EP0686502A2 - 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

Info

Publication number: EP0686502A2
Authority: EP; European Patent Office
Prior art keywords: cylinder; force; drive; drive crank; machine frame
Prior art date: 1994-06-10
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.): Granted

Application number

EP95810333A

Other languages

German (de)

English (en)

Other versions

EP0686502B1 (fr

EP0686502A3 (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.)

1994-06-10

Filing date

1995-05-19

Publication date

1995-12-13

1995-05-19 Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG

1995-12-13 Publication of EP0686502A2 publication Critical patent/EP0686502A2/fr

1996-11-27 Publication of EP0686502A3 publication Critical patent/EP0686502A3/fr

2001-04-04 Application granted granted Critical

2001-04-04 Publication of EP0686502B1 publication Critical patent/EP0686502B1/fr

2015-05-19 Anticipated expiration legal-status Critical

Status 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
- 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 device for reducing cylinder deflection in rotary printing presses.
support rings for mutually supporting cylinders rolling on each other the use of support rings, in particular bearer rings, is known from the prior art.
the support rings are usually arranged on the cylinder shaft between the cylinder and its bearing, ie within the cylinder bearings in the machine frame.
a support ring arrangement with which the distance between the cylinders rolling on one another can be adjusted is known, for example, from CH-PS 402 895. However, this does not counteract the bending load resulting from the mutual unwinding.
support rings known from DE 29 26 570 A1 on both sides of the cylinder, both inside and outside the machine frame, the reduction of the deflection is not intended.
a cylinder bearing designed as a bracing bearing, which is arranged eccentrically adjustable in the direction of the bearing force occurring in the operating state.
the bracing bearing is located on a cylinder journal protruding beyond the machine frame-side bearing of the cylinder. Adaptation of the bracing to different operating states of the cylinder is not taught, however.
This bracing bearing is in particular not designed to counteract a change in the direction of the line loads acting on the cylinder, as is caused by the change in the operating states of the cylinder.
reversible pressure units can assume different operating states, in which the reversal always leads to a change in the direction of the bending load acting on the reversed cylinder.
the object of the invention is to provide a cylinder pretensioning device with which a cylinder pretensioning force can be automatically adjusted in adaptation to different operating states of the cylinder.
a device for reducing the deflection of a cylinder under a bending load, in particular a blanket cylinder of a rotary printing press, with which a biasing force counteracting the bending load can be applied has, according to the invention, a drive for applying a variable driving force, which is also referred to below as external force, and a gearbox with which the driving force is converted into the required pretensioning force, which counteracts the bending loads prevailing in the respective operating states of the cylinder.
the application of an external force by means of a specially provided drive basically opens up the possibility of flexibly adapting the pretensioning force to every operating state of a cylinder.
the external force can be changed by controlling the drive. Manual adjustment on site is not necessary. Setting from a machine control center is possible. If necessary, the driving force can also be changed during operation.
the cylinder to be preloaded is reversed, for example from a rubber / rubber production to a rubber / steel production and vice versa, the direction of the bending load acting on the cylinder changes considerably, while the position of the cylinder in space is changed only slightly.
the prestressing force can be applied to the cylinder journal at a location between or outside of the machine-side cylinder bearing either on one or both cylinder journals.
the transmission is designed according to the invention as a push crank.
it has a drive crank which is rotatably mounted on the cylinder journal and on which the external force applied by the drive acts.
a tension member that can only be loaded under tension is articulated on the one hand on the drive crank and on the other hand on the machine frame.
the drive crank can be locked in a predetermined angular position.
a pressure member can also be used for force deflection. A force parallelogram is thus formed between the external force exerted by the drive on the crank and the counterforce also acting on the drive crank to the tensile force absorbed by the tension member.
the force parallelogram can be formed by a suitable choice of the point of application and the direction depending on the external force and the tensile force so that a line through the intersection of these two forces or their extensions and the axis of rotation of the cylinder runs almost and ideally exactly congruent with the bending load. This means that the resulting force, namely the pretensioning force, is rectified for the bending load and is therefore suitable for its compensation.
this transmission which is preferably designed as a thrust crank with a tension member
the arrangement of the tension member simply has to ensure that the counterforce exerted by the tension member on the crank, i.e. the line through the articulation of the tension member on the machine frame and the articulation of the tension member on the Drive crank, has a component in the direction of the biasing force to be applied.
the magnitude of the pretensioning force can be adjusted to suit the circumstances simply by increasing or decreasing the external force exerted by the drive on the crank. In principle, no other changes are necessary. Different prestressing forces can also be applied to each pin of a cylinder and asymmetrical bending loads can be compensated for.
the tension member can be formed by a chain, a rope or the like.
a tab is preferably used which is articulated at one end to the machine frame and is movably guided at its other end on the drive crank up to its blocking position.
a tension member is provided for different cylinder positions with correspondingly different bending loads. In each cylinder position, only one of the tension members is stressed, while the other or the other remain free of forces.
the above tert parallelogram is formed by means of the tension member provided for the respective cylinder position. The point of application of the external force on the drive crank is the same in all cases.
a likewise advantageous embodiment of the invention consists in arranging the articulation of the tab so that it can move in relation to the machine frame and can be locked in any or in predetermined positions. On the one hand, this enables an additional fine adjustment of the resulting pretensioning force for each operating state. This is advantageous, for example, when the plate or forme cylinders have different plate assignments. On the other hand, it becomes possible to manage with different operating states with a single tab with a corresponding arrangement of the position of the blocking positions on the drive crank.
the drive crank is preferably formed by a disk on which a bolt, which is arranged eccentrically with respect to the cylinder journal, is seated for rotating the drive.
a disc as a power transmission link opens up the greatest possible freedom in the choice of the location for the articulation of the drive and the location for the articulation of the tension member or members.
the disk can be provided with a guide for each tension member, in which, for example, a bolt fastened to the respective tension member is guided and runs against a type of stop for the purpose of blocking the disk.
a wide angular range of the disk is available for such guides in a drive crank designed as a disk. This can be particularly advantageous if, due to different spatial conditions in different machines, the tension members are to be arranged differently from machine to machine relative to the location of the articulation of the drive on the drive crank.
the device according to the invention preferably has a motor-driven pull and push actuated screw gear or a double-acting hydraulic cylinder with which a lever rod can be driven in both directions along its longitudinal axis.
the direction of the pretensioning force can be set in an even larger range.
the adjustable range can be increased further in that the lever rod, possibly together with the drive, can be tilted about an axis parallel to the cylinder journal.
a measurement signal for the force absorbed by the spring element can be used to regulate the motor by means of a suitable motor controller.
FIG. 1 shows a cylinder arrangement of a printing unit with a steel cylinder 3, two blanket cylinders 1 and 2, a forme cylinder 4 for the blanket cylinder 1 and a forme cylinder 5 for the blanket cylinder 2.
the blanket cylinders 1 and 2 are reversible. In a first position A they roll on the steel cylinder 3 and in a second position B they roll on each other.
a piston rod 9 of the working cylinder 8 carries at its end a coupling piece 10 which is articulated on a lever 12 by means of a pivot bearing 11.
the lever 12 sits rigidly on an eccentric bushing 7.
Another lever 13, also rigidly connected to the eccentric bushing 7, carries a bolt 14 which is adjustable by means of an adjusting screw 15 and in a machine frame wall 6 between two Stop positions A1, B1 for the two cylinder positions A and B is performed.
the center point of the bearing 11 moves along the dash-dotted circular section line 21 about the axis of rotation 19 of the eccentric bushing 7 between the two stop positions A1, B1 specified by the bolt 14.
Each rubber cylinder 1 and 2 is rotatably supported with a shaft journal section 17 (FIGS. 4, 7) in such an eccentric bushing 7 and thus describes when the eccentric bushing 7 rotates about its axis of rotation 19, which corresponds to the axis of rotation 1.1 or 2.1 of the respective rubber cylinder 1 or 2 runs eccentrically, a circular section path 20 about the axis of rotation 19 of the eccentric bushing 7.
the blanket cylinder 1 is thereby pressed either against its rubber counter cylinder 2 or the steel cylinder 3. In its center position C is turned off by both counter cylinders 2, 3 and by the corresponding forme cylinder 5.
the deflection f has the known, undesirably pronounced profile.
a reduction in the deflection f can, as shown in FIG. 3, be achieved by reinforcing the cylinder bearings 22 by designing the two bearings 22.1 as multi-roller bearings with a defined play. This stretching of the bearings 22.1 in the cylinder axis direction can already achieve a certain reduction in the deflection.
Fig. 4 shows how the deflection f of the cylinder load Q with the application of a counterforce PV1 by applying a counterforce PV1 on a protruding through a bearing 22 shaft journal 18 and a counterforce PV2 on the projecting over the other bearing 22, opposite shaft journal 18 largely is 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 weight of the cylinder changes its direction and its size, for example, when reversing between the two pressure positions A and B.
FIGS. 5 to 7 show an arrangement for applying a biasing force, which can be changed in adaptation to the different pressure positions A and B in their direction and in adaptation to line loads Q, which can also differ in size, for example, depending on the cylinder lengths.
a biasing force which can be changed in adaptation to the different pressure positions A and B in their direction and in adaptation to line loads Q, which can also differ in size, for example, depending on the cylinder lengths.
Fig. 5 the blanket cylinder 2 is in position A, i.e. it rolls on the steel cylinder 3 and the associated forme cylinder 5, as a result of which a line load resulting from both unwinds and its own weight acts on the rubber cylinder 2.
a force 37 acting in the same direction is applied to the two journal ends 18 of the shaft journals 17 of the rubber cylinder 2 which protrude beyond the bearings 22 in the machine frame wall 6.
a disk 23 is rotatably supported on the pin ends 18 on both sides of the rubber cylinder 2 by means of bearings 22.2.
the disk 23 sits further outside on the cylinder journal than a drive gear 16 of the cylinder 2.
a lever rod 31 is pivotally articulated about the pin 32 on a bolt 32 which is seated eccentrically to the cylinder axis of rotation 2.1 and points in the cylinder axis direction.
the lever rod 31 is driven back and forth via a gear by a drive motor 26, which is located on the side of the rubber cylinder 2 facing away from the rubber cylinder 1.
the direction of movement of the lever rod 31 extends transversely to the cylinder axis of rotation 2.1.
the disk 23 forms a crank which, under the action of the lever rod 31, rotates about the cylinder axis of rotation 2.1.
the eccentrically arranged bolt 32 is attached in a region of the disk 23 which is delimited by the connecting lines from the axis of rotation 2.1 of the rubber cylinder 2 to its lines of engagement E with the two cylinders 3 and 5 on which it rolls is and protrudes into the space between the steel cylinder 3 and the forme cylinder 5.
the direction of movement of the lever rod 31 can be changed by reversing the drive 26.
the transmission of the exemplary embodiment has a rod-shaped first and a rod-shaped second bracket 38 and 46, which are preferably rigid bodies.
the first bracket 38 is fastened at one end in a first frame 43 on the machine frame side by means of a joint 39 and the second bracket 46 is fastened at one end in a second frame 44 on the machine frame side by means of a joint 45.
the articulation of the two tabs on the machine frame 6 allows the tabs to be rotated about axes parallel to the cylinder axis of rotation 2.1.
the joints 39 and 45 are formed by rotary bearings.
a first bolt 40 sits at the free end of the first bracket 38 and a second bolt 47 sits at the free end of the second bracket 46.
the two brackets 38 and 46 are guided on the disk 23 via bolts 40 and 47. They limit the freedom of rotation of this disk 23, specifically one tab in one direction of rotation.
the disk 23 has two guides 42 and 48 designed as recesses, which run in the form of circular sections along a common circular arc 34 about the axis of rotation 2.1 of the rubber cylinder 2.
the eccentrically arranged bolt 32 also lies on the same circular arc.
the recesses 42 and 48 have approximately a width which corresponds to the diameter of the two bolts 40 and 47 and are located in the eccentrically arranged bolt 32 via the cylinder axis of rotation 2.1 extended region of the disk 23.
the bolt 40 of the first bracket 38 and in the second recess 48 the bolt 47 of the second bracket 46 is slidably received.
the two bolts 40 and 47 point in the direction of the cylinder axis of rotation 2.1 and protrude through their respective recesses.
the disk 23 can thus be rotated until one of the two recesses 42 or 48, with its trailing end, comes to lie against the bolt 40 or 47 slidably received in it, the corresponding tab 38 or 46 is subjected to tension and blocked the rotation.
the two brackets are articulated on the machine frame 6 and on the disk 23 in such a way that they can only be subjected to pure tension along their respective connecting line from these two articulations.
the articulation of the lever rod 31 to the disk 23 and the two articulations 39, 40 and 45, 47 of the two tabs 38 and 46 are each arranged in such a way that when the disk 23 is blocked, a parallelogram of forces is created, the resulting force vector of the disk about the axis of rotation 2.1 23 is directed and has the same direction as the resulting line load Q.
crank mechanism 23, 31 of the embodiment and the two on both sides, d. H. on the machine frame and on the disk 23, rotatably articulated brackets 38 and 46 it is already achieved that the resulting force vector always points to the cylinder axis of rotation.
the intersection of the forces thus predetermined in their directions is selected such that the Resulting force starting from the intersection and pointing to the cylinder axis of rotation in the direction of the resulting line load predetermined by the machine.
the compressive force 36 also acting on the bolt 32 forms with this counterforce 35 a resultant force 37 which is directed from the intersection towards the cylinder axis of rotation 2.1.
the tab 38 can only be subjected to tension along the connecting line of its two articulations, the bolts 39 and 40, and acts like a rope fastened at 39, which by the force 36 over the intersection of the forces 36 and 35, in the present case therefore the eccentrically arranged bolt 32 is tensioned and pushes this bolt or the imaginary intersection of forces in the direction of the axis of rotation 2.1.
the resulting force 37 is therefore always in the connecting line between the point of force intersection and the cylinder axis of rotation 2.1. As described above, this point of intersection is structurally determined, so that only the size of the resulting force 37 can be changed by adjusting the driving force 36 according to size or direction or a combined setting of size and direction.
the second recess 48 plays no role in the compensation of the line load acting in the position A. It only has to extend along the circular arc 34 to such an extent that the bolt 47 sitting on the second tab 46 cannot come into contact with it in a force-fitting manner.
the blanket cylinder 2 is in the printing position B. It thus rolls on the opposite blanket cylinder 1 and its own forme cylinder 5. This changes in particular the direction of the resultant line load, which now comes from these two rolling cylinders 1 and 5 and further again is exerted on this rubber cylinder 2 by the dead weight component of the rubber cylinder 2. The dead weight component now even increases the line load to be balanced.
the resulting force 57 acting on the cylinder axis of rotation 2.1 can be set in the desired direction and size in the same way as in the cylinder position A. .
the first recess 42 plays no role. However, it too must extend along the circular arc 34 to such an extent that the bolt 40 seated on the first tab 38 does not come to rest against its trailing end and can thereby inhibit the disk 23.
the disk 23 forms a push crank with each of the two tabs 38 and 46.
One of these two thrust cranks is actuated in one of the two cylinder positions A and B independently of the other.
An electric motor serves as the drive motor 26 and drives the lever rod 31 via a gear 27, 28 and a thread 27.1.
the entire drive, in particular the lever rod 31, is rotatably mounted about a tilt axis 24 parallel to the cylinder axis of rotation 2.1 on a support 25 on the machine frame side. As a result, the lever rod 31 can more easily follow a rotation of the disk 23 between the stop positions for the two cylinder positions A and B.
the lever rod 31 has a sleeve part 29 in which a spring element 30 is seated, which exerts the force from the drive on the bolt mounted eccentrically on the disk 23 32 transmits.
the force 36 or 56 absorbed in this way by the spring element 30 or the size of the deflection is measured by means of a liner potentiometer 33 attached to the sleeve part 29 and compared in an engine control with the desired force value and kept in register with this desired value.
the sleeve part 29 with the spring element 30 is a prestressed spring cartridge that is effective in the pulling and pushing directions.
the engine control essentially has a computer 51 with a controller and a PC as a service device 52, which are connected to a machine control center 50.
a preset force can be applied from the control station 50 to the pin end 18 of the blanket cylinder 2, held in a controlled manner or, if necessary, changed manually at the control station, for example in order to be able to counter non-preset operating states.
the magnitude of the external force 36 or 56 on the disk 23 can also be changed fully automatically in accordance with programming.
FIG. 8 shows a tab 38.1 which is movably arranged in relation to the machine frame 6.
Your machine-side linkage 39.1 can be moved in the block 43.1 along the horizontal line L and between in any desired position two end positions can be locked.
This movable tab 38.1 makes it possible to make a fine adjustment of the pretensioning force 37 or 37 'in the respective operating position of the cylinder 2 (here: position A). This is advantageous, for example, if different bending loads can occur in a printing position, as can be the case due to differently loaded plate cylinders 5.
Locking positions of the articulation 39.1 can also be predefined, namely according to the conceivable different plate assignments.
a single, movably arranged tab 38 is also sufficient to counter the different operating states, as are shown, for example, in FIGS. 5 and 6.
the tab 38.1 can be arranged to be movable about a central position, which can lie approximately perpendicularly below the cylinder axis of rotation 2.1.
the recess 42.1 is to be designed and positioned accordingly.

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

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
DE4420355		1994-06-10
DE4420355A DE4420355C2 (de)	1994-06-10	1994-06-10	Verfahren und Vorrichtung zur Beeinflussung des Biegeverlaufs eines Zylinders einer Rotationsdruckmaschine

Publications (3)

Publication Number	Publication Date
EP0686502A2 true EP0686502A2 (fr)	1995-12-13
EP0686502A3 EP0686502A3 (fr)	1996-11-27
EP0686502B1 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)	FI952788L (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO1998010199A1 (fr) *	1996-09-06	1998-03-12	Poeppinghaus Winfried	Procede et dispositif pour modifier la flexion d'un arbre, d'un axe ou d'un autre organe porteur
FR2827544A1 (fr) *	2001-07-23	2003-01-24	Goss Systemes Graphiques Nante	Presse offset a montage de cylindre ameliore

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
DE10335758C5 (de)	2003-08-05	2015-12-03	Manroland Web Systems Gmbh	Verfahren und Druckwerk zur Beeinflussung der lateralen Bahnspreizung insbesondere an Rotationsdruckmaschinen

Citations (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CH402895A (de)	1962-08-16	1965-11-30	Goebel Gmbh Maschf	Druckwerk mit beiderseits des Form- und des Druckzylinders auf deren Wellen angeordneten Stützringen
DE2802153A1 (de)	1978-01-19	1979-07-26	Maschf Augsburg Nuernberg Ag	Schmitzringverbindung zwischen zwei druckwerkszylindern
DE2926570A1 (de)	1979-06-30	1981-01-22	Koenig & Bauer Ag	Anordnung zum gegenseitigen abstuetzen von miteinander in beruehrung stehenden zylindern eines druckwerkes
DE3836972A1 (de)	1987-11-16	1989-05-24	Polygraph Leipzig	Lagerung fuer zylinder und trommeln

Family Cites Families (5)

* 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
DE2033515A1 (fr) *	1970-07-07	1972-06-08
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

1994
- 1994-06-10 DE DE4420355A patent/DE4420355C2/de not_active Expired - Fee Related
1995
- 1995-05-19 EP EP95810333A patent/EP0686502B1/fr not_active Expired - Lifetime
- 1995-05-19 DE DE59509142T patent/DE59509142D1/de not_active Expired - Fee Related
- 1995-06-07 FI FI952788A patent/FI952788L/fi unknown

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
CH402895A (de)	1962-08-16	1965-11-30	Goebel Gmbh Maschf	Druckwerk mit beiderseits des Form- und des Druckzylinders auf deren Wellen angeordneten Stützringen
DE2802153A1 (de)	1978-01-19	1979-07-26	Maschf Augsburg Nuernberg Ag	Schmitzringverbindung zwischen zwei druckwerkszylindern
DE2926570A1 (de)	1979-06-30	1981-01-22	Koenig & Bauer Ag	Anordnung zum gegenseitigen abstuetzen von miteinander in beruehrung stehenden zylindern eines druckwerkes
DE3836972A1 (de)	1987-11-16	1989-05-24	Polygraph Leipzig	Lagerung fuer zylinder und trommeln

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number	Priority date	Publication date	Assignee	Title
WO1998010199A1 (fr) *	1996-09-06	1998-03-12	Poeppinghaus Winfried	Procede et dispositif pour modifier la flexion d'un arbre, d'un axe ou d'un autre organe porteur
US6360982B1 (en)	1996-09-06	2002-03-26	Poeppinghaus Winfried	Method and device for correcting the bending of a shaft, an axle or another carrier
FR2827544A1 (fr) *	2001-07-23	2003-01-24	Goss Systemes Graphiques Nante	Presse offset a montage de cylindre ameliore
EP1279496A1 (fr) *	2001-07-23	2003-01-29	Goss Systemes Graphiques Nantes	Presse offset à montage de cylindre amélioré
US6834580B2 (en)	2001-07-23	2004-12-28	Goss Systemes Graphiques Nantes	Offset press with improved cylinder mounting

Also Published As

Publication number	Publication date
EP0686502B1 (fr)	2001-04-04
FI952788A7 (fi)	1995-12-11
DE59509142D1 (de)	2001-05-10
EP0686502A3 (fr)	1996-11-27
FI952788A0 (fi)	1995-06-07
DE4420355A1 (de)	1995-12-14
DE4420355C2 (de)	1999-09-23
FI952788L (fi)	1995-12-11

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