EP0930159B1 - Machine rotative d'impression - Google Patents

Machine rotative d'impression Download PDF

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Publication number
EP0930159B1
EP0930159B1 EP99106200A EP99106200A EP0930159B1 EP 0930159 B1 EP0930159 B1 EP 0930159B1 EP 99106200 A EP99106200 A EP 99106200A EP 99106200 A EP99106200 A EP 99106200A EP 0930159 B1 EP0930159 B1 EP 0930159B1
Authority
EP
European Patent Office
Prior art keywords
cylinder
printing press
drive motor
rotary printing
cylinders
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
EP99106200A
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German (de)
English (en)
Other versions
EP0930159A1 (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.)
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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 EP0930159A1 publication Critical patent/EP0930159A1/fr
Application granted granted Critical
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Classifications

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

Definitions

  • the present invention relates to the combination of cylinders Rotary printing press for individual cylinder groups including one Drive control for this.
  • 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. Controllers of the motors - will 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 Tension springs that are closest to the engine. That through the controller engine torque accelerates parts of the coupling and subsequently the cylinder or the driven roller. Energy is both at this time stored in the springs as well as in the mass movement, the division of which is constantly changing.
  • the motor likes the correct position within a short time have taken, but is again due to the occurring mass forces distracted, which leads to another control process.
  • the system must, through a relatively slow controller can be controlled, stabilized.
  • the present invention has set itself the task of driving a To create cylinder or a roller of a rotary printing press with which the Cylinder or roller optimized for performance and with high control quality, i.e. Regarding the dynamics and the position and / or speed accuracy, regulated is driven.
  • the regulation should be inexpensive and not too demanding to the coupling of motor and load.
  • 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.
  • each of a pressure point formed according to the invention includes one Cylinder group and a corresponding impression cylinder that goes to the cylinder group can belong, but does not have to. In the latter case, a pressure point is passed through two mutually associated cylinder groups are formed.
  • Drive technology are, however the printing points of the printing press are mechanically independent in both cases, d. H. the printing points of the printing press are electrically coupled to one another.
  • 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 takes place according to the invention 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 oscillator according to the invention be disregarded.
  • the load acting as a low-pass filter is insensitive against the vibrations of the much smaller motor.
  • the effects of the load on the drive motor can be neglected become.
  • the inventive, not least because of its simplicity inexpensive 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 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 transmitter for the control is torque-free Shaft end of the driven cylinder of a cylinder group or the driven roller of an inking unit attached.
  • At least the drive motors are preferably the same Printing side of a paper web working cylinder groups of a cylinder unit position controlled. 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 output from a drive motor takes place on the respective cylinder group preferably by means of a toothed belt.
  • a timing belt has a high elasticity.
  • a group of cylinders is driven by the use of a toothed belt given possibility of high damping of a drive motor and the existing mechanical system of large cylinders Value, as will be explained later.
  • the invention also allows Direct drive, which can even be advantageous for small cylinders.
  • 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.
  • 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 the invention 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.
  • the effects of the load on the drive motor can be neglected become.
  • the blanket cylinder is preferably used in the cylinder groups according to the invention 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 is on one pressure side, and two cylinder groups are on the opposite pressure side of a continuous between Paper web arranged.
  • the rubber cylinder forms the one Printing side of the paper web arranged cylinder group the impression cylinder for the other two rubber cylinders on the opposite pressure side of the Paper web arranged cylinder groups, both advantageously each can be operated alternately.
  • This configuration offers the highest Flexibility of use for a rubber / rubber production because of continuous production the two mutually usable rubber cylinders for converting the Pressure can be configured. This is done by changing the plate plate cylinder not assigned to the rubber cylinder. Every cylinder group can be stored in a single frame.
  • the two are one Printing side of the paper web horizontally opposite cylinder groups to one summarized in a frame mounted cylinder unit.
  • 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 through another gear coupling.
  • Such a cylinder group represents already represents a pressure point between their blanket and impression cylinders the paper web to be printed is passed through.
  • the impression cylinder can a steel or another blanket cylinder for double-sided printing.
  • Such an impression cylinder can in particular also be a central cylinder Be cylinder unit with, for example, nine or ten cylinders.
  • also preferred embodiment of the invention is such a Central cylinder powered by its own drive motor. That kind of Summary provides the greatest versatility for a cylinder unit.
  • each of the cylinder groups assigned to the central cylinder can made of blanket and plate cylinders individually and independently of the others Cylinder groups can be reversed, such as for alternating pressure or is required for the flying plate change.
  • 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.
  • a paper web to be printed 1 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, 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 4 for the blanket cylinder 2 with this blanket cylinder 2 mechanically is coupled.
  • the cylinder group 10 sits down from the blanket cylinder 2, its impression cylinder 4 and the plate cylinder 3 and their mechanical coupling together, so that the pressure point is formed by a single cylinder group 10.
  • 2 is not the blanket cylinder 2, but the plate cylinder 3 assigned to this cylinder by a three-phase motor 5 driven.
  • a cylinder group is its constant delivery behavior because of the mechanical Coupling the blanket cylinder 2 with its impression cylinder 4 and that due to this mechanical coupling, there is no direct interference between the Cylinder 2 and 4 takes place.
  • the impression cylinder 4 can be a second blanket cylinder or a steel cylinder, for example a central cylinder Be 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 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 the own motor 5 for the central cylinder 6 can be saved.
  • a 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.
  • 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 moved longitudinally together.
  • 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 peaks 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 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 the one printing side of the paper web 1, and one second and third cylinder groups 10 are on the opposite pressure side this paper web 1 arranged.
  • the two on the same printing side of the paper web 1 arranged cylinder groups 10 are mutually attached to the rubber cylinder 2 of the first cylinder group 10 adjustable. This is indicated by two straight arrows W.
  • the two upper cylinder groups 10 are approximately horizontal opposite to form a cylinder unit 20 and as such in the Machine frame stored independently of the lower cylinder group 10.
  • Each Cylinder group 10 is again driven by an engine 5, as is the case with the two Cylinder groups 10 of Figure 1 has been driven individually.
  • 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 printing position to the opposite Rubber cylinder 2 of the first cylinder group 10 stands.
  • the change of production takes place in a known manner by changing the plates of the pivoted Blanket cylinder 2 assigned plate cylinder 3rd
  • FIG. 11 shows an alternative pressure point also with three cylinder groups 10. What has been said regarding the arrangement of FIG Figure 11. While the three cylinder groups 10 of the arrangement of Figure 10 each form the legs of a "Y”, form the cylinder groups 10 of FIG. 11 an upside down “Y” or a "Lambda”. In the arrangement according to the figure 11 are the two lower, horizontally opposite cylinder groups 10 stored in the machine frame independently of the upper cylinder group 10. These two lower cylinder groups 10 thereby form the assembly or cylinder unit 20th
  • Figures 10 and 11 show the high flexibility of the invention Formation of cylinder groups and the control according to the invention each cylinder group. The most varied can be done in a particularly simple manner Form pressure points, for example by cylinder units 20 with cylinder groups 10 (FIGS. 10 and 11) or a plurality of cylinder units 20 arranged one above the other be (Fig. 1). Basically, the cylinders of the arrangements according to the Figures 10 and 11 also coupled in a different way than that of Figures 1 to 4 be, for example, via a single gear.

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  • Mechanical Engineering (AREA)
  • Engineering & Computer Science (AREA)
  • Rotary Presses (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Screen Printers (AREA)
  • Glass Compositions (AREA)
  • Impact Printers (AREA)
  • Soil Working Implements (AREA)
  • Printing Plates And Materials Therefor (AREA)
  • Treatment Of Fiber Materials (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)

Claims (13)

  1. Machine d'impression rotative
    a) comportant des cylindres (2) porte-blanchet qui forment avec des cylindres (2 ; 4) de contrepression ou un cylindre (6) de contrepression commun des points d'impression,
    b) comportant des cylindres (3) porte-cliché qui sont réunis au cylindre (2) porte-blanchet chaque fois par couple par accouplement mécanique de leur entraínement pour former des groupes (10) de cylindres,
    c) les groupes (10) de cylindres étant entraíné chacun par un moteur (5) d'entraínement propre,
    d) comportant un indicateur (21) de valeur réelle pour produire une valeur réelle de position angulaire de rotation et/ou de vitesse de rotation et un indicateur (22) de valeur de consigne pour émettre une valeur de consigne de position angulaire de rotation et/ou de vitesse de rotation pour chaque fois l'un des groupes (10) de cylindres et,
    e) comportant un régulateur (23) auquel la valeur de consigne de l'indicateur (22) de valeur de consigne et de valeur réelle de l'indicateur (21) de valeur réelle est fourni et qui régule le moteur (5) d'entraínement de ce groupe (10) de cylindres en fonction d'une comparaison de la valeur de consigne et de la valeur réelle,
       caractérisée en ce que
    f) l'indicateur (21) de valeur réelle est monté sur l'extrémité d'arbre exempte de couple du cylindre (2, 3) du groupe (10) de cylindres, qui est entraíné par le moteur (5) d'entraínement régulé au moyen du régulateur (23).
  2. Machine d'impression rotative suivant la revendication 1, caractérisée en ce qu'un groupe (10) de cylindres a un moment d'inertie de masse qui est plus grand que le moment d'inertie de masse du moteur (5) d'entraínement de ce groupe (10) de cylindres et en ce qu'une courroie (11) dentée forme l'accouplement entre le moteur (5) d'entraínement et le groupe (10) de cylindres et, avec le groupe de cylindres, un filtre passe-bas.
  3. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce que, dans un groupe (10) de cylindres, le cylindre (2) porte-blanchet est entraíné au moyen d'une courroie (11) dentée par le moteur (5) d'entraínement du groupe (10) de cylindres et est sorti par le cylindre (2) porte-blanchet sur le cylindre (3) porte-cliché du groupe (10) de cylindres.
  4. Machine d'impression rotative suivant la revendication 1 ou 2, caractérisée en ce que, dans un groupe (10) de cylindres, le cylindre (2) porte-cliché est entraíné au moyen d'une courroie (11) dentée par le moteur (5) d'entraínement du groupe (10) de cylindres et il y a une prise de mouvement du cylindre (3) porte-blanchet sur le cylindre (2) porte-cliché du groupe (10) de cylindres.
  5. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce que les moteurs (5) d'entraínement sont des moteurs électriques asynchrones.
  6. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce qu'une valeur réelle émise par l'indicateur (21) de valeur réelle forme la grandeur de réglage principale pour le régulateur (23).
  7. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce que, pour la régulation, il n'est pas prévu d'indicateur mécanique supplémentaire de valeur réelle, de préférence il n'est pas prévu d'indicateur mécanique de valeur réelle pour la détection de la position ou de la vitesse de rotation du moteur (5) d'entraínement.
  8. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce qu'un indicateur mécanique est prévu sur le moteur (5) d'entraínement, le signal de sortie de cet indicateur étant utilisé comme signal d'entrée pour une mise hors circuit d'urgence du moteur (5) d'entraínement.
  9. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce qu'au moins un rouleau (7) encreur d'un mécanisme d'encrage ou d'un mécanisme d'encrage et de mouillage qui est associé à un groupe (10) de cylindres est couplé mécaniquement à ce groupe (10) de cylindres ou en ce que, pour l'entraínement d'au moins l'un des rouleaux (7) d'encrage d'un mécanisme d'encrage de ce genre, il est prévu un moteur (5) d'entraínement propre qui entraíne le rouleau (7) d'encrage au moyen d'une courroie (15) dentée.
  10. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce que le cylindre de contrepression commun est un cylindre (6) central d'une unité (20) de cylindres à plusieurs groupes (10) de cylindres, qui est muni d'un moteur (5) d'entraínement propre ou qui est couplé pour l'entraínement mécaniquement au cylindre (2) porte-blanchet d'un groupe (10) de cylindres de l'unité (20) centrale.
  11. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce qu'une unité (20) de cylindres à plusieurs groupes (10) de cylindres comporte deux cylindres (6) centraux qui sont munis chacun d'un moteur (5) d'entraínement propre.
  12. Machine d'impression rotative suivant l'une des revendications précédentes, caractérisée en ce que trois groupes (10) de cylindres forment un point d'impression et en ce que l'un des trois groupes (10) de cylindre est monté sur l'une des côtés d'impression et les deux autres groupes (10) de cylindres sur le côté d'impression opposé d'une bande (1) de papier.
  13. Machine d'impression rotative suivant la revendication précédente, caractérisée en ce que deux groupes de cylindres qui se font faces horizontalement des trois groupes (10) de cylindre sont réunis en une unité (21) de cylindres et montés en tant que tels dans un bâti de machine indépendamment du troisième groupe (10) de cylindres.
EP99106200A 1993-12-29 1994-12-27 Machine rotative d'impression Expired - Lifetime EP0930159B1 (fr)

Applications Claiming Priority (7)

Application Number Priority Date Filing Date Title
DE4344912 1993-12-29
DE19934344912 DE4344912C5 (de) 1993-12-29 1993-12-29 Antrieb eines farbübertragenden Druckzylinders einer Rollenrotationsdruckmaschine
DE4344896 1993-12-29
DE19934344896 DE4344896C5 (de) 1993-12-29 1993-12-29 Antrieb für Zylinder 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

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
EP94810752A Division 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

Publications (2)

Publication Number Publication Date
EP0930159A1 EP0930159A1 (fr) 1999-07-21
EP0930159B1 true EP0930159B1 (fr) 2001-04-11

Family

ID=27205938

Family Applications (4)

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

Family Applications Before (3)

Application Number Title Priority Date Filing Date
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
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

Country Status (8)

Country Link
EP (4) EP0644048B2 (fr)
JP (2) JP3424999B2 (fr)
CN (1) CN1061301C (fr)
AT (4) ATE524311T1 (fr)
DE (3) DE59410108D1 (fr)
DK (3) DK0930160T3 (fr)
ES (3) ES2135557T5 (fr)
RU (1) RU2127668C1 (fr)

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Also Published As

Publication number Publication date
ATE216317T1 (de) 2002-05-15
ES2157676T3 (es) 2001-08-16
RU94045261A (ru) 1996-12-10
ATE200449T1 (de) 2001-04-15
ES2175867T3 (es) 2002-11-16
EP1155826A2 (fr) 2001-11-21
RU2127668C1 (ru) 1999-03-20
JPH11268249A (ja) 1999-10-05
EP0644048A3 (fr) 1995-06-28
DK0930160T3 (da) 2002-07-29
CN1122279A (zh) 1996-05-15
EP0930159A1 (fr) 1999-07-21
EP1155826A3 (fr) 2002-06-26
DK0644048T4 (da) 2005-05-02
JPH0834108A (ja) 1996-02-06
ES2135557T3 (es) 1999-11-01
EP0930160A1 (fr) 1999-07-21
EP0644048B1 (fr) 1999-07-07
DK0644048T3 (da) 2000-01-31
EP0644048B2 (fr) 2005-03-23
ATE181879T1 (de) 1999-07-15
JP3424999B2 (ja) 2003-07-07
EP0930160B1 (fr) 2002-04-17
EP1155826B1 (fr) 2011-09-14
DK0930159T3 (da) 2001-08-13
ATE524311T1 (de) 2011-09-15
DE59408463D1 (de) 1999-08-12
JP3415469B2 (ja) 2003-06-09
CN1061301C (zh) 2001-01-31
ES2135557T5 (es) 2005-09-01
EP0644048A2 (fr) 1995-03-22
DE59410108D1 (de) 2002-05-23
DE59409732D1 (de) 2001-05-17

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