EP0467832B1 - Dispositif pour le transfert des feuilles seules au cylindre presseur d'une presse rotative à feuilles - Google Patents

Dispositif pour le transfert des feuilles seules au cylindre presseur d'une presse rotative à feuilles Download PDF

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Publication number
EP0467832B1
EP0467832B1 EP91810527A EP91810527A EP0467832B1 EP 0467832 B1 EP0467832 B1 EP 0467832B1 EP 91810527 A EP91810527 A EP 91810527A EP 91810527 A EP91810527 A EP 91810527A EP 0467832 B1 EP0467832 B1 EP 0467832B1
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EP
European Patent Office
Prior art keywords
shaft
cylinder
drum
sheet
printing
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
EP91810527A
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German (de)
English (en)
Other versions
EP0467832A2 (fr
EP0467832A3 (en
Inventor
Albrecht Josef Germann
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.)
KBA Notasys SA
Original Assignee
De la Rue Giori SA
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
Application filed by De la Rue Giori SA filed Critical De la Rue Giori SA
Publication of EP0467832A2 publication Critical patent/EP0467832A2/fr
Publication of EP0467832A3 publication Critical patent/EP0467832A3/de
Application granted granted Critical
Publication of EP0467832B1 publication Critical patent/EP0467832B1/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F21/00—Devices for conveying sheets through printing apparatus or machines
    • B41F21/10—Combinations of transfer drums and grippers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F11/00—Rotary presses or machines having forme cylinders carrying a plurality of printing surfaces, or for performing letterpress, lithographic, or intaglio processes selectively or in combination

Definitions

  • the invention relates to a device for transferring individual sheets to the printing cylinder of a sheet-fed rotary machine according to the preamble of patent claim 1.
  • Such sheet transfer devices in rotary printing presses often consist of a stop drum and a transfer drum cooperating therewith, which transports the sheets onto the printing cylinder at regular intervals. These distances of course correspond to the positions of the printing plates which are evenly fastened on the plate cylinder of the printing press.
  • a device of the type described in the preamble of claim 1 is known. This device works with a suction conveyor roller which can be driven at a non-uniform speed such that a sheet conveyed by it is conveyed against the front stops of the printing cylinder at a somewhat excessive speed.
  • the previously known sheet transfer devices have in common that they deliver the incoming sheets to the printing cylinder in exactly the same rhythm, the transfer point of the transfer cylinder at which the leading edge of the sheet is taken over by the grippers of the printing cylinder is always the same.
  • care must be taken when attaching the printing plates to the plate cylinder that the printing plates are exactly uniform, i.e. with exact the same distance on the circumference of the plate cylinder. So that means that with a plate cylinder cylinders with two, with three or with four pressure plates, these must have an exact angular distance of 180 °, 120 ° or 90 °.
  • AT-B-319 982 discloses a drive device for the sheet feed cylinder in printing machines, in which the gripper device can be adjusted relative to the cylinder shaft during one revolution of the cylinder, but this adjustment is sufficient even with larger sheet formats and higher printing output To achieve a long time interval for the sheet acceptance, so that a suitable sheet transfer is made possible by the gripper device.
  • the gripper device is installed on the cylinder shaft, and a uniformly rotating gear wheel is mounted on the cylinder shaft, which meshes with the drive gear wheel of the printing cylinder.
  • the cylinder shaft is connected to the gearwheel in such a way that the cylinder shaft rotates at a predeterminable, variable angular velocity during the rotation of the sheet feed cylinder, whereby the desired relative movement of the gripper device is generated, which also is adjustable relative to the cylinder shaft with the aid of a further control curve.
  • the invention has for its object to provide a sheet transfer device which allows an automatic adjustment of the sheet transfer such that the sheets always reach the printing plates printing them in an exactly aligned position, that is to say completely in register, so that the need for the printing plates themselves is eliminated their opening on the plate cylinder at exactly the same angular intervals.
  • the printing plates do not need to be adjusted to exact positions within a fraction of a millimeter when they are attached to the plate cylinder, but it is sufficient to adjust the adjusting device for the front stop of the transfer cylinder in accordance with the positions of the printing plates on the plate cylinder before printing begins adjust.
  • This can either be done by hand on the basis of a few test prints or automatically by servomotors, which are controlled by reading devices as a function of register marks printed on the sheets.
  • stretching of the printing plates can be approximately compensated for by adjusting the adjusting device without readjusting them.
  • the transfer cylinder 2 of the device is arranged between a feed roller S and the printing cylinder D of a rotary printing press, in particular an intaglio printing press, the plate cylinder P of which, only schematically indicated in FIG. 6, cooperates with the printing cylinder D and at least two printing plates, generally N.
  • the plate cylinder P has four printing plates which are mounted at an angular distance of approximately 90 °, that is, they do not necessarily have to be adjusted to a fraction of a millimeter exactly at a 90 ° distance on the plate cylinder.
  • the sheets B are fed one by one onto the transfer cylinder 2 by the feed roller S, which in the example under consideration is a known suction roller which is driven at a non-uniform speed, an incoming sheet being conveyed against the front stop 8a of the transfer cylinder 2 and by the latter until it is handed over to the printing cylinder D.
  • the front stop 8a is part of a curved grip 8 articulated on the transfer cylinder 2, which according to FIG the sheet B, which is schematically indicated, moves the sheet B and transfers it to the sheet gripper G2 of the printing cylinder D according to FIG.
  • the directions of rotation of all cylinders are indicated by arrows in FIGS. 1 to 3.
  • impression cylinder D and plate cylinder are of the same size, and since there are four printing plates, the impression cylinder D has four printing segments covered with rubber blankets and sheet grippers in front of each rubber blanket, of which the gripper G1 in FIG. 1 and the gripper G2 can be seen in FIG.
  • the diameter of the transfer cylinder 2 is 1 / N of the diameter of the plate cylinder, in the example considered a quarter of this diameter, accordingly the transfer cylinder 2 executes and rotates N revolutions for one full rotation of the plate cylinder or the printing cylinder, i.e. four revolutions in the example considered one sheet B.
  • FIGS. 3 to 5 The structure of the device according to the invention will now be described with reference to FIGS. 3 to 5 and the highly schematic FIGS. 6 and 7, on which the parts which correspond to the parts shown in FIGS. 3 to 5 are provided with the same reference symbols.
  • the transfer cylinder 2 has a shaft 3 driven at a uniform speed which makes N revolutions when the plate cylinder P makes one full revolution; if the impression cylinder D has the same diameter as the plate cylinder, which is generally the case, then of course this corresponds to one revolution of the impression cylinder.
  • the printing cylinder can also have a different diameter than the plate cylinder.
  • the diameter of the printing cylinder D is only 1 / N of the diameter of the plate cylinder P, that is to say the printing cylinder D is only adapted to the size of a sheet and is exactly the same size as the transfer cylinder 2.
  • the transfer cylinder 2 has a drum 4 which is adjustable in the circumferential direction relative to its shaft 3 and on which the sheet gripper 8 is articulated with its front stop 8a.
  • a drum 4 which is adjustable in the circumferential direction relative to its shaft 3 and on which the sheet gripper 8 is articulated with its front stop 8a.
  • several sheet grippers lying side by side in a row are provided both on the transfer cylinder 2 (FIG. 7) and on the printing cylinder D.
  • the shaft 3 and the drum 4 are kinematically connected to one another by two levers 12 and 13.
  • the one ends of both levers 12 and 13 are pivotally connected to one another at a common articulation point 14.
  • a roller 15 is rotatably mounted.
  • the other end of the lever 12 is articulated on a part 6 fastened to the shaft 3 by means of a pin 16 and the other end of the lever 13 is articulated on a part 5 fastened on the drum 4 by means of a pin 17. 3, this part 5 is indicated as a thickening of the drum 4.
  • the axis of the shaft 3 and the mentioned levers 12 and 13 are surrounded by an annular actuator 10 which is outside of the Axis of the shaft 3 lying pin 11 is pivotally articulated on the device frame 1 and has a cylindrical inner circumference 10a, on which the roller 15 bears under the action of a spring 18 and can roll.
  • This spring 18 is compressed between a shoulder 7 of the part 6 and a spring plate 19 pivotably pivoted about the pin 19a on the part 5 and therefore seeks to press the shaft 3 and drum 4 in opposite directions, as a result of which the articulation point 14 with the roller 15 against the inner circumference 10a of the actuator 10 is pressed.
  • the adjustment of the actuator 10 is supported by the spring 26.
  • this actuator 10 can now be deflected somewhat in one direction or the other from the neutral position shown in FIG. 3, in which its inner circumference 10a is concentric to the axis of the shaft 3, in what way, how from the following description it follows that a corresponding displacement of the drum 4 relative to the shaft 3 in one or the other circumferential direction results.
  • This control device has a cam disk 9 attached laterally to the shaft 3 in the form of an eccentric and a lever mechanism which, in the example under consideration, consists of two two-armed, angled levers 20 and 25.
  • the mutually adjacent lever arms 20b and 25a of the two levers are pivotally attached to one another at a common joint point 24.
  • the lever 20 is pivotally attached to the actuator 10 by means of a pin 21 which is diametrically opposite the pin 11.
  • the other lever arm 20a of the lever 20 extends up to the circumference of the cam disk 9 and carries at its end a cam roller 23 which can be rotated about the axis 22.
  • the other lever 25 is articulated on the device frame 1 by means of a pin 27 fastened thereon.
  • the end of its other lever arm 25b carries a wheel 28, in the example under consideration a gearwheel which can be rotated about the axis 30 and is driven in this way by means of a drive wheel 31 at a uniform speed is that it makes 1 / N revolutions with one complete revolution of the transfer drum, i.e. a quarter revolution in the example considered.
  • the wheel 28 is driven by a gear 35 seated on the shaft 3, which meshes with a gear 34 of twice the size on the axis 33, and via a gear 32 seated on the axis 33, which meshes with the toothed drive wheel 31 combs and is half the size of this one.
  • the wheel 28, which is as large as the drive wheel 31, is therefore driven with respect to the shaft 3 with a reduction ratio of 4: 1.
  • N stop parts 28a to 28d are fastened on the axis 30 of the wheel 28, their angular distance from one another being 360 ° / N, that is to say 90 ° in the example considered.
  • These stop parts interact with individually adjustable stationary stops 29a to 29d, which, at the level of the relevant stop parts 28a to 28d, are slidably mounted in the device frame 1 for the purpose of adjustment.
  • FIG. 7 schematically illustrates four different positions of these stops 29a to 29d and also indicates servomotors Ma, Mb, Mc, Md coupled to these stops, by means of which the stops can be set.
  • the lever mechanism described from the levers 20 and 25 can thus be pivoted about the stationary pin 27 on the frame and is subject to a spring 26 which is supported on the frame 1 and acts on the lever mechanism in such a way that the cam roller 23 at the end of the lever 20 is pressed against the cam disc 9.
  • the spring 26 acts on the joint 24 of the two levers 20 and 25.
  • the cam roller 23 continuously rolls on the circumference of the cam disk 9 when the shaft 3 rotates under the action of the spring 26, as a result of which the levers 20 and 25 correspond to the shape of the eccentric cam disk 9 Carry out pivoting movement and consequently the actuator 10 articulated on the lever 20 swings back and forth from its neutral position in exactly the same way with each revolution of the cam disk.
  • the levers 12 and 13 which are guided by the roller 15 along the inner circumference 10a, cause a small displacement of the drum 4 relative to the shaft 3 in or opposite to the direction of rotation thereof.
  • the amplitude of the pivoting of the actuator 10, that is the maximum deflection, is defined by the eccentricity of the cam disk 9. This eccentricity is dimensioned in such a way that the maximum permissible tolerances when fastening the printing plates to the plate cylinder can be compensated for by appropriately corrected sheet transfers to the printing cylinder.
  • the shape of the cam disk 9 is selected such that approximately half a peripheral section 9a has a shape concentric to the axis of the shaft 3, while the other half peripheral section 9b has a continuously decreasing and then increasing radius, that is to say the actual eccentricity.
  • the arrangement is such that the cam roller 23 is in the area of the maximum eccentricity, ie in the area E of the smallest radius of the cam disk 9, when the sheet gripper 8 passes the sheet transfer position.
  • these servomotors can be operated, for example, by pressing a button on a control panel, or the servomotors are controlled as a function of the register deviations measured automatically by reading register marks.
  • the register marks applied during printing are used for this purpose, the reading of which corrects the positions of the subsequent sheets. If the incoming sheets already have a first print, for example a background, then register marks printed in the first printing unit can be used for automatic register correction.
  • the cam roller 23 rests under the action of the spring 26 at the beginning of the concentric peripheral section 9a of the cam disk 9, and according to FIG. 4, while the sheet B is taken over by the transfer drum 2, the cam roller 23 is located in the end region of this peripheral section 9a .
  • FIG. 5 at the moment the sheet is transferred to the impression cylinder, the position of the levers 20, 25 and so that the cam roller 23 is determined by one of the stops 29a to 29d, on which the relevant stop part 28a to 28d rests, so that the cam roller 23 remains in a more or less raised position from the cam disk 9, which corresponds to the desired displacement of the drum 4 with respect to the Wave 3 corresponds.
  • the cam roller 23 lies in front of the area E of the smallest radius of the cam disk 9.
  • FIG. 5 shows three different positions S1, S2 and S3 of the adjustable parts, namely a middle position and two extreme positions, that is to say one position shifted to one side and one position shifted to the other side.
  • the drum 4 In the position S1 shown in solid lines, which is determined by the stop 29a, the drum 4 assumes a central position relative to the shaft 3, which can correspond, for example, to the exactly adjusted position of the printing plate in question on the plate cylinder.
  • the effective stop 29b is further away from the axis 30 of the wheel 28, so that the lever 25 is pivoted somewhat clockwise relative to the position S1. This causes the transfer point of transfer cylinder 2 to be shifted somewhat in the opposite direction to its direction of rotation.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
  • Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Rotary Presses (AREA)
  • Registering Or Overturning Sheets (AREA)
  • Replacement Of Web Rolls (AREA)
  • Electrostatic Charge, Transfer And Separation In Electrography (AREA)

Claims (7)

  1. Dispositif pour le transfert de feuilles isolées au cylindre d'impression d'une machine d'impression rotative a la feuille comprenant un cylindre porte-plaques (P) équipé de N plaques d'impression, N étant un nombre entier supérieur à 1, et comprenant un cylindre de transfert (2) coopérant avec le cylindre d'impression, caractérisé en ce que le cylindre de transfert (2), dont le diamètre est égal à un Nième din diamètre du cylindre porte-plaques (P), présente un arbre (3) pouvant être entraîné à une vitesse constante et effectuant N rotations pour une rotation du cylindre porte-plaques (P), et un tambour (4) muni d'une butée avant (8a) pour les feuilles (B) arrivant et pouvant être déplacé relativement à l'arbre (3) en direction périphérique au moyen d'un dispositif de réglage commandable, que ce dispositif de réglage présente deux leviers (12, 13) reliant l'arbre (3) et le tambour (4) et reliés ensemble de manière articulée par une de leurs extrémités, l'un des leviers (12) étant articulé par son autre extrémité à une pièce (6) fixée sur l'arbre (3) et l'autre levier étant articulé par son autre extrémité a une pièce (5) fixée au tambour (4), ces leviers portant au niveau de leur point d'articulation commun (14) un galet de roulement (15), qu'il est prévu un organe de réglage (10) en forme d'anneau et entourant l'axe de l'arbre (3), cet organe de réglage étant articulé au bâti (1) du dispositif de façon à pivoter autour d'un pivot (11) ne se trouvant pas sur l'axe de l'arbre (3), la circonférence intérieure (10a) de l'organe de réglage (10) étant cylindrique, ledit galet de roulement (15) étant appuyé sous l'action d'un ressort (18) contre cette circonférence intérieure (10a) et pouvant rouler sur celle-ci, et qu'il est prévu un dispositif de commande provoquant le basculement de l'organe de réglage (10) à chaque rotation din cylindre de transfert (2), ce dispositif de commande déviant l'organe de réglage (10) d'une position neutre dans une position excentrée par rapport à l'axe de l'arbre (3), cette déviation permettant aux deux leviers (12, 13) dirigés par le galet de roulement (15) de déplacer le tambour (4) et ainsi la butée avant (8a) relativement à l'arbre (3) de telle sorte que lors din passage de la butée avant (8a) dans sa position de transfert, dans laquelle une feuille est transférée au cylindre d'impression, cette butée avant (8a) prend une position au moyen de laquelle le registre exact de cette feuille est réglé relativement à la position sur le cylindre porte-plaques (P) de la plaque d'impression imprimant cette feuille.
  2. Dispositif selon la revendication 1, caractérisé en ce que la butée avant (8a) est une partie de pinces de feuilles (8) articulées au tambour (4).
  3. Dispositif selon la revendication 1 ou 2, caractérisé en ce que ledit ressort (18) est disposé entre une pièce fixée à l'arbre (3) et une pièce fixée an tambour (4) et exerce une pression sur l'arbre (3) et le tambour (4) dans des directions opposées.
  4. Dispositif selon la revendication 3, caractérisé en ce que le galet de roulement (15), les leviers (12, 13) et lesdites pièces (5, 6) sont disposés de telle sorte en direction périphérique que l'organe de réglage (10) est appuyé par la force de pression dans la position de travail correspondante.
  5. Dispositif selon l'une des revendications 1 à 4, caractérisé en ce que le dispositif de commande présente un disque à cames (9) en forme d'excentrique, fixé à l'arbre (3) et un mécanisme à leviers, d'une part articulé au côté de l'organe de réglage (10) opposé au pivot (11) et d'autre part monté pivotant sur un axe de rotation (27) monté fixement sur le bâti du dispositif (1), que ce mécanisme à leviers porte à une extrémité un cylindre à cames (23) dont le but est d'appuyer un ressort (26) contre la circonférence du disque à cames (9), ce qui permet de déplacer le mécanisme à leviers et ainsi l'organe de réglage (10) conformément à la configuration du disque à cames (9) lors de la rotation de l'arbre (3), et que le déplacement maximal du mécanisme à leviers défini par l'excentricité du disque à cames (9) peut être limité par N butées (29a à 29d) réglables individuellement, ces butées devenant actives l'une après l'autre au cours de N rotations successives du cylindre de transfert (2).
  6. Dispositif selon la revendication 5, caractérise en ce que le mécanisme à leviers est constitué de deux leviers (20, 25), reliés ensemble de manière articulée par l'une de leurs extrémités, un des leviers (20) étant articulé à l'organe de réglage (10) et portant à son autre extrémité ledit cylindre à cames (23), l'autre levier (25) étant articulé au bâti du dispositif (1) et portant à son autre extrémité une roue rotative et entraînable (28) à laquelle sont fixées N pièces de butée (28a à 28d), coopérant chacune avec l'une des N butées (29a à 29d) réglables, les pièces de butée étant disposées l'une à côte de l'autre en direction axiale de la roue (28) avec un espacement angulaire de 360°/N et les butées (29a à 29d) étant disposées en ligne l'une à côté de l'autre, la roue (28) effectuant un Nième de rotation pour une rotation complète du cylindre de transfert(2).
  7. Dispositif selon la revendication 6, caractérisé en ce que les butées réglables (29a à 29d) sont couplées avec des servomoteurs (Ma, Mb, Mc, Md) actionnables manuellement ou en fonction de l'écart de registre mesuré automatiquement en lisant les marques de registre
EP91810527A 1990-07-20 1991-07-05 Dispositif pour le transfert des feuilles seules au cylindre presseur d'une presse rotative à feuilles Expired - Lifetime EP0467832B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH241190 1990-07-20
CH2411/90 1990-07-20

Publications (3)

Publication Number Publication Date
EP0467832A2 EP0467832A2 (fr) 1992-01-22
EP0467832A3 EP0467832A3 (en) 1993-07-28
EP0467832B1 true EP0467832B1 (fr) 1996-08-28

Family

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Family Applications (1)

Application Number Title Priority Date Filing Date
EP91810527A Expired - Lifetime EP0467832B1 (fr) 1990-07-20 1991-07-05 Dispositif pour le transfert des feuilles seules au cylindre presseur d'une presse rotative à feuilles

Country Status (11)

Country Link
US (1) US5125336A (fr)
EP (1) EP0467832B1 (fr)
JP (1) JP2951440B2 (fr)
KR (1) KR0163789B1 (fr)
CN (1) CN1028979C (fr)
AT (1) ATE141890T1 (fr)
AU (1) AU637750B2 (fr)
CA (1) CA2047473C (fr)
DE (1) DE59108115D1 (fr)
RU (1) RU1838154C (fr)
UA (1) UA19835A (fr)

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DE4330392A1 (de) * 1993-09-08 1995-03-16 Heidelberger Druckmasch Ag Schwingender Vorgreifer einer Bogendruckmaschine
US5421257A (en) * 1993-12-02 1995-06-06 Okuda; Masaharu Sheet transferring machine for printing machine
ATE167112T1 (de) * 1994-02-17 1998-06-15 De La Rue Giori Sa Vorrichtung zur uebergabe einzelner bögen an den druckzylinder einer bogenrotationsdruckmaschine
DE19901699B4 (de) * 1998-02-04 2007-11-15 Heidelberger Druckmaschinen Ag Verfahren und eine Vorrichtung zur Durchführung des Verfahrens zur Beseitigung von rhythmischen Passerfehlern in Rotationsdruckmaschinen
CA2372719A1 (fr) * 1999-05-24 2000-11-30 Dennis P. Couturier Appareil de retention de tissu et procede destine a une lame de coupe
EP1361028A1 (fr) * 2002-05-06 2003-11-12 Kba-Giori S.A. Dispositif de découpe destiné à découper des fenêtres dans un substrat
EP1442878A1 (fr) * 2003-02-03 2004-08-04 Kba-Giori S.A. Entraínement du dispositif d'encrage dans une machine d'impression en creux
EP2749416B1 (fr) * 2012-12-28 2020-01-22 Komori Corporation Presse d'impression en creux
DE102019108763A1 (de) * 2019-04-03 2020-10-08 Fraunhofer-Gesellschaft zur Förderung der angewandten Forschung e.V. Vorrichtung und Verfahren zum Aufbringen einer Struktur aus Druckmedium auf ein Substrat

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US1514049A (en) * 1922-12-27 1924-11-04 Ichida Koshiro Rotary multicolor printing press
FR576960A (fr) * 1923-02-14 1924-08-29 Machine pour l'impression en offset en deux couleurs
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DE2435203C2 (de) * 1974-07-22 1981-10-01 Van Vlaanderen Machine Co., Paterson, N.J. Bogen-Rotationsdruckmaschine
JPS53135710A (en) * 1977-04-30 1978-11-27 Raes Karl Printing cylinder unit
DE3112964A1 (de) * 1981-04-01 1982-10-21 Heidelberger Druckmaschinen Ag, 6900 Heidelberg "bogenuebertragungszylinder von bogenrotationsdruckmaschinen mit einer einrichtung zur passerkorrektur der aufdrucke"
DE3428668A1 (de) * 1984-08-03 1986-02-13 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Umfuehrtrommel fuer bogendruckmaschinen, insbesondere kartonmaschinen
DE3445886A1 (de) * 1984-12-15 1986-06-26 M.A.N.- Roland Druckmaschinen AG, 6050 Offenbach Greifervorrichtung fuer eine druckmaschine
JPS61148058A (ja) * 1984-12-24 1986-07-05 Shinohara Tekkosho:Kk 枚葉印刷機の用紙展伸調整装置
JPH082630B2 (ja) * 1985-03-26 1996-01-17 リョービ株式会社 オフセット印刷機
DE3836544A1 (de) * 1988-10-27 1990-05-03 Rotaprint Gmbh Gegendruckzylinder mit greifersystem

Also Published As

Publication number Publication date
KR920002335A (ko) 1992-02-28
CN1060063A (zh) 1992-04-08
EP0467832A2 (fr) 1992-01-22
ATE141890T1 (de) 1996-09-15
CA2047473C (fr) 2000-11-14
CN1028979C (zh) 1995-06-21
UA19835A (uk) 1997-12-25
RU1838154C (ru) 1993-08-30
CA2047473A1 (fr) 1992-01-21
JPH04226759A (ja) 1992-08-17
AU7946191A (en) 1992-01-23
DE59108115D1 (de) 1996-10-02
AU637750B2 (en) 1993-06-03
JP2951440B2 (ja) 1999-09-20
KR0163789B1 (ko) 1999-03-30
US5125336A (en) 1992-06-30
EP0467832A3 (en) 1993-07-28

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