EP2072252B1 - Procédé et agencement de compensation d'asynchronismes d'angles de rotation en fonction du réglage - Google Patents

Procédé et agencement de compensation d'asynchronismes d'angles de rotation en fonction du réglage Download PDF

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Publication number
EP2072252B1
EP2072252B1 EP08172069.0A EP08172069A EP2072252B1 EP 2072252 B1 EP2072252 B1 EP 2072252B1 EP 08172069 A EP08172069 A EP 08172069A EP 2072252 B1 EP2072252 B1 EP 2072252B1
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EP
European Patent Office
Prior art keywords
cylinder
transmitter
rotary
support point
drive
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EP08172069.0A
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German (de)
English (en)
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EP2072252A2 (fr
EP2072252A3 (fr
Inventor
Martin Riese
Victor Hefftler
Bodo Zirnstein
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Koenig and Bauer AG
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Koenig and Bauer AG
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    • 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
    • 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
    • B41P2213/90—Register control

Definitions

  • the invention relates to a rotary printing machine for carrying out a method for compensating control-induced Drehwinkel- asynchronisms of two independently driven cylinder, which occur during the feed movement of the cylinder, according to the preamble of the first claim and a corresponding method for the compensation of control-induced rotational angle Asynchronticianen.
  • printing presses such as offset printing presses
  • individual cylinders are spun off from the continuous drive wheel train in order to shorten set-up times and are driven individually parallel to the main drive.
  • plate cylinders in offset printing units may have a separate drive motor (single drive), so that, for example, all plate cylinders can be simultaneously rotated to the plate change position in order to be able to perform the plate change on all printing units at the same time (eg DE 196 23 224 C1 ).
  • the angular positions of the individually and centrally driven cylinders eg plate and blanket cylinders
  • Synchronization is understood to mean the continuous assurance of the correct angular position assignment of the adjacent cylinders.
  • rotary encoders are arranged in the drive wheel train, which specify the rotation angle setpoints for the control of the individual drives.
  • the synchronous rotation of the respectively adjacent cylinders should ensure that the cylinder surfaces always slip on each other slip-free and no relative movements at the contact points of the cylinder surfaces come about, whereby either the print image transfer is impaired or tensile stresses are generated in the substrate.
  • Synchronization problems when pivoting in the contact area arise from the fact that only the rotation of the blanket cylinder during rolling of the tooth flanks during pivoting detected by the arranged on the rubber cylinder shaft rotary encoder and the rotational position of the plate cylinder can be tracked synchronously via the machine control.
  • the detection of the translational movement of the cylinder axis of rotation with a rotary encoder without additional measures is not possible so that the tangential displacement of the blanket cylinder surface relative to the plate cylinder surface is not recognized by the machine control and consequently not with an equivalent additional co-rotation of the individual drive on the adjacent plate cylinder is traced.
  • the plate cylinder is caused on the one hand by the frictional surface contact between the rubber and pressure plate or between the bearer rings to rotate.
  • a Drehwinkelkorrektur disturbance is known for a single-pivoting cylinder, which determines either by means of additional measuring means either the translational movement of the cylinder axis or the pivot angle and feeds a multi-stage controller, which determines therefrom the required correction angle for the single drive for the suppression of relative movements between the adjacent cylinder surfaces.
  • a disadvantage is the economic outlay for additional position sensors and control devices. Usually, this is achieved by the rotor of the encoder (hollow shaft encoder) is firmly mounted on the cylinder axis and the stator of the encoder (encoder housing) via a torque arm on the frame of the printing press is supported.
  • a disadvantage of these solutions is that in the pressure-on delivery movement due to the acceleration of the blanket cylinder during the pivoting movement and the delayed tracking of the compensation rotation of the plate cylinder, a following error occurs, so that the two cylinder surfaces not in the conventional (theoretically resulting) rotational angle position but to offset the following error. This deviation must be compensated in the cylinder and bearer contact, resulting in an undesirable and disturbing moments generating relative movement between the cylinder surfaces and bearer rings.
  • Another synchronization problem arises from the changing contact pressure of the cylinder combination blanket cylinder / impression cylinder.
  • the blanket cylinder forms with an adjacent impression cylinder on which the sheets are transported by the respective printing unit, the pressure zone, wherein the pressure changes as the passage of the cylinder passages through the pressure zone abruptly.
  • the invention is therefore based on the object to minimize the positional error when pivoting a second cylinder to a first cylinder, especially in the pressure-on circuit of a blanket cylinder to a plate cylinder in an offset printing unit, at the moment of contact of the cylinder.
  • the object is achieved by a rotary printing machine having the features of claim 1 or a method having the features of claim 7.
  • the invention has the advantage that pressure disturbances causing relative movements of the synchronized cylinders during pivoting in the contact area can be safely avoided.
  • Fig. 1 shows a schematic representation of a printout section of a sheet-fed offset rotary printing press in side view with a simple large plate cylinder 1.P, a pivoting single-sized blanket cylinder 2.G, which is mounted with its shaft 10 on both sides in eccentric bearings 4, and a double-sized impression cylinder 3.
  • the cylinder 1, 2 are stored in side frames of the printing press.
  • the plate cylinder 1.P is associated with a first drive, which may be, for example, a known single drive M, which is associated with the plate cylinder 1.P and of a (not shown) known drive controller with respect to. Rotational angular position, rotational speed and acceleration with the blanket cylinder. G is synchronized.
  • the blanket cylinder 2.G is driven in the embodiment via a central drive wheel train by a second drive, the main press machine drive. Between plate cylinder 1.P and rubber cylinder 2.G there is no positive mechanical drive connection.
  • the individually driven plate cylinder 1.P are associated with two bearer rings on both sides, which cooperate in a known manner with two other bearer rings on the shaft 10 of the blanket cylinder 2.G.
  • the bearer rings roll in pairs from each other frictionally. For reasons of simplification was in the Fig. 1 not differentiated between the Abicalz Vietnamese the bearer rings and the contact area of the cylinder surfaces.
  • a first rotary encoder 5 for detecting the absolute angular position is arranged centrally.
  • a second rotary encoder 6 is mounted centrally on the shaft 10 of the adjacent blanket cylinder 2.G whose rotor 6.R is rotatably connected to the shaft 10 and the stator 6.S (rotary encoder housing) rotatably mounted on the shaft 10 is.
  • the shaft 10 can be pivoted by rotation of the eccentric 4 between a "pressure-on” - position and a "pressure-off” - position.
  • a rigid Statorabstützung 7 is fixed and arranged in the radial direction, which ensures a rotational angle play free storage of the stator 6.S.
  • the Statorabstützung 7 is rotatably supported at its end facing away from the stator 6.S end to a frame-fixed stop, the Geberabstweiltician 8.1, 8.2 or 8.3, to transform the pivoting movement of the blanket cylinder 2.G in a rotational movement of the stator 6.S.
  • the stator support 7 is designed, for example, as a rod-shaped anti-twist device welded to the rotary encoder housing. At the free end, the StatorabstNeillung 7 abuts a stop contour, which is aligned so that the extended longitudinal axis of the Statorabstützung 7 points in the direction of the plate cylinder 1.P.
  • the Statorabstützung 7 is non-positively connected for play-free storage on the stop 8, for example via a tension spring 9 with the stopper 8. Since the pivoting movements of the blanket cylinder 2.G also cause a change in the distance to the stop 8, the Statorabstützung 7 is slidably mounted in its longitudinal direction on the stop 8. The Statorabst Reifenung 7 may also be connected in a rotary bearing with the stopper 8. However, this then requires a variable-length design of the stator support 7, which is for this purpose formed in two parts with parts overlapping in the longitudinal direction, which are movable in the longitudinal direction relative to each other.
  • the solution according to the invention now provides for supporting the rotary encoder housing not at the conventional encoder support point 8.0 but at a remote encoder support point 8.1, 8.2 or 8.3.
  • the proposed new Geberabstützit 8.1, 8.2 or 8.3 are located away from the conventional Geberabstweiltician 8.0, wherein the direction and the amount of the distance of the Geberabstweiln invention 8.1, 8.2, 8.3 from the conventional Geberabstütztician 8.0 of the Schwenkgetriebegeometrie or the pivoting curve of the axis of rotation of the blanket cylinder. 2 G and the following error to be compensated for the drive control.
  • the positions of the Geberabstütz relate 8.1, 8.2 or 8.3 relative to the conventional Geberabstweilticianen 8.0 and the positions relative to the axes of rotation of the blanket cylinder 2.G are variable due to a degree of freedom for the Geberabstweiler.
  • the encoder control points 8.1, 8.2 or 8.3 serving to compensate for the control errors are located on a geometric location which can be determined from the geometrical conditions of the pivoting movement of the blanket cylinder 2.G with the aid of CAD programs for the time of the bearer ring contact. In the FIG. 1 are exemplary and not to scale three encoder support points 8.1, 8.2 or 8.3 shown, which were determined so.
  • the generation of a leading setpoint value for the drive controller of the plate cylinder 1.P can therefore be achieved, for example, by changing the lever length of the stator support 7 and / or changing the relative position to the pivoting curve of the axis of rotation of the blanket cylinder 2.G compared to the conventional encoder support point 8.0.
  • the conventional Geberabstütztician 8.0 located in the rolling point of plate and blanket cylinder 1.P, 2.G or in the rolling point of the associated bearer rings.
  • the further points 8.1, 8.2, 8.3 denote possible encoder support points, in which the Drehwinkelgebergephase is rotated in the approach phase of the cylinder surfaces by an additional angle, which compensates the following error .DELTA. ⁇ s and due to the acceleration of the blanket cylinder 2.G and the regulation delay during the pressure -an motion arises.
  • a suitable point 8.3 is preferably selected, which approximately compensates for the following error ⁇ s during the pressure-on movement and at the same time for eliminating the influence of the bending vibrations of the blanket cylinder 2.G due to the channel impacts when rolling on the impression cylinder 3 in the direction of the rubber cylinder 2.G (connecting line rubber cylinder 2.G - pressure cylinder 3) is arranged.
  • the encoder support point 8 should lie in the region of the cylinder circumference (8.1) in order to reduce the effects of disturbances in the area of the encoder support, in particular concentricity error of the encoder and encoder mounting, by using the largest possible lever length.
  • the finally selected encoder support point will advantageously be a compromise between the two requirements and is exemplified in the drawing as the encoder support point 8.2.
  • the blanket cylinder 2.G In the "print-on" position of the blanket cylinder 2.G is employed in a known manner both to the plate cylinder 1.P and to the impression cylinder 3 and transmits the pressure (partial) image of the plate cylinder 1.P on the printing cylinder 3 guided bows.
  • the second rotary encoder 6 on the shaft 10 of the blanket cylinder 2.G detects the time course of the rotational angle values of the blanket cylinder 2.G and transmits them to the drive control of the single drive M for the plate cylinder 1.P to the rotation of the plate cylinder 1.P with the synchronized by the drive wheel train rubber cylinder 2.G to synchronize.
  • Both cylinders 1, 2 rotate in the ideal case with the same peripheral speed and with a predetermined relative Drehwinkelsynchronlage.
  • the pivoting is in the millimeter range. In this case, the meshing of the drive wheels of rubber and pressure cylinder 2.G, 3 persist. When swinging it is therefore in addition to the displacement of the blanket cylinder 2.G against the plate cylinder 1.P to a rolling movement of the drive gear of the blanket cylinder 2.G on the printing cylinder gear to the tooth engagement point, which causes an additional rotation of the blanket cylinder 2.G.
  • This cylinder rotation is detected by the second rotary encoder 6 and then the plate cylinder 1.P synchronously by the drive control of the single drive M also rotated by this angle, so that it therefore no relative movement comes at the contact points with the plate cylinder 1.P (rubber pressure plate, bearer rings).
  • the correction rotation of the plate cylinder 1.P results in a circumferential path which approximates the translation path of a surface point on the blanket cylinder 2.G.
  • the plate cylinder 1.P carries out with its correction rotation the translational displacement of the blanket cylinder 2.G, whereby there may be no loss of the angular position of the two cylinders 1, 2.
  • the quality of approach of the circumferential path of the plate cylinder 1.P and translational path of the blanket cylinder 2.G is essential with increasing approach of the blanket cylinder 2.G to its print-on position for the print quality, since the plate cylinder 1.P in restoring the surface contact of the To prevent circumferential register errors or blurring of the printed image, bear in mind that it should rotate synchronously with the blanket cylinder 2.G.
  • the support point 8 of the rotary encoder 6 of the blanket cylinder 2.G to be pivoted 2.G is not placed in the rolling point of the bearer rings, as it is ideally considered, but deviates so that when the cylinder 1 moves toward one another, 2 of the following error .DELTA. ⁇ s of the drive control is compensated and the cylinder surfaces in the desired angular position to each other, ie, each other untwisted meet.
  • the control-induced following error .DELTA. ⁇ s in the rotational angle position of the plate cylinder 1.P causes the plate cylinder 1.P to lag in the range from 2 to 80 .mu.m and is compensated by an anticipatory rotation of the rotary encoder housing by a correction angle corresponding to .DELTA. ⁇ s .
  • the lagging of the plate cylinder 1.P compared to the synchronous position (target rotational position) as a result of the control delay is thus compensated with a corrected by the following error .DELTA. ⁇ s rotation angle setpoint, which causes a temporary flow of the plate cylinder 1.P, so that the cylinder surfaces at Swing the blanket cylinder 2.G against the plate cylinder 1.P in synchronizing position.
  • the resulting additionally in the pressure-off movement error is not critical, since it can be easily compensated by the drive controller after the end of the contact of blanket cylinder 2.G and plate cylinder 1.P.
  • the inventive compensation of control-related asynchronisms between electronically synchronized via rotary encoders cylinders or other bodies of revolution by shifting the Geberabstützins the setpoint generator is also on other pivotal cylinders, which are in the salaried state in rolling contact with adjacent cylinders used.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)

Claims (9)

  1. Machine d'impression rotative pour mettre en oeuvre un procédé de compensation d'asynchronismes d'angle de rotation conditionnés par un réglage, de deux cylindres entraînés indépendamment l'un de l'autre, qui surviennent pendant le mouvement d'approche de l'un des cylindres, dans laquelle
    - un premier cylindre (1) monté dans un bâti, auquel est affecté un entraînement individuel (M) électrique, se trouve en contact par roulement avec un second cylindre (2) contigu monté de manière pivotante, qui est raccordé à un second entraînement, pendant l'opération d'impression,
    - un capteur d'angle de rotation (6) est agencé contre le second cylindre (2), lequel fournit des valeurs nominales d'angle de rotation pour un réglage d'entraînement de l'entraînement individuel (M), dans laquelle
    - un logement de capteur d'angle de rotation forme un stator (6.S) du capteur d'angle de rotation (6), monté de manière rotative autour de l'axe de rotation du second cylindre (2) et est soutenu par un support de moment de couple (7) contre un point de support de capteur (8) solidaire du bâti et
    - un rotor (6.R) du capteur d'angle de rotation (6) est raccordé à l'axe de rotation du second cylindre (2) de manière à résister à la torsion,
    caractérisée
    en ce que le point de support de capteur (8.1, 8.2, 8.3) est agencé à distance dans une direction radiale et/ou circonférentielle du point de support de capteur (8.0) conventionnel formé par le point de roulement du cylindre (1, 2) ou par des bagues de support, dans lequel direction et grandeur de l'écart du point de support de capteur (8.0) conventionnel sont déterminés par l'erreur de poursuite Δαs à contrebalancer du réglage d'entraînement, de sorte qu'un retard lié à un réglage est compensé à hauteur de l'erreur de poursuite Δαs entre la position d'angle de rotation souhaitée et la position d'angle de rotation réalisée du premier cylindre (1) pendant le basculement du second cylindre (2) contre le premier cylindre (1), de sorte que les surfaces de cylindre se rencontrent au moment du contact en position synchrone.
  2. Machine d'impression rotative selon la revendication 1,
    caractérisée
    en ce que le premier cylindre (1) est un cylindre porte-plaque (1.P) avec entraînement individuel (M) dans une machine d'impression rotative offset à feuilles et
    en ce que le second cylindre (2) est un cylindre porte-blanchet (2.G), lequel peut pivoter depuis une position de « dégagement » sans contact de surface vers une position de « pressage » dans laquelle des bagues de support agencées contre le cylindre porte-plaque (1.P) et le cylindre porte-blanchet (2.G) se déroulent les unes sur les autres.
  3. Machine d'impression rotative selon la revendication 1 ou 2,
    caractérisée
    en ce que le point de support de capteur (8.1) se situe dans la région de la circonférence du cylindre pour réduire, par une longueur du levier si possible grande, les effets d'interférences dans la région du support de capteur, notamment des défauts de concentricité de capteur et fixation de capteur.
  4. Machine d'impression rotative selon la revendication 2 ou 3,
    caractérisée
    en ce que le point de support de capteur (8.1, 8.2, 8.3) est déplacé, pour éliminer l'impact de vibrations de flexion du cylindre porte-blanchet (2.G) suite à un roulement sur les gorges, dans une zone d'impression formée entre le cylindre porte-blanchet (2.G) et un cylindre d'impression (3) vers la droite de jonction entre l'axe du cylindre d'impression (3) et l'axe du cylindre porte-blanchet (2.G).
  5. Machine d'impression rotative selon la revendication 2, 3 ou 4,
    caractérisée
    en ce que le point de support de capteur (8.2) est déplacé, pour éliminer l'impact de vibrations de flexion du cylindre porte-blanchet (2.G) suite à un roulement sur les gorges et pour réduire des interférences dans la région du support de capteur, dans une direction radiale et circonférentielle par rapport au cylindre porte-blanchet (2.G).
  6. Machine d'impression rotative selon la revendication 2, 3, 4 ou 5,
    caractérisée
    en ce que la direction et la grandeur de la distance du point de support de capteur (8.0) conventionnel dépendent en outre de la géométrie d'engrenage pivotant ou de la courbe pivotante des axes de rotation du cylindre porte-blanchet (2.G).
  7. Procédé de compensation d'asynchronismes d'angle de rotation conditionnés par un réglage, de deux cylindres entraînés indépendamment l'un de l'autre dans des machines d'impression rotative, qui surviennent pendant un mouvement d'approche de l'un des cylindres, dans laquelle
    - un premier cylindre (1) monté dans un bâti, auquel est affecté un entraînement individuel (M) électrique, se trouve en contact par roulement avec un second cylindre (2) contigu monté de manière pivotante, qui est raccordé à un second entraînement, pendant l'opération d'impression,
    - un capteur d'angle de rotation (6) est agencé contre le second cylindre (2), lequel fournit des valeurs nominales d'angle de rotation pour un réglage d'entraînement de l'entraînement individuel (M), dans laquelle
    - un logement de capteur d'angle de rotation forme un stator (6.S) du capteur d'angle de rotation (6), monté de manière rotative autour de l'axe de rotation du second cylindre (2) et est soutenu par un support de moment de couple (7) contre un point de support de capteur (8) solidaire du bâti et
    - un rotor (6.R) du capteur d'angle de rotation (6) est raccordé à l'axe de rotation du second cylindre (2) de manière à résister à la torsion, caractérisée
    en ce que un retard lié à un réglage est compensé à hauteur de l'erreur de poursuite Δαs entre la position d'angle de rotation souhaitée et la position d'angle de rotation réalisée du premier cylindre (1) pendant le basculement du second cylindre (2) contre le premier cylindre (1) par déplacement du point de support de capteur (8.1, 8.2, 8.3) du point de support de capteur (8.0) conventionnel, lequel permet un synchronisme d'angle de rotation chez un cylindre (2) engagé sans tenir compte d'erreurs de réglage, de sorte que les surfaces de cylindre se rencontrent au moment du contact en position synchrone.
  8. Procédé selon la revendication 7,
    dans lequel après un premier contact des surfaces de cylindre, la grandeur de correction est à nouveau contrebalancée pendant la mise en place du pressage par l'agencement du point de support de capteur (8.1, 8.2, 8.3) et suite à l'inertie du régulateur comparé à la vitesse du mouvement de mise en pression, de sorte qu'au point final du mouvement pivotant les cylindres (1, 2) se trouvent de manière exacte l'un par rapport à l'autre.
  9. Procédé selon la revendication 7 ou 8,
    dans lequel l'erreur de poursuite Δαs conditionnée par un réglage et à contrebalancer provoque dans la position d'angle de rotation d'un cylindre porte-plaque (1.P) un retard du cylindre porte-plaque (1.P) dans la plage de 2 à 80 µm et est contrebalancée par une torsion anticipée du logement de capteur d'angle de rotation à hauteur d'un angle de correction Δαs correspondant.
EP08172069.0A 2007-12-22 2008-12-18 Procédé et agencement de compensation d'asynchronismes d'angles de rotation en fonction du réglage Active EP2072252B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102007062628 2007-12-22

Publications (3)

Publication Number Publication Date
EP2072252A2 EP2072252A2 (fr) 2009-06-24
EP2072252A3 EP2072252A3 (fr) 2012-07-04
EP2072252B1 true EP2072252B1 (fr) 2018-11-14

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE102021112080A1 (de) 2021-05-10 2022-11-10 Koenig & Bauer Ag Verfahren zum Betreiben einer Bogendruckmaschine mit mindestens einem Druckwerk
DE102022102028A1 (de) 2022-01-28 2023-08-03 Koenig & Bauer Ag Verarbeitungswerk und Verfahren zum Betreiben eines Verarbeitungswerkes einer Verarbeitungsmaschine

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Publication number Priority date Publication date Assignee Title
DE19623224C1 (de) 1996-06-11 1997-09-11 Roland Man Druckmasch Antrieb für eine Druckmaschine
DE19635796C2 (de) 1996-09-04 1998-07-02 Roland Man Druckmasch Befestigung für einen Drehgeber
DE19720952C2 (de) 1997-05-17 2001-02-01 Roland Man Druckmasch Schwenkbarer, durch einen elektrischen Einzelantrieb angetriebener Zylinder
DE10304495B4 (de) 2003-02-05 2015-04-16 Koenig & Bauer Aktiengesellschaft Verfahren und Anordnung für die Synchronisierung eines elektrischen Einzelantriebes
DE102005018528C5 (de) 2004-05-05 2019-03-14 manroland sheetfed GmbH Lagegeber für einen Direktantrieb eines Zylinders in einer Verarbeitungsmaschine
DE102005029968A1 (de) 2005-06-28 2007-01-11 Koenig & Bauer Ag Anordnung von Drehwinkelgebern
DE102005029969A1 (de) 2005-06-28 2007-01-11 Koenig & Bauer Ag Anordnung von Drehwinkelgebern

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* Cited by examiner, † Cited by third party
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Publication number Publication date
DE102008054854A1 (de) 2009-06-25
EP2072252A2 (fr) 2009-06-24
EP2072252A3 (fr) 2012-07-04

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