine with each individually driven cylinders known.
  • the individual drives of the cylinders and their drive controller can be summarized to groups of pressure groups arbitrarily.
  • the groups of printing groups are assigned to folders from which they obtain their position reference.
  • the proposed control system consists of a fast BUS system for the individual drives and the drive controllers of a print group and a higher-level control system for managing print group groups.
  • One from the JP-A 63-236651 known printing machine has printing units that are driven individually by their own drive motors.
  • the printing units comprise paired mechanically for their common drive coupled blanket cylinder and plate cylinder.
  • the motors each drive on the plate cylinders of the printing units. From the plate cylinders is driven on gearwheel couplings on the blanket cylinder.
  • the engines sit directly on the shafts of the plate cylinder.
  • Engine controls are supplied with machine control signals as command signals and engine speed and motor speed signals as actual signals.
  • the regulation of the motors takes place as a function of a comparison between the desired value signals and the actual value signals, ie on the basis of the difference between the desired value signals and the motor-side actual value signals.
  • the present invention has set itself the task of creating a highly flexible, yet economical rotary printing press.
  • blanket cylinder and plate cylinder of a rotary printing machine in pairs a cylinder group, in each of which a blanket cylinder and a plate cylinder are mechanically coupled together and are driven together by a separate drive motor per cylinder group.
  • the printing couples are understood to mean the pairs of cylinders between which a paper web to be printed passes and is printed on one side or on both sides.
  • each include a cylinder group and a corresponding impression cylinder, which may belong to the cylinder group, but need not.
  • a pressure point is formed by two cylinder groups assigned to one another.
  • the pressure points of the printing press in both cases are mechanically independent, ie the printing areas of the printing press are electrically coupled to one another.
  • a non-inventive cylinder groups of the blanket cylinder is driven, which in turn aborts the mechanical coupling on the plate cylinder of the same cylinder group.
  • the drive drives the plate cylinder shaft, so that the blanket cylinder is driven only by the mechanical coupling of the plate cylinder.
  • the blanket cylinder is decisive for the positional accuracy or circumferential register setting.
  • the non-inventive first solution has the advantage that the cylinder, which ultimately comes into direct contact with a paper web to be printed, does not have to be driven only on a possibly affected with game transfer element.
  • a cylinder group is on the one pressure side, and two cylinder groups are arranged on the opposite pressure side of a paper web passing therebetween.
  • the blanket cylinder of the group of cylinders arranged on one side of the paper web forms the impression cylinder for the other two blanket cylinders of the cylinder groups arranged on the opposite side of the paper web, which can advantageously be operated alternately.
  • This configuration offers the highest flexibility of use for a rubber / rubber production, as with continuous production the two interchangeable rubber cylinders can be configured to change the pressure. This is done by plate replacement of a non-employed rubber cylinder associated plate cylinder.
  • Each cylinder group can be stored in a single frame.
  • the two groups of cylinders lying horizontally opposite a printing side of the paper web are preferably combined to form a cylinder unit mounted in a frame.
  • a cylinder group can be extended according to the invention by an impression cylinder for the blanket cylinder.
  • This third cylinder of the cylinder group thus formed may be mechanically coupled to the blanket cylinder, preferably by a further gear coupling.
  • Such a cylinder group already represents a pressure point, between the blanket and impression cylinders, the paper web to be printed is passed.
  • the impression cylinder can be a steel or even another blanket cylinder for double-sided printing.
  • Such an impression cylinder may 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 summary provides the highest versatility for a cylinder unit.
  • each of the central cylinder associated cylinder groups of blanket and plate cylinder individually and independently of the other cylinder groups are reversed, as is required for example for alternating pressure or for the flying plate change.
  • the output of 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 invention also allows the direct drive, which may even be advantageous for small cylinders.
  • a toothed belt has the advantage of a backlash-free run and a not absolutely fixed gear ratio.
  • gears are preferably provided for the mechanical coupling between the cylinders within a cylinder group, although other transmission elements are quite conceivable.
  • the meshing gears may be straight or helical teeth.
  • the inking roller or the inking rollers or dampening rollers of an inking unit or of a inking and dampening unit which is assigned to a cylinder group, can be mechanically coupled to this cylinder group, so that the inking roller or the inking rollers are driven by the drive motor of this cylinder group become.
  • 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-propelled 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 drives preferably via a backlash-free timing belt with high damping and optionally via a reduction gear transmission, the ink roller or in the case of multiple ink rollers the plate cylinder of the corresponding cylinder group closest to the ink roller.
  • the peripheral speed of this ink roller is advantageously adjustable, in particular with negative slip relative to the plate cylinder, wherein the peripheral speed of the ink roller is preferably slightly less than that of the corresponding plate cylinder.
  • Control of the position or speed of a cylinder is known in the printing machine industry, in which a mechanical encoder on the motor side for detecting the engine speed or the rotor angular position of the motor is used for a target / actual comparison of the engine control.
  • this known control increasingly encounters its dynamic limits. If the actual position on the motor shaft is measured, both the coupling and the mechanical load are outside the actual control loop. she However, these can be influenced by the acceleration moments acting on the motor shaft.
  • the engine which in this case has a much smaller mass than the coupling and the cylinder, is thereby significantly influenced.
  • the load torque is highly frequency-dependent, which ultimately determines the dynamic behavior of the system.
  • the springs closest to the engine are first tensioned.
  • the engine torque caused by the controller accelerates parts of the coupling and subsequently the cylinder or the driven roller.
  • Energy is stored at this time both in the springs and in the mass movement whose division is constantly changing.
  • the motor may have taken the correct position within a short time, but is distracted again by the mass forces that occur, resulting in a further control process.
  • the system must be stabilized by a relatively slow regulator.
  • the present invention has therefore also set itself the task of creating a scheme with which the position and / or the rotational speed of a cylinder or a roller, which is driven by a motor, performance optimized and with sufficiently high control quality, d. H. Regarding the dynamics and the speed or position accuracy, can be controlled.
  • the scheme should be inexpensive and not too high demands on the coupling of motor and load, in particular to the torsional stiffness and backlash of the coupling.
  • At least the drive motors of the cylinder groups of a cylinder unit operating on the same pressure side of a paper web are position-controlled.
  • Preferred is a so-called ideal position control, ie a delay-free position control with a following error.
  • ideal position control ie a delay-free position control with a following error.
  • complex type of position control can certainly be dispensed with.
  • a simple position control is likewise a preferred, in particular less expensive, embodiment of the invention.
  • control cascades and active filters are known for so-called dual mass oscillator, but all require a large technical control effort.
  • load / motor systems described above i. H. the self-propelled cylinder groups
  • This actual value - angular position and / or rotational speed of the relevant cylinder - is enough to achieve high dynamics and control quality even alone.
  • 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 much smaller engine on the other hand.
  • the effects of the load on the drive motor can be neglected.
  • the inventive, not least because of its simplicity inexpensive control offers the further advantage that it is simply the wide range of inertia of load and motor and on in the course of operation changing parameters, such as the elasticity of a coupling, can be adjusted.
  • the load By the actual value to be controlled according to the invention is taken off the load, what is measured, what exactly has to run, namely the load, not the motor, is also measured.
  • the existing of the drive motor, a coupling and the load mechanical replacement system is to be regarded as a low-pass filter.
  • the low-pass filter of the motor-coupling-load-distance system is used to filter shocks and vibrations that occur in the controlled system. Such shocks and vibrations are thus returned to a reduced extent in the controller. The danger of a Aufschaukelung is thereby reduced.
  • the dynamics of the control and thus the control quality can be significantly increased compared to the described conventional control with identical coupling.
  • the figuratively speaking from the motor side to the load side migrated actual value encoder forms the main control variable for the controller of the engine, d. H. the motor is guided from the load side by its actual value.
  • no mechanical actual value encoder for detecting the position or the rotational speed of the engine is required in the context of the control of the engine.
  • An optionally integrated in the engine actual value detection can be used advantageously for the pure drive monitoring, possibly for a motor emergency shutdown.
  • the actual value encoder for the control is mounted according to the invention on 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 as the drive motors. So far, 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 the rollers of an inking unit, in which therefore the driven load a comparatively high mass moment of inertia has the drive motor
  • the use of induction motors is not known.
  • asynchronous motors are particularly suitable.
  • Asynchronous motors have a higher field stiffness than the DC motors previously used for the applications in question, so that their use improves the dynamics and control quality of the system to be controlled.
  • the use of other engine types, such as DC motors is not excluded in principle.
  • the stability of the control is further improved by the preferred use of a backlash-free toothed belt with high damping as coupling between the engine and the load.
  • the drive motor can even be left out of consideration in the two-mass oscillator in question.
  • the load acting as a low-pass filter is insensitive to the vibrations of the much smaller engine on the other hand. On the other hand, the effects of the load on the drive motor can be neglected.
  • the two cylinder groups 10 are each formed by the blanket cylinder 2 and an associated plate cylinder 3, which are mechanically coupled together 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 cylinder 2 of each cylinder group 10 are driven by a three-phase motor 5.
  • the configuration according to the Fig. 1 in which only one blanket cylinder 2 and one plate cylinder 3 are combined by a mechanical coupling to a cylinder group 10, characterized by their simple design and the highest degree of freedom in configuration in the formation of pressure points or groups of pressure points.
  • Fig. 2 shows a variant for forming a pressure point, in which a counter-pressure cylinder 4 is mechanically coupled for the blanket cylinder 2 with this blanket cylinder 2.
  • the cylinder group 10 is composed of the blanket cylinder 2, the impression cylinder 4 and the plate cylinder 3 and the mechanical coupling together, so that the pressure point is formed by a single cylinder group 10.
  • the embodiment of Fig. 2 is unlike the the Fig. 1 not the blanket cylinder 2, but the cylinder associated with this plate cylinder 3 driven by a three-phase motor 5.
  • the impression cylinder 4 may 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 reversed in both embodiments.
  • the drive of the plate cylinder 3 has the advantage that the cylinder group 10 can be easily reversed, while in the other case the unclaimed drive of the blanket cylinder 2 of the paper web 1 directly printing cylinder is driven and thereby a drive free of play transfer elements, such as Gears, is possible.
  • a cylinder unit 20 is shown, consisting of a central steel cylinder 6 and four, this central cylinder 6 associated cylinder groups 10.
  • Each a blanket cylinder 2 and a plate cylinder 3 are summarized in this embodiment to a cylinder group 10.
  • a separate three-phase motor 5 is provided for the drive of the central cylinder 6, a separate three-phase motor 5 is provided.
  • the central cylinder 6 with one of the four cylinder groups 10, a cylinder group corresponding to the in Fig. 2 form variant shown.
  • the own engine 5 would be saved for the central cylinder 6.
  • a cylinder group 10 formed from cylinder pairs is equal in terms of configurability to a concept with individually driven cylinders.
  • Fig. 4 is the interaction of one of a blanket / plate cylinder pair 2, 3 existing cylinder group 10 is shown with a paint roller 7.
  • the Ink roller 7 via its own drive by a motor 5, which may be identical to the engine 5 for the cylinder group 10, but need not be.
  • the motor 5 for the ink roller 7 drives via a toothed belt 15 and a gear pair 16, 17, wherein the gear 17 is seated on the shaft of the ink roller 7, the ink roller 7 at.
  • the different mass moments of inertia of the motor 5 and the ink roller 7 are defused 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 slight negative slippage relative to the plate cylinder 3.
  • the risk can be counteracted that the formed by a pair of gears 12, 13 mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 is lifted from the meshing.
  • the drive of the cylinder group 10 is not erfindungsgemä ⁇ from the engine 5 via the timing belt 11 on the blanket cylinder 2.
  • the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3 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. Compared with a basically also suitable direct coupling or a gear coupling is achieved with the toothed belt 11 a very high damping of the motor / load system 5, 10.
  • the two gears 12 and 13, which form the mechanical coupling between the blanket cylinder 2 and the plate cylinder 3, may be helical or spur gears.
  • the blanket cylinder 2 is longitudinally displaced in the 9.registerver ein while the gear 12 and the corresponding gear for the toothed belt 11 remain stationary, i.
  • These two gears are mounted longitudinally displaceable on the cylinder shaft 14.
  • the gear 12 and the gear for the toothed belt 11 sit firmly on the shaft 14 and are moved together along with the blanket cylinder 2 and the motor 5 for the cylinder group 10 together.
  • the motor / load system 5, 10 is guided by an actual value which is generated by a mechanical load transmitter 21 mounted on the load side, namely on the torque-free end of the shaft 14 of the blanket cylinder 2.
  • the same type of control, namely with an attached to the load-free shaft end of the ink roller 7 loader 27 is selected for the control of the speed of this ink roller 7.
  • FIG. 5 A known in printing machine construction control is in Fig. 5 shown schematically.
  • the control of the motor 5, which drives a load 25 via an elastic coupling 24, is effected by means of a regulator 23.
  • the load 25 is a heavy roll or a heavy cylinder or a corresponding roll or cylinder system whose mass moment of inertia is typically more than five times as high as that of the engine 5 is. Nevertheless, the regulation of this motor / load system should be optimized in terms of performance and with sufficiently high control quality for the speed or the angular position and the speed of the load 25. It should not be too high demands on the coupling 24 of motor and load with respect to their torsional stiffness and backlash.
  • a mechanical feedback sensor 21 for generating a characteristic of the position or the rotational speed and the position of the rotor of the motor 5 electrical signal is attached to this rotor.
  • the load 25 is fixed to the motor shaft end with the coupling 24, which has an elasticity and possibly a certain play.
  • the coupling and the load are outside the actual control loop. However, you can influence this by means of the acceleration torques acting on the motor shaft.
  • This system quickly reaches its dynamic limits with high mass inertia ratios from load to motor. If the control system becomes unstable, the engine will vibrate while the load remains relatively quiet.
  • Fig. 6 shows, however, a scheme in which, as in Fig. 4 already shown, the reference variable for the control is generated by a transmitter 21, which is attached to the load 25 and not to the motor 5.
  • This actual value encoder 21 is attached to the free shaft end of the load, in the exemplary embodiment at the free end of the blanket cylinder 2 of a cylinder group 10.
  • This actual value encoder 21 is therefore referred to below as a loader.
  • the coupling 24 is formed by the already described toothed belt 11 with respect to a direct coupling or a gear coupling high elasticity but also high damping. In addition, this coupling 24 is free of play with a toothed belt.
  • the feedback required for the control generated by the loader 21 actual value, which represents the angular position of the blanket cylinder 2 or its speed and its angular position, 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 are within the actual control loop.
  • the load and the coupling 24 form a low-pass filter for in the
  • Control system resulting shocks and vibrations which are thus attributed only to a reduced extent in the controller 23 and therefore can not lead to unwanted suggestions of the scheme.
  • the dynamics and the quality of control compared to conventional systems are significantly increased even with otherwise the same coupling.
  • the system, consisting of governor, engine, clutch and cylinder, is already substantially more damped. Resonance peaks therefore do not occur to the same extent.
  • the controller can therefore be set faster without leaving the stable working area.
  • An optionally attached to the engine 5, according to the embodiment Fig. 6 illustrated actual value detection can be used for additional monitoring of the engine 5, for example, in a desired emergency shutdown of the engine 5.
  • FIGS. 7 and 8 is the dynamic behavior of the two regulations according to the FIGS. 5 and 6 compared.
  • the reciprocal value of the reset time T i of the drive is selected.
  • the dynamics is shown as a function of the mass inertia ratio of load to motor with identical coupling and identical phase reserve. This shows clearly that the scheme after Fig. 6 with the actual value detection on the load, especially with larger mass inertia ratios of the actual value detection on the motor according to FIG. 5 is clearly superior.
  • Fig. 8 is the dynamics as a function of the torsional stiffness of the coupling 24 at a constant mass inertia ratio and identical phase reserve shown. This shows the regulation Fig. 6 especially at low torsional stiffness of the coupling compared to the conventional control accordingly Fig. 5 think.
  • the control diagram of the controller 23 shows the setpoint and the actual value, in the exemplary embodiment the desired or actual center position of a blanket cylinder 2, are fed to a first differential amplifier 31 to form the difference setpoint actual value.
  • the difference D 1 formed there is a first proportional amplifier 34 supplied and given as a proportional amplified signal K 1 XD 1 to a second differential amplifier 35.
  • the setpoint value and the actual value are each supplied to a differentiator 32 or 33, differentiated and the corresponding output signals S s and S i are fed to the second differential amplifier 35.
  • the sum k 1 D 1 + S s -S i formed there is amplified in a second proportional amplifier 36 and fed via an integrator 37 to a current regulator for the motor 5.
  • FIG. 10 shows a pressure point, which is formed by three cylinder groups 10.
  • a first cylinder group 10 is on the one pressure side of the paper web 1, and a second and a third cylinder group 10 are arranged on the opposite pressure side of this paper web 1.
  • the two cylinder groups 10 arranged on the same pressure side of the paper web 1 can be set alternately against the blanket cylinder 2 of the first cylinder group 10. This is indicated by two straight arrows W.
  • the two upper cylinder groups 10 which are approximately horizontally opposed to form a cylinder unit 20 and stored as such in the machine frame independently of the lower cylinder group 10.
  • Each cylinder group 10 is again from a motor 5, as already in the two cylinder groups 10 of FIG. 1 the case has been driven individually.
  • This arrangement allows the flying change of production with continuous continuous paper web 1.
  • Each one of the two swing-off blanket cylinder 2 is pivoted, while the other is in printing position to the opposite blanket cylinder 2 of the first cylinder group 10.
  • the production change takes place in a known manner by changing the plates of the pivoted blanket cylinder 2 associated plate cylinder. 3
  • FIG. 11 shows an alternative pressure point also with three groups of cylinders 10.
  • the arrangement of FIG. 10 The above applies in principle to the arrangement of FIG. 11 , While the three cylinder groups 10 of the arrangement after FIG. 10 each form the legs of a "Y” form the cylinder groups 10 of FIG. 11 an upside down “Y” or a “lambda".
  • the two lower, horizontally opposed cylinder groups 10 are stored in the machine frame independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the construction or cylinder unit 20.
  • Figures 10 and 11 show the high flexibility of the inventive formation of cylinder groups and the inventive control of each cylinder group. It can be formed in a particularly simple manner a wide variety of pressure points by, for example, cylinder units 20 with cylinder groups 10 ( Fig. 10 and 11 ) or several cylinder units 20 are arranged one above the other ( Fig. 1 ). Basically, the cylinders of the arrangements according to the Figures 10 and 11 also in a different way than after the FIGS. 1 to 4 be coupled, for example via a single transmission.

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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)
  • Printing Plates And Materials Therefor (AREA)
  • Impact Printers (AREA)
  • Soil Working Implements (AREA)
  • Glass Compositions (AREA)
  • Holding Or Fastening Of Disk On Rotational Shaft (AREA)
  • Lubrication Of Internal Combustion Engines (AREA)
  • Switches With Compound Operations (AREA)
  • Soft Magnetic Materials (AREA)
  • Fixed Capacitors And Capacitor Manufacturing Machines (AREA)
  • Auxiliary Devices For And Details Of Packaging Control (AREA)
EP01116647A 1993-12-29 1994-12-27 Rotationsdruckmaschine Expired - Lifetime EP1155826B1 (de)

Applications Claiming Priority (8)

Application Number Priority Date Filing Date Title
DE4344896 1993-12-29
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
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
EP99106201A EP0930160B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine

Related Parent Applications (3)

Application Number Title Priority Date Filing Date
EP99106201A Division EP0930160B1 (de) 1993-12-29 1994-12-27 Rotationsdruckmaschine
EP94810752.9 Division 1994-12-27
EP99106201.9 Division 1999-04-09

Publications (3)

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

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ID=27205938

Family Applications (4)

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

Family Applications After (3)

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

Country Status (8)

Country Link
EP (4) EP1155826B1 (zh)
JP (2) JP3424999B2 (zh)
CN (1) CN1061301C (zh)
AT (4) ATE181879T1 (zh)
DE (3) DE59409732D1 (zh)
DK (3) DK0930160T3 (zh)
ES (3) ES2135557T5 (zh)
RU (1) RU2127668C1 (zh)

Families Citing this family (61)

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Publication number Priority date Publication date Assignee Title
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EP1155826A3 (de) 2002-06-26
JP3415469B2 (ja) 2003-06-09
DK0644048T3 (da) 2000-01-31
DE59408463D1 (de) 1999-08-12
ES2135557T3 (es) 1999-11-01
EP0644048A3 (de) 1995-06-28
ATE524311T1 (de) 2011-09-15
EP0644048B1 (de) 1999-07-07
DE59410108D1 (de) 2002-05-23
ES2175867T3 (es) 2002-11-16
EP0930160A1 (de) 1999-07-21
JP3424999B2 (ja) 2003-07-07
EP0644048A2 (de) 1995-03-22
JPH0834108A (ja) 1996-02-06
ATE181879T1 (de) 1999-07-15
DE59409732D1 (de) 2001-05-17
ES2157676T3 (es) 2001-08-16
JPH11268249A (ja) 1999-10-05
ES2135557T5 (es) 2005-09-01
DK0930159T3 (da) 2001-08-13
CN1061301C (zh) 2001-01-31
CN1122279A (zh) 1996-05-15
RU2127668C1 (ru) 1999-03-20
EP0644048B2 (de) 2005-03-23
RU94045261A (ru) 1996-12-10
ATE216317T1 (de) 2002-05-15
EP0930160B1 (de) 2002-04-17
DK0930160T3 (da) 2002-07-29
ATE200449T1 (de) 2001-04-15
EP0930159B1 (de) 2001-04-11
EP1155826A2 (de) 2001-11-21
DK0644048T4 (da) 2005-05-02

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