EP0686502B1 - Installation pour réduire la flexion d'un cylindre dans des machines d'impression rotatives - Google Patents

Installation pour réduire la flexion d'un cylindre dans des machines d'impression rotatives Download PDF

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Publication number
EP0686502B1
EP0686502B1 EP95810333A EP95810333A EP0686502B1 EP 0686502 B1 EP0686502 B1 EP 0686502B1 EP 95810333 A EP95810333 A EP 95810333A EP 95810333 A EP95810333 A EP 95810333A EP 0686502 B1 EP0686502 B1 EP 0686502B1
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EP
European Patent Office
Prior art keywords
cylinder
crank
force
bending
external force
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
EP95810333A
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German (de)
English (en)
Other versions
EP0686502A3 (fr
EP0686502A2 (fr
Inventor
Peter Ing. Htl Gertsch
Robert Ing. Htl Imhof
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Wifag Maschinenfabrik AG
Original Assignee
Wifag Maschinenfabrik AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Publication of EP0686502A2 publication Critical patent/EP0686502A2/fr
Publication of EP0686502A3 publication Critical patent/EP0686502A3/fr
Application granted granted Critical
Publication of EP0686502B1 publication Critical patent/EP0686502B1/fr
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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
    • B41F13/08—Cylinders
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F13/00—Common details of rotary presses or machines
    • B41F13/08—Cylinders
    • B41F13/24—Cylinder-tripping devices; Cylinder-impression adjustments
    • B41F13/26—Arrangement of cylinder bearings
    • B41F13/28—Bearings mounted eccentrically of the cylinder axis

Definitions

  • the present invention relates to a method and an apparatus for influencing the Bending curve of a cylinder of a rotary printing press.
  • the Back-up rings are usually on the cylinder shaft between the cylinder and its bearing, i.e. arranged within the cylinder bearings in the machine frame.
  • the generic DE-AS 20 33 515 relates to the local change of that generated by a pressure cylinder Printed image. For this purpose, a bending moment is applied to the cylinder, whereby the position, the length and the largest deflection of the bending lines of the desired one Print image changes are adjusted.
  • the forces to bend the cylinder attack on bearing points that are spaced from the two pivot bearings of the cylinder are.
  • the forces are applied by means of pistons, each via piston rods to a bearing body act or applied via eccentric.
  • the bearing journals are in the eccentrics of the cylinder eccentrically to the axis of rotation of the eccentric.
  • US-43,722.05 relates to a device for bending a cylinder parallel to an opposing cylinder a rotary printing machine, in particular a forme cylinder in a gravure printing machine to a bending press.
  • a clamping device at the two ends of a bending press is an individual Adjustment of the bending moment and thus the deflection of the impression roller according to position, Length and size of the deflection and the contact pressure at the ends related to the impression cylinder possible.
  • the setting of the bending moment in relation to different ones Printing positions of a printing cylinder is however not possible.
  • DE-29 40 879 relates to a device for bending a printing roller in a rotary printing press and teaches an operating principle with the due to the opposite adjustment of the control lever by means of a connected pneumatic cylinder a bending moment can be transferred to the jacket of a pressure roller.
  • This principle of action is not designed to change the direction of the on the cylinder counteracting line loads, such as those caused by changing operating states of the cylinder is caused.
  • the object of the invention is to adapt a cylinder preload to different Set operating states of the cylinder.
  • the invention relates to a method for influencing the bending profile of a cylinder a rotary printing press.
  • Axis of rotation of the cylinder generated at a distance from a machine-side bearing of the Cylinder applied to a pin of the cylinder.
  • the bending moment serves to deflect the cylinder due to a bending load in different positions of the cylinder.
  • the preload force is generated by a gearbox in the different positions of the Cylinder blocked in a different gear position as the resultant force
  • the invention further relates to a device for influencing the bending profile of a Cylinder of a rotary printing press by applying a bending moment around one Axis transverse to an axis of rotation of the cylinder.
  • the bending moment is applied using a crank that is spaced from a machine side bearing of the cylinder a pivot of the cylinder is rotatably mounted in a rotary bearing and a drive a changeable external force can be applied to the crank.
  • the external force acts eccentrically on the pivot bearing of the crank.
  • It is at least one blocking means is provided, through which the crank against one through the outer Force caused rotation in at least two stop angular positions with respect to the cylinder is lockable, in each of which a reaction force on the external bearing of the crank Force is exerted which, together with the external force, forms a parallelogram of forces, the resulting force of a deflection of the cylinder due to a bending load counteracts.
  • the application of an external force by a specially designed drive opens basically the possibility to flexibly adjust the preload to any operating condition Adjust cylinders.
  • the external force can be controlled by controlling the drive to change. Manual adjustment on site is not necessary. A shot of one Machine control center will be possible. If necessary, the driving force can also be during of operations can be changed.
  • the direction of the bending load acting on the cylinder changes considerably, while the position of the cylinder in the room is changed little.
  • the biasing force can be on the cylinder journal at a location between or outside the machine-side cylinder bearing applied to either or both cylinder journals become.
  • the transmission is preferably designed as a push crank. According to the invention, it has one on the cylinder journal rotatably mounted crank on which the outer, from the drive applied force attacks. Furthermore, a blocking agent that can only be loaded on tension becomes one hinged to the crank and the other to the machine frame. This is the Crank can be locked in a given angular position.
  • Blocking agents can also be a pressure-resistant blocking agent for force deflection be used. A parallelogram of forces is thus formed between that of the drive external force exerted on the crank and the force also acting on the crank Counterforce to the force absorbed by the blocking agent.
  • the parallelogram of forces can be selected by a suitable choice of the point of attack and the direction depending on the external force and the force absorbed by the blocking agent be that a line through the intersection of these two forces or their extensions and the axis of rotation of the cylinder almost and ideally exactly congruent Bending load runs. This means that the resulting force, namely the preload force, rectified to the bending load and is therefore suitable for their compensation.
  • the gear is preferably designed as a push crank with blocking means that can be subjected to tensile loads
  • the gear must only be ensured that the Counterforce exerted by the blocking agent on the crank, i.e. the line through the Articulation of the blocking agent on the machine frame and the articulation of the blocking agent on the crank, has a component in the direction of the preload to be applied.
  • the size of the preload can be easily increased or decreased external force exerted by the drive on the crank adapted to the circumstances to adjust. In principle, no other changes are necessary. It can also be used each pin of a cylinder has different prestressing forces and is asymmetrical Bending loads can be compensated.
  • the blocking means can be formed by a chain, a rope or the like.
  • a tab is preferably used, which has one end on Machine frame hinged and with its other end on the crank to his Blocked position is movably guided.
  • a blocking means is provided in accordance with different bending loads. In every Only one of the blocking means is claimed in the cylinder position, while the or the others remain without strength.
  • the parallelogram of forces explained above becomes by means of the blocking means provided for the respective cylinder position. The External force on the crank is the same in all cases.
  • Another advantageous embodiment of the invention is the machine side Articulation of the blocking means movable in relation to the machine frame and in each or lockable in predetermined positions.
  • this creates an additional Fine adjustment of the resulting preload force for each operating state enables. This is, for example, with different plate assignments of the plate or forme cylinder an advantage.
  • the crank is preferably formed by a disk on which an eccentric to the Cylinder pin arranged bolts for a rotary linkage of the drive.
  • the disc can be used for each tension member be provided with a guide in which, for example, one on the respective tension member attached bolt is slidably guided and for the purpose of blocking the disc against a kind of attack is going on.
  • a guide in which, for example, one on the respective tension member attached bolt is slidably guided and for the purpose of blocking the disc against a kind of attack is going on.
  • guides is one designed as a disc Drive crank a wide angular range of the disc available. This can be special then be advantageous if due to different spatial relationships with different Machines the tension members relative to the location of the articulation of the drive on the The drive crank must be arranged differently from machine to machine.
  • the device according to the invention preferably has a motor-driven one pull and push actuable screw gear or a double-acting Hydraulic cylinder on, with a lever rod along its longitudinal axis in both Directions can be driven. This allows the direction of the preload in an even wider range.
  • the adjustable range can be wider be increased in that the lever rod, possibly together with the drive, by one to Cylinder pin parallel axis is tiltable.
  • lever rod between its articulation on the drive crank and its drive end a spring element for measuring that of the lever rod order transmitted force.
  • a measurement signal for the recorded by the spring element Force can be used to regulate the motor by means of a suitable motor control.
  • Fig. 1 shows a cylinder arrangement of a printing unit with a steel cylinder 3, two Rubber cylinders 1 and 2, a forme cylinder 4 for the rubber cylinder 1 and one Forme cylinder 5 for the blanket cylinder 2.
  • the blanket cylinders 1 and 2 are reversible. In a first pressure position A they roll on the steel cylinder 3 and in a second Pressure position B rolls on each other.
  • a piston rod 9 of the working cylinder 8 carries at its end a coupling piece 10, which by means of a pivot bearing 11 a lever 12 is articulated. 7, the lever 12 is rigidly seated an eccentric sleeve 7.
  • Another, also rigidly connected to the eccentric sleeve 7 Lever 13 carries a bolt 14 which is adjustable by means of an adjusting screw 15 and in a machine frame 6 between two stop positions A1, B1 for the two pressure positions A and B is performed.
  • Each rubber cylinder 1 and 2 is with a cylinder pin 17 (Fig. 4, 7) in such an eccentric bushing 7 and thus describes at Rotation of the eccentric bushing 7 about its axis of rotation 19, which is relative to the axis of rotation 1.1 or 2.1 of the each rubber cylinder 1 or 2 runs eccentrically, a circular section path 20 the axis of rotation 19 of the eccentric sleeve 7.
  • the blanket cylinder 1 is either pressed against its rubber counter cylinder 2 or the steel cylinder 3. In its middle position C it is switched off from both counter cylinders 2, 3 and from the corresponding forme cylinder 5.
  • the deflection f of the cylinder 2 is shown, which is between its two machine frame-side bearings 22 as a result of rolling on a corresponding counter cylinder 1 or 3 is under a line load Q.
  • the deflection f has the known undesirably pronounced course.
  • a reduction in the deflection f can, as shown in FIG.
  • Reinforcement of the cylinder bearing 22 can be achieved by using the two bearings as multi-roller bearings 22.1 are trained with a defined game. Due to this extension of the bearings 22.1 in A certain reduction in the deflection can already be achieved in the cylinder axis direction.
  • FIG 4 shows how the deflection f of the cylinder 2 loaded with the line load Q by the application of a counterforce PV 1 to a shaft journal 18 projecting beyond the bearing 22 and a counterforce PV 2 to the opposite shaft journal projecting beyond the other bearing 22 18 is largely reduced.
  • two equally large and rectified forces PV 1 and PV 2 are applied symmetrically to the two shaft journals 18.
  • the deflection f therefore also runs symmetrically and maintains its greatest value in the middle between the two bearings 22.
  • the opposing forces PV 1 and PV 2 can be changed both in their direction and in their absolute size, so that differently extending line loads Q can be adequately counteracted.
  • the line load Q formed from the unwinding and the dead weight of the cylinder changes its direction and its size, for example, when reversing between the two pressure positions A and B.
  • FIG. 5 to 7 show an arrangement for applying a biasing force, which in Adaptation to the different pressure positions A and B in their direction and in Adaptation to line loads Q, which, for example, also depends on the cylinder lengths can differ in size. can be changed.
  • a biasing force which in Adaptation to the different pressure positions A and B in their direction and in Adaptation to line loads Q, which, for example, also depends on the cylinder lengths can differ in size. can be changed.
  • Fig. 5 the blanket cylinder 2 is in position A, i.e. he rolls on the Steel cylinder 3 and the associated forme cylinder 5, causing the rubber cylinder 2 a line load resulting from both unwinds and its own weight acts.
  • a preload force acting in the same direction is used 37 on the two projecting beyond the bearings 22 in the machine frame wall 6 Pin ends 18 of the cylinder pin 17 of the blanket cylinder 2 applied.
  • the eccentrically arranged bolt 32 is attached in a region of the disk 23 which through the connecting lines from the axis of rotation 2.1 of the blanket cylinder 2 to the latter Lines of engagement E with the two cylinders 3 and 5, on which it rolls, is limited and protrudes into the space between the steel cylinder 3 and the forme cylinder 5.
  • the direction of movement the lever rod 31 can be changed by reversing the motor 26.
  • the transmission of the exemplary embodiment has a rod-shaped one first and a rod-shaped second tab 38 and 46, which are preferably rigid bodies are.
  • the first tab 38 is at one end in a first frame on the machine frame side 43 by means of a joint 39 and the second tab 46 is at one end in its own machine frame side second bracket 44 fastened by means of a joint 45.
  • the linkage of the two tabs on the machine frame 6 allows the tabs to be rotated around Rotation axis 2.1 of the blanket cylinder 2 parallel axes.
  • the Joints 39 and 45 formed by pivot bearings.
  • first tab 38 At the free end of the first tab 38 a first bolt 40 is seated, and at the free end of the second tab 46 sits a second bolt 47.
  • the two tabs 38 and 46 are over the bolts 40 and 47 guided on the disk 23. They limit the freedom of rotation of these Disk 23, one tab in each direction of rotation.
  • the disk 23 has two guides 42 and 48 formed as recesses, which are in the form of circular sections along a common circular arc 34 about the axis of rotation 2.1 of the Rubber cylinder 2 run. In the exemplary embodiment lies on the same circular arc also the eccentrically arranged bolt 32.
  • the recesses 42 and 48 have approximately a width that corresponds to the diameter of the two bolts 40 and 47 and are extended in the eccentrically arranged bolt 32 beyond the cylinder axis of rotation 2.1 Area of the disk 23.
  • the pin 40 is the first Tab 38 and in the second guide 48, the bolt 47 of the second tab 46 is sliding added.
  • the two bolts 40 and 47 point in the direction of the axis of rotation 2.1 of the Rubber cylinder 2 and protrude through their respective recess.
  • the disk 23 can thus be rotated until one of the two guides 42 or 48 with their trailing end against the sliding in it received bolt 40 or 47 comes to rest, the corresponding tab 38th or 46 is tensioned and the rotation is blocked.
  • the two tabs are on Machine frame 6 and articulated on the disk 23 so that they only along their respective Connecting line of these two articulations can be claimed on the pure train.
  • the linkage of the lever rod 31 to the disk 23 and the two linkages 39, 40 and 45, 47 of the two tabs 38 and 46 are each arranged so that the Blocking the disk 23 creates a parallelogram of forces, the resulting one Force vector to the common axis of rotation 2.1 of the blanket cylinder 2 and the disk 23 is directed and has the same direction as the resulting line load Q.
  • the disk 23 and the lever rod 31 comprising crank mechanism of the embodiment and the two on both sides, d. H. on the machine frame and on the disk 23, rotatable hinged tabs 38 and 46 is already achieved that the resulting force vector always points to the axis of rotation of the cylinder.
  • the second recess 48 plays in the compensation of the in the printing position A. acting line load does not matter. It only has to go as far along the circular arc 34 extend that the bolt 47 seated on the second tab 46 is not non-positively can come into contact with it.
  • the first guide 42 plays no role. She also has to However, extend along the arc 34 so far that the one on the first tab 38 seated bolts 40 do not come to rest against their trailing end and can inhibit the disc 23.
  • the disk 23 forms a push crank with each of the two tabs 38 and 46. One per these two thrust cranks become independent in one of the two pressure positions A and B. operated by the other.
  • An electric motor is used as the motor 26, which has a gear 27, 28 and a thread 27.1 the lever rod 31 drives.
  • the entire drive, in particular the lever rod 31, is around a to the axis of rotation 2.1 of the rubber cylinder 2 parallel tilt axis 24 rotatable on one machine frame side support 25 stored.
  • the lever rod 31 can be a Rotation of the disk 23 between the stop positions for the two pressure positions follow A and B more easily.
  • the lever rod 31 has a sleeve part 29 in which a spring element 30 is seated, which exerts the force on the eccentrically on the disk 23 attached bolt 32 transmits.
  • the force 36 thus absorbed by the spring element 30 or 56 or the size of the deflection is attached to the sleeve part 29 by means of a Liner potentiometers 33 measured and in a motor control with the force setpoint compared and kept in register with this target value or brought.
  • the Sleeve part 29 with the spring element 30 is effective in the pulling and pushing directions preloaded spring cartridge.
  • the engine control essentially has a computer 51 with a controller and a PC Service device 52, which are connected to a machine control center 50. So from Control station 50 from a preset force on the pin end 18 of the blanket cylinder 2 applied, kept regulated or, if necessary, changed manually at the control center, in order, for example, to be able to meet non-preset operating states. At a new machine settings made at the control center 50, for example a change the pressure position of the rubber cylinder 2, the magnitude of the external force 36 or 56 changed to the disk 23 according to a programming also fully automatically become.
  • FIG. 8 shows a tab 38.1 which is movable in relation to the machine frame 6 is arranged.
  • Your machine-side linkage 39.1 is in the trestle 43.1 along the horizontal line L slidable and in any desired position between two Lockable end positions.
  • This movable tab 38.1 makes it possible in the respective operating position of cylinder 2 (here: pressure position A), a fine adjustment of the Preload 37 or 37 'to make. This is advantageous, for example, if Different bending stresses can occur in a pressure position, as is the case differently occupied plate cylinder 5 may be the case.
  • Locking positions of the linkage 39.1 can also be predefined, namely according to the conceivable different plate assignments.
  • tab 38 to the different operating conditions, such as shown in Figures 5 and 6 to meet.
  • the tab 38.1 can be increased by one Middle position, which is approximately perpendicular below the axis of rotation 2.1 of the blanket cylinder 2 may be arranged to be movable.
  • the recess 42.1 is to be designed accordingly and position.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Rotary Presses (AREA)

Claims (12)

  1. Procédé pour influer sur le profil de courbure d'un cylindre d'une machine d'impression rotative dans lequel :
    a)au moyen d'une force (36, 56) extérieure qui
    peut être modifiée et qui est appliquée par un dispositif d'entraínement, on applique, sur un tourillon (17) de cylindre à une certaine distance d'un palier (2) de cylindre du côté de la machine, une force (37, 57) de précontrainte qui produit un couple de flexion autour d'un axe transversal à un axe (2.1) de rotation du cylindre, et
    b)le couple de flexion sert à réduire la flèche du cylindre (2) due à des charges de flexion en des points différents du cylindre (1.2)
    caractérisé en ce que
    c) la force (37, 57) de précontrainte est formée, par une transmission qui se bloque en les positions différentes du cylindre respectivement dans une autre position de transmission, sous la forme d'une force résultante d'un parallélogramme de forces qui est tendu par la force (36, 56) extérieure et par une force (35, 55) de réaction formée par la transmission.
  2. Dispositif pour influer sur le profil de flexion d'un cylindre d'une machine d'impression rotative par application d'un couple de rotation par rapport à un axe transversal à un axe (2.1) de rotation du cylindre au moyen :
    a) d'une manivelle (23) qui est montée à rotation, à une certaine distance d'un palier (22) de cylindre du côté de la machine sur un tourillon (17) de cylindre, sur un coussinet (22.2) de pivotement, et
    b) un dispositif (26, 31) d'entraínement par lequel il peut être appliqué une force (36, 56) extérieure variable à la manivelle (23) et en ce que
    c) la force (36, 56) extérieure attaque de manière excentrée par rapport au coussinet (22.2) de pivotement de la manivelle (23)
    caractérisé en ce que
    d) il est prévu au moins un moyen (38, 46) de blocage, par lequel la manivelle (23) peut être bloquée par rapport au cylindre (2) à l'encontre d'une rotation provoquée par la force (36, 57) extérieure, en au moins deux positions angulaires de butée dans lesquelles
    e) il est appliqué sur le coussinet (22.2) de pivotement de la manivelle (23) respectivement une force (35, 55) de réaction qui ensemble avec la force (36, 56) extérieure forme un parallélogramme de forces dont la force résultante s'oppose à une flèche du cylindre (2) due à une charge (Q) de flexion.
  3. Dispositif suivant la revendication 2, caractérisé en ce que pour des positions (A, B) d'impressions différentes du cylindre (2) avec des charges (Q) de flexions différentes il est prévu un seul ou respectivement un moyen (38, 46) de blocage, qui peut être monté mobile par rapport à un bâti (6) de la machine.
  4. Dispositif suivant la revendication 2 ou 3, caractérisé en ce que la manivelle (23) est formée par un disque ayant un axe (32) monté excentré par rapport au tourillon (17) du cylindre (2) et destiné à l'articulation du dispositif (26, 31) d'entraínement sur la manivelle (23).
  5. Dispositif suivant la revendication 4, caractérisé en ce que la manivelle (23) comporte un guidage (42, 48) dans lequel le moyen (38,46) de blocage constitué de manière rigide est guidé pour une rotation de la manivelle (23) sous l'effet de la force (36, 56) extérieure jusqu'à une position de butée bloquant toute rotation supplémentaire.
  6. Dispositif suivant la revendication 5, caractérisé en ce que la manivelle (23) comporte pour chaque moyen (38, 46) de blocage un guidage (42, 48).
  7. Dispositif suivant l'une des revendications 2 à 6, caractérisé en ce que le dispositif d'entraínement comporte un moteur (26) ou un vérin hydraulique ainsi qu'une barre (31) de levier qui peut être déplacée le long de son axe longitudinal par le moteur (26) et qui est articulée à la manivelle (23).
  8. Dispositif suivant la revendication 7, caractérisé en ce que la barre (31) de levier peut basculer autour d'un axe (24) parallèle au tourillon (17) du cylindre (2).
  9. Dispositif suivant la revendication 7 ou 8, caractérisé en ce que la barre (31) de levier comporte, entre son articulation à la manivelle (23) et son extrémité du côté du moteur, une pièce (29) en forme de douille dans laquelle est disposé un élément (30) élastique de mesure de la force transmise par la barre (31) de levier.
  10. Dispositif suivant la revendication 9, caractérisé en ce qu'un signal de mesure de la force absorbée par l'élément (30) élastique sert à la régulation du moteur (26) au moyen d'un ordinateur (51).
  11. Cylindre d'une machine d'impression rotative, caractérisé en ce qu'il est prévu respectivement un dispositif suivant l'une des revendications 2 à 10, sur les deux tourillons (17) du cylindre (2).
  12. Cylindre suivant la revendication 11, caractérisé en ce que les deux dispositifs peuvent être actionnés indépendamment l'un de l'autre.
EP95810333A 1994-06-10 1995-05-19 Installation pour réduire la flexion d'un cylindre dans des machines d'impression rotatives Expired - Lifetime EP0686502B1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4420355A DE4420355C2 (de) 1994-06-10 1994-06-10 Verfahren und Vorrichtung zur Beeinflussung des Biegeverlaufs eines Zylinders einer Rotationsdruckmaschine
DE4420355 1994-06-10

Publications (3)

Publication Number Publication Date
EP0686502A2 EP0686502A2 (fr) 1995-12-13
EP0686502A3 EP0686502A3 (fr) 1996-11-27
EP0686502B1 true EP0686502B1 (fr) 2001-04-04

Family

ID=6520305

Family Applications (1)

Application Number Title Priority Date Filing Date
EP95810333A Expired - Lifetime EP0686502B1 (fr) 1994-06-10 1995-05-19 Installation pour réduire la flexion d'un cylindre dans des machines d'impression rotatives

Country Status (3)

Country Link
EP (1) EP0686502B1 (fr)
DE (2) DE4420355C2 (fr)
FI (1) FI952788A (fr)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE19636184C2 (de) 1996-09-06 2002-04-04 Winfried Poeppinghaus Verfahren und Vorrichtung zum selbständigen Verändern der Durchbiegung einer Welle, Achse oder eines anderen Trägers
FR2827544B1 (fr) 2001-07-23 2003-10-17 Goss Systemes Graphiques Nante Presse offset a montage de cylindre ameliore
DE10335758C5 (de) * 2003-08-05 2015-12-03 Manroland Web Systems Gmbh Verfahren und Druckwerk zur Beeinflussung der lateralen Bahnspreizung insbesondere an Rotationsdruckmaschinen

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE753695C (de) * 1940-04-02 1952-11-24 Faber & Schleicher A G Vorrichtung zum An- und Abstellen des Gummizylinders einer Dreizylinder-Rotationsgummidruckmaschine
DE1253282B (de) * 1962-08-16 1967-11-02 Goebel Gmbh Maschf Druckwerk mit beiderseits des Form- und Druckzylinders auf deren Wellen angeordnetenStuetzringen
DE2033515A1 (fr) * 1970-07-07 1972-06-08
DE2802153C2 (de) * 1978-01-19 1986-08-07 M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8900 Augsburg Schmitzringanordnung
DE2926570A1 (de) * 1979-06-30 1981-01-22 Koenig & Bauer Ag Anordnung zum gegenseitigen abstuetzen von miteinander in beruehrung stehenden zylindern eines druckwerkes
CH648238A5 (de) * 1979-10-09 1985-03-15 Roland Man Druckmasch Vorrichtung zum durchbiegen einer druckwalze einer rotationsdruckmaschine.
DE2940879A1 (de) * 1979-10-09 1981-04-23 M.A.N.- Roland Druckmaschinen AG, 6050 Offenbach Vorrichtung zum biegen einer druckwalze in einer rotationsdruckmaschine
DE3707996C1 (en) * 1987-03-12 1988-10-20 Roland Man Druckmasch Device for influencing the pressure of the bearing ring
DD267463B5 (de) * 1987-11-16 1993-09-09 Kba Planeta Ag Lagerung fuer zylinder und trommeln

Also Published As

Publication number Publication date
EP0686502A3 (fr) 1996-11-27
FI952788A0 (fi) 1995-06-07
DE4420355A1 (de) 1995-12-14
DE59509142D1 (de) 2001-05-10
FI952788A (fi) 1995-12-11
EP0686502A2 (fr) 1995-12-13
DE4420355C2 (de) 1999-09-23

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