EP0480879A1 - Dispositif de réglage continu du mouvement de distribution axial de rouleaux distributeurs - Google Patents

Dispositif de réglage continu du mouvement de distribution axial de rouleaux distributeurs Download PDF

Info

Publication number
EP0480879A1
EP0480879A1 EP91810784A EP91810784A EP0480879A1 EP 0480879 A1 EP0480879 A1 EP 0480879A1 EP 91810784 A EP91810784 A EP 91810784A EP 91810784 A EP91810784 A EP 91810784A EP 0480879 A1 EP0480879 A1 EP 0480879A1
Authority
EP
European Patent Office
Prior art keywords
axis
eccentric
rotation
housing
eccentric pin
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.)
Granted
Application number
EP91810784A
Other languages
German (de)
English (en)
Other versions
EP0480879B2 (fr
EP0480879B1 (fr
Inventor
Andreas Miescher
Max Egger
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
Family has litigation
First worldwide family litigation filed litigation Critical https://patents.darts-ip.com/?family=6416188&utm_source=google_patent&utm_medium=platform_link&utm_campaign=public_patent_search&patent=EP0480879(A1) "Global patent litigation dataset” by Darts-ip is licensed under a Creative Commons Attribution 4.0 International License.
Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
Publication of EP0480879A1 publication Critical patent/EP0480879A1/fr
Application granted granted Critical
Publication of EP0480879B1 publication Critical patent/EP0480879B1/fr
Publication of EP0480879B2 publication Critical patent/EP0480879B2/fr
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F31/00—Inking arrangements or devices
    • B41F31/15—Devices for moving vibrator-rollers
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10—TECHNICAL SUBJECTS COVERED BY FORMER USPC
    • Y10S—TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y10S101/00—Printing
    • Y10S101/38—Means for axially reciprocating inking rollers

Definitions

  • the invention relates to a device on rotary printing presses for the continuous adjustment of the axial rubbing movement of friction rollers of inking and dampening units according to the preamble of claim 1.
  • Devices of this type are known.
  • DE-PS 38 14 927 shows such a device in which an eccentric pin is slidably arranged on a rotating body. The eccentric pin is displaced along a groove that runs perpendicular to the axis of rotation of the rotating body and through its center. A slot nut is slidably inserted into the groove and is connected to the eccentric pin by means of a clamping screw.
  • the clamping screw To adjust the distance between the eccentric pin and the axis of rotation of the rotating body, the clamping screw must be loosened, whereby the eccentric pin can be moved into the desired position along the groove. Then the clamping screw is to be tightened again and the eccentric pin is in turn firmly connected to the rotating body.
  • a stepless adjustment of the axial stroke of the friction rollers can be carried out with this device, however, for each adjustment process, at least the drive of the rotary body must be uncoupled from the machine drive in order to stop the rotary movement of the rotary body.
  • the aforementioned device it is therefore not possible to adjust the axial stroke of the friction rollers during the production process.
  • the adjustment of the axial stroke of the friction roller consequently requires extensive intervention in the stroke drive.
  • An automatic Adjustment or an adjustment from outside the machine is not possible with this device.
  • DE-OS 25 14 414 shows a further device for adjusting the axial stroke for the back and forth movement of friction rollers.
  • a rocker arm is pivotally mounted in a rotating body and can be deflected from its zero position by an adjusting device.
  • a hinge pin is attached to its end facing away from the adjusting device.
  • a lever is articulated to this hinge pin, which transmits the movement to the friction rollers as a reciprocating movement. By deflecting the rocker arm from its zero position, the pivot pin is at a distance from the axis of rotation of the rotating body and is thus brought into an eccentric position.
  • the ink can be rubbed in the production process with such reciprocating movements of friction rollers, but that these axial movements can also be used in the automatic washing process of the inking unit and dampening unit rollers.
  • different widths can be printed across the width of the web to be printed.
  • the applicator rollers have punctures at the edge zones of the sides.
  • the axial stroke of the rubbing movement of the distribution rollers is smaller than the width of the recesses of the application rollers in order to avoid different colors is transferred from one zone to the other by the friction rollers.
  • the object of the invention is to provide a device with which it is possible to continuously or manually adjust the axial rubbing movement of friction rollers for inking and dampening units during the running of the machine in such a way that the adjustable maximum stroke, the is used for automatic washing of the inking and dampening unit rollers, is greater than the largest stroke required for rubbing during the production process, as a result of which an efficient washing of the rollers can be achieved when the production is changed over.
  • the adjustment of the eccentric pin by turning of the eccentric bolt is advantageously carried out via a sleeve provided with internal teeth and external helical teeth, which is rotatably mounted coaxially on the rotating housing.
  • This sleeve is rotated with respect to the housing in a simple manner by displacing a gearwheel, which likewise has helical teeth, which is arranged outside the housing on an axis parallel to the axis of rotation of the housing.
  • This helical toothed gear is connected in a rotationally fixed but displaceable manner via a gearwheel which is in engagement with a toothing attached to the housing, as a result of which the helical toothed gear does not change its rotational position with respect to the housing.
  • This helical toothed wheel is advantageously carried out with the aid of a pneumatically actuated piston.
  • An end position of the piston which is specified by a fixed stop, corresponds to the washing stroke position of the eccentric pin.
  • the stroke is adjusted by moving the pneumatically actuated piston away from the maximum stroke position against an adjustable stop. This stop can be adjusted manually or automatically in a known manner.
  • a further advantageous embodiment of the invention is that two eccentric bolts are arranged in the housing, which have the same or different distances from the axis of rotation of the housing.
  • This arrangement ensures that an eccentric pin is available on both sides of the housing, one of which is available Movement for the axial back and forth can be removed by two friction rollers.
  • the axial stroke movement of these two friction rollers is different at different distances between the eccentric bolts from the axis of rotation of the housing because of the different eccentricities of the eccentric pins. So that the axial lifting movements of the two friction rollers are not in phase, the two eccentric pins are mutually out of phase by 90 °.
  • the two eccentric bolts are each provided on the outside with a conical bearing surface, which form plain bearings with correspondingly shaped bearing strikes of the housing. Both eccentric bolts are pressed into the corresponding conical plain bearings by spring pressure.
  • the angle of the slide bearing cone is adjusted in relation to the spring force with which eccentric bolts are pressed into the corresponding slide bearings so that the load changes that occur during the drive for the lifting movements of the friction rollers are not transferred to the gears due to the adhesion of the conical sliding surfaces that, when adjusting the eccentric bolts, the static friction can be overcome without excessive force and the eccentric bolts can be rotated.
  • the housing with the integrated eccentric bolt (s) is advantageously mounted in the printing press in such a way that the axis of rotation of the housing is perpendicular to the axes of rotation of the friction rollers.
  • the respective eccentric pin can be placed directly in a sliding block, which is known on the shaft of the friction roller Way is appropriate to intervene.
  • the housing is equipped with two eccentric bolts, it can be placed between two friction roller shafts in such a way that two eccentric pins arranged on both sides can simultaneously move two friction rollers axially back and forth without the need for additional elements for motion transmission. This results in a simple and space-saving design.
  • the rotatably drivable housing 3 is in supports 4 and 5, fixed to the machine frame, by means of bearings 6 or 7 rotatably mounted.
  • a gearwheel 8 is connected in a rotationally fixed manner to the housing 3 which can be driven in rotation. This gear 8 meshes with a drive gear, not shown, which is driven by the machine drive, whereby the rotatably drivable housing is set in rotation about the axis of rotation 9.
  • the rotatingly drivable housing 3 is enclosed by a coaxially arranged sleeve 10.
  • This sleeve 10 is rotatably mounted with respect to the rotatably drivable housing 3 by a bearing 11 or bearing surface 12.
  • the sleeve 10 has a helical toothing 13 on its outside and a helical toothing 14 on its inside.
  • a recess 15 is made in the rotatably drivable housing 3, which leaves space for a planet gear 16.
  • the planetary gear 16 is freely rotatable on an axis 17.
  • the axis 17 is arranged parallel to the axis of rotation 9 in the rotatingly drivable housing 3.
  • the planetary gear 16 is in engagement with the internal toothing 14 of the sleeve 10.
  • An eccentric bolt 18 is rotatably mounted in the housing 3, which can be driven in rotation, parallel to the axis of rotation 9.
  • the eccentric pin 18 is equipped on one side with an axially parallel eccentric pin 20 which is at a distance a from the axis of rotation 19 of the eccentric pin 18.
  • the eccentric pin 20 projects beyond the cover 21 which closes the housing 3. It engages in a sliding block 29 which, in a known manner, sets the rotating movement of the eccentric pin 20 in the reciprocating movement, which serves as a rubbing movement of the friction roller 30.
  • the eccentric pin 18 is provided on the side of the eccentric pin 20 with a conical slide bearing surface 22, which with a bearing 24 forms a correspondingly shaped opening 21 in the cover.
  • the end of the eccentric pin 18 opposite the eccentric pin 20 is mounted in a radial bearing 23.
  • the eccentric pin 18 is provided with a toothing 25 which is in engagement with the planet gear 16.
  • the eccentric pin 18 is pressed into the conical bearing 24 by a spring 26, which is inserted in an opening 27 of the eccentric pin 18 and which is supported on the cover 28, which closes the rotatably drivable housing 3 at its rear end.
  • the spring force and the cone angle of the bearing 24 are coordinated with one another in such a way that the eccentric pin 18 can be rotated to adjust the distribution stroke, but that the load changes which result from the reciprocating movement of the friction roller do not affect the toothing 25 and the planet gear 16 are transmitted.
  • the adjustment of the distance of the eccentric pin 18 from the axis of rotation 9 of the rotatably drivable housing 3 and thus the adjustment of the stroke of the rubbing movement of the friction roller is carried out by turning the eccentric bolt 18 with respect to the rotatably drivable housing 3.
  • This rotation of the eccentric bolt 18 is done in a descriptive manner that the sleeve 10 is rotated relative to the rotatably drivable housing 3, as a result of which this rotational movement is transmitted to the eccentric pin 18 via the planet gear 16.
  • the rotatably drivable housing 3 has teeth 31 arranged coaxially with the axis of rotation 9, which has the same effective diameter as the helical teeth 13 of the sleeve 10.
  • the rotatably drivable housing 3 is constructed identically, as was described in FIG. 1. The difference is that two eccentric bolts 32 and 33 are rotatably mounted parallel to the axis of rotation 9 of the rotatably drivable housing 3.
  • the first eccentric bolt 32 and the second eccentric bolt 33 abut one another in the middle in the rotatably drivable housing 3 with a small space on the end face.
  • the axis of rotation 34 of the first eccentric bolt 32 and the turning axis 35 of the second eccentric bolt 33 can be at a different distance a and b from the axis of rotation 9 of the housing 3 which can be driven in rotation (cf. FIG. 7).
  • Both eccentric bolts 32 and 33 are equipped at the outer ends with an eccentric pin 36 and 37, respectively, which, in the manner described, cause the corresponding friction rollers 38 and 39 to move axially back and forth. Both eccentric bolts 32 and 33 can be seen on the eccentric pin side with conical sliding bearing surfaces 40 and 41, which are rotatably supported in corresponding openings in the covers 42 and 43, which close off the rotatingly drivable housing 3 on both sides. Each of the eccentric bolts 32 and 33 is held with an additional radial bearing 44 and 45, respectively. Both eccentric bolts 32 and 33 are equipped at their adjacent ends with teeth 46 and 47, respectively, both of which are in engagement with the planetary gear 16. By turning the sleeve 10, the two eccentric bolts 32 and 33 are rotated together via the planet gear 16.
  • a spring bolt 49 is slidably inserted into an opening of the first eccentric bolt 32 and is pressed with a spring 50 against the end face of the second eccentric bolt 33.
  • This spring bolt 49 causes both the first eccentric bolt 32 and the second eccentric bolt 33 to be pressed against the corresponding conical slide bearing surface 40 or 41.
  • the spring force of the spring 50 and the cone angle of the two slide bearing surfaces 40 and 41 are matched to one another in such a way that the eccentric bolts 32 and 33 can be rotated to adjust the displacement stroke of the two friction rollers 38 and 39, but that the load changes that result from the back and forth movement of the friction rollers 38 and 39 respectively , not be transferred to the toothing of the adjustment device.
  • the rotatably drivable housing 3 has a recess 15 in which the planet gear 16 is arranged.
  • the planetary gear 16 is freely rotatable about the axis 17, which is fixedly connected to the rotatingly drivable housing 3.
  • the sleeve 10 is rotatably mounted around the rotatably drivable housing 3.
  • the sleeve 10 has a helical toothing 13 on the outside, while the inner straight toothing 14 is in engagement with the planetary gear 16.
  • Both the rotatably drivable housing 3 and the sleeve 10 have a common axis of rotation 9.
  • the first eccentric pin 32 is rotatably supported at a distance a from the axis of rotation 9, while the second eccentric pin 33 is at a distance b from the axis of rotation 9. Both the toothing 46 of the first eccentric bolt 32 and the toothing 47 of the second eccentric bolt 33 are in engagement with the planet gear 16 and consequently have the same distance from the axis 17 of the planet gear 16.
  • FIGS. 4 and 5 show in spatial representation how the rotation of the sleeve 10 with respect to the rotatably drivable housing 3 takes place.
  • a spur gear 52 is arranged which is in permanent engagement with the toothing 31 of the rotatably drivable housing 3.
  • helical toothed adjusting wheel 53 which is continuously in engagement with the helical toothing 13 of the sleeve 10.
  • the adjusting wheel 53 is displaceable with respect to the spur gear 52 on the schematically illustrated shaft 51, but maintains its rotational position with respect to the spur gear 52. This is achieved in that the adjusting wheel 53 has a bush 54 which is profiled in the longitudinal direction and which can be inserted into a correspondingly shaped opening 55 of the spur gear 52.
  • the rotatably drivable housing 3 sets the gear wheel 8 in rotation from the machine drive.
  • the spur gear 52 which engages with the toothing 31 of the rotatably drivable housing and the adjusting wheel 53 are also set in rotation.
  • the adjusting wheel 53 transmits the rotational movement via the helical toothing 13 to the sleeve 10. Since the toothing 31 and helical toothing 13 of the sleeve 10 on the one hand and the adjusting wheel 53 and the spur gear 52 on the other hand have the same effective diameter, the rotatably drivable housing 3 and the sleeve 10 are relative to each other silent.
  • the adjusting wheel 53 is displaced in the longitudinal direction of the shaft 51 shown schematically.
  • the helical toothing of the adjusting wheel 53 and the helical toothing 13 of the sleeve 10 cause the sleeve 10 to rotate.
  • This adjusting process can be carried out both during the running of the rotatably drivable housing 3 and when it is at a standstill.
  • Fig. 4 shows the adjusting wheel 53 in its left extended position. In this position, the eccentric pin 36 has its maximum distance c from the axis of rotation 9 of the rotatably drivable housing 3. This means that the back and forth movement transferred to the friction roller is maximum and corresponds to the washing stroke.
  • FIG. 6 shows the adjusting device for displacing the adjusting wheel 53.
  • the adjusting wheel 53 is equipped with a bushing 54, which is profiled on its surface in the longitudinal direction.
  • This sleeve 54 can be inserted into a correspondingly designed opening 55 of the spur gear 52, which is stationary.
  • Both spur gear 52 and adjusting wheel 53 are rotatable about axis 51.
  • the bush 54 is firmly connected to a piston rod 56.
  • the piston rod 56 forms a unit with a piston 57 and a cylinder housing 58, which has the function of a pneumatic cylinder.
  • the piston rod 56 is divided into two parts, which are coupled together in a known manner with a bearing, so that the rotational movement of the spur gear 52 and the adjusting wheel 53 is not transmitted to the piston 57, whereas the pushing movement of the piston 57 onto the sleeve 54 of the adjusting wheel 53 must be transferred.
  • the left end position of the adjusting wheel 53 is fixed by the fixed stop 59 of the piston 57. This position means that the reciprocating movement of the friction roller becomes maximum and corresponds to the washing stroke.
  • the piston 57 is acted upon by a pressure medium from the other side and moves against an adjustable stop 60.
  • the adjustable stop 60 is provided with a thread 61 so that it can be turned the position of the adjustable stop 60 as a result of the thread 61 can be changed.
  • the adjustable stop 60 is rotated via a toothed belt drive (not shown) onto the toothed belt pinion 62.
  • the axis of rotation 34 of the first eccentric bolt 32 is at a distance a from the axis of rotation 9.
  • the eccentric pin 36 has the same distance a from the axis of rotation 34 of the eccentric pin 32.
  • the axis of rotation 35 of the second eccentric bolt 33 is arranged at a distance b from the axis of rotation 9 at right angles to the distance a.
  • the center of the eccentric pin 37 is at the same distance b from the axis of rotation 35 of the second eccentric pin 33.
  • the center of the eccentric pin 37 coincides with the axis of rotation 9 at zero position.
  • the right angle between the distance a of the eccentric bolt 32 and the distance b of the eccentric bolt 33 from the axis of rotation 9 was chosen so that the displacement stroke of two simultaneously driven reciprocating friction rollers does not run in phase.
  • Fig. 8 shows schematically the placement of such a rotatable housing 3 with the two eccentric pins 36 and 37 between two distribution rollers 38 and 39 of a printing press 65. From the distribution rollers 38 and 39, the ink or dampening solution is transferred to the plate cylinder 68 via application rollers 66 and 67. From there, the print image is transferred via the blanket cylinder 69 to the print carrier, not shown.

Landscapes

  • Transmission Devices (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
EP91810784A 1990-10-12 1991-10-08 Dispositif de réglage continu du mouvement de distribution axial de rouleaux distributeurs Expired - Lifetime EP0480879B2 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE4032470A DE4032470A1 (de) 1990-10-12 1990-10-12 Vorrichtung zur stufenlosen verstellung der axialen verreibungsbewegung von reibwalzen
DE4032470 1990-10-12

Publications (3)

Publication Number Publication Date
EP0480879A1 true EP0480879A1 (fr) 1992-04-15
EP0480879B1 EP0480879B1 (fr) 1994-09-21
EP0480879B2 EP0480879B2 (fr) 1999-02-03

Family

ID=6416188

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91810784A Expired - Lifetime EP0480879B2 (fr) 1990-10-12 1991-10-08 Dispositif de réglage continu du mouvement de distribution axial de rouleaux distributeurs

Country Status (3)

Country Link
US (1) US5158019A (fr)
EP (1) EP0480879B2 (fr)
DE (2) DE4032470A1 (fr)

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730448A1 (fr) * 1995-02-10 1996-08-14 Heidelberger Druckmasch Ag Commande de rouleaux distributeurs du mecanisme encreur de machines rotatives a imprimer
US6220159B1 (en) 1997-08-20 2001-04-24 Koenig & Bauer Aktiengesellschaft Crank mechanism for distribution cylinder in a rotary press

Families Citing this family (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4140048C2 (de) * 1991-12-05 1995-09-21 Roland Man Druckmasch Farbwerk einer Druckmaschine, insbesondere Bogenoffsetdruckmaschine
DE29503966U1 (de) * 1995-03-08 1995-06-14 MAN Roland Druckmaschinen AG, 63075 Offenbach Vorrichtung zur Verstellung des Verreibungseinsatzes
DE19756077A1 (de) * 1997-12-17 1999-06-24 Heidelberger Druckmasch Ag Verfahren zum Betrieb einer Rotationsdruckmaschine und Vorrichtung in einer Rotationsdruckmaschine
EP1552924A3 (fr) * 2001-11-08 2007-09-05 Koenig & Bauer Aktiengesellschaft Dispositif d'entrainement d'un groupe d'impression
DE202012004791U1 (de) * 2012-05-15 2012-07-03 Heidelberger Druckmaschinen Ag Reiberwalze mit separatem Antriebsmotor

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3077159A (en) * 1961-02-10 1963-02-12 Samuel M Langston Co Variable stroke reciprocating mechanism
US3118373A (en) * 1964-01-21 mosemiller

Family Cites Families (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DD45547A (fr) *
DD65937A (fr) *
US897152A (en) * 1906-11-14 1908-08-25 Max Rockstroh Attachment for printing-presses.
DE1227747B (de) * 1961-02-10 1966-10-27 Samuel M Langston Company Getriebe zur UEbertragung einer Drehbewegung in die hin- und hergehende Bewegung zweier Wellen in Achsrichtung mit veraenderlichem Hub, insbesondere zum Hin- und Herbewegen von Farbwalzen in Achsrichtung in einer Druckpresse
DE1761389A1 (de) * 1968-05-13 1971-06-03 Polygraph Leipzig Vorrichtung zum Verstellen des Reibzylinderhubes in Farbwerken von Rotationsdruckmaschinen
DE2514414C3 (de) * 1975-04-02 1979-11-08 Koenig & Bauer Ag, 8700 Wuerzburg Vorrichtung zum axialen Hin- und Herbewegen von Reibwalzen
DE8015906U1 (de) * 1980-06-14 1980-09-11 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Vorrichtung zum axialen hin- und herbewegen einer farbwerkswalze an rotationsdruckmaschinen
DD159837A3 (de) * 1981-04-29 1983-04-13 Hermann Doebler Vorrichtung zum verstellen des axialen changierhubes von reibwalzen
DE3814927C1 (fr) * 1988-05-03 1989-12-14 Man Roland Druckmaschinen Ag, 6050 Offenbach, De
DE3840871A1 (de) * 1988-12-03 1990-06-07 Heidelberger Druckmasch Ag Walze fuer ein farbwerk von druckmaschinen

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3118373A (en) * 1964-01-21 mosemiller
US3077159A (en) * 1961-02-10 1963-02-12 Samuel M Langston Co Variable stroke reciprocating mechanism

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2730448A1 (fr) * 1995-02-10 1996-08-14 Heidelberger Druckmasch Ag Commande de rouleaux distributeurs du mecanisme encreur de machines rotatives a imprimer
US6220159B1 (en) 1997-08-20 2001-04-24 Koenig & Bauer Aktiengesellschaft Crank mechanism for distribution cylinder in a rotary press

Also Published As

Publication number Publication date
US5158019A (en) 1992-10-27
EP0480879B2 (fr) 1999-02-03
EP0480879B1 (fr) 1994-09-21
DE4032470A1 (de) 1992-04-30
DE59103035D1 (de) 1994-10-27
DE4032470C2 (fr) 1992-09-24

Similar Documents

Publication Publication Date Title
DE2818662C2 (de) Vorrichtung zum Einstellen des Seiten- und Umfangsregisters eines Plattenzylinders einer Rotationsdruckmaschine
EP1441905B1 (fr) Dispositif d'entrainement d'un groupe d'impression
CH692141A5 (de) Druckwerk für den fliegenden Druckplattenwechsel.
DE19724765A1 (de) Antrieb für ein Druckwerk einer Rotationsdruckmaschine
EP0340428B1 (fr) Transmission intermédiaire pour transférer un mouvement rotatif dans le va-et-vient d'un rouleau dans le dispositif d'encrage et/ou de mouillage des imprimeries rotatives
DE19736118C2 (de) Kurbeltrieb
EP0480879B1 (fr) Dispositif de réglage continu du mouvement de distribution axial de rouleaux distributeurs
DE4442302B4 (de) Vorrichtung zum axialen hin- und herbewegen von Reibwalzen im Farbwerk von Druckmaschinen
DE2658362C3 (de) Farbwerk für eine Druckmaschine, insbesondere zum Bedrucken von Tuben, Hülsen u.dgl.
CH616109A5 (fr)
DE2153690A1 (de) Einrichtung zum Drucken- und Druckabstellen von Zylindern und Walzen in Druckmaschinen
DE69400707T2 (de) Einrichtung zum verstellen des abstandes zwischen zylinderachsen in einer druckmaschine
EP0267504B1 (fr) Palier pour rouleaux applicateurs à mouvement de va-et-vient dans les machines d'impression
DE4013416C1 (fr)
EP1361055B1 (fr) Entraînement pour un rouleau baladeur
DE10328801A1 (de) Vorrichtung zur Druckan- und abstellung in einer Druckmaschine
DE3327872A1 (de) Farbwerk, insbesondere zur anwendung bei tubenbedruckmaschinen
EP0598677A1 (fr) Installation pour éviter des vibrations dans des machines à imprimer
EP1336481B1 (fr) Dispositif de commutation de la commande des pinces d'un cylindre à pinces
DE10242009A1 (de) Druckmaschine, vorzugsweise Flexodruckmaschine
DE3905250C2 (fr)
DE3112995C2 (de) Druckwerk für eine Kleinoffsetdruckmaschine
DE10163962B4 (de) Antrieb eines Druckwerkes
DE1140207B (de) Schaltantrieb fuer die Farbkastenwalze einer Druckmaschine
DE4214709C2 (de) Verreibhubantrieb für Reibzylinder

Legal Events

Date Code Title Description
PUAI Public reference made under article 153(3) epc to a published international application that has entered the european phase

Free format text: ORIGINAL CODE: 0009012

AK Designated contracting states

Kind code of ref document: A1

Designated state(s): CH DE FR GB IT LI SE

17P Request for examination filed

Effective date: 19920724

17Q First examination report despatched

Effective date: 19940222

GRAA (expected) grant

Free format text: ORIGINAL CODE: 0009210

AK Designated contracting states

Kind code of ref document: B1

Designated state(s): CH DE FR GB IT LI SE

REF Corresponds to:

Ref document number: 59103035

Country of ref document: DE

Date of ref document: 19941027

ITTA It: last paid annual fee
ITF It: translation for a ep patent filed

Owner name: SOCIETA' ITALIANA BREVETTI S.P.A.

GBT Gb: translation of ep patent filed (gb section 77(6)(a)/1977)

Effective date: 19941110

ET Fr: translation filed
EAL Se: european patent in force in sweden

Ref document number: 91810784.8

PLBI Opposition filed

Free format text: ORIGINAL CODE: 0009260

26 Opposition filed

Opponent name: MAN ROLAND DRUCKMASCHINEN AG

Effective date: 19950619

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PLAW Interlocutory decision in opposition

Free format text: ORIGINAL CODE: EPIDOS IDOP

PUAH Patent maintained in amended form

Free format text: ORIGINAL CODE: 0009272

STAA Information on the status of an ep patent application or granted ep patent

Free format text: STATUS: PATENT MAINTAINED AS AMENDED

27A Patent maintained in amended form

Effective date: 19990203

AK Designated contracting states

Kind code of ref document: B2

Designated state(s): CH DE FR GB IT LI SE

REG Reference to a national code

Ref country code: CH

Ref legal event code: AEN

Free format text: AUFRECHTERHALTUNG DES PATENTES IN GEAENDERTER FORM

ITF It: translation for a ep patent filed

Owner name: SOCIETA' ITALIANA BREVETTI S.P.A.

EN Fr: translation not filed
REG Reference to a national code

Ref country code: FR

Ref legal event code: RN

Ref country code: FR

Ref legal event code: FC

GBTA Gb: translation of amended ep patent filed (gb section 77(6)(b)/1977)
ET3 Fr: translation filed ** decision concerning opposition
PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: CH

Payment date: 20010116

Year of fee payment: 10

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: LI

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

Ref country code: CH

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20011031

REG Reference to a national code

Ref country code: GB

Ref legal event code: IF02

REG Reference to a national code

Ref country code: CH

Ref legal event code: PL

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: GB

Payment date: 20040928

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: FR

Payment date: 20041019

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: SE

Payment date: 20041025

Year of fee payment: 14

PGFP Annual fee paid to national office [announced via postgrant information from national office to epo]

Ref country code: DE

Payment date: 20041130

Year of fee payment: 14

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: IT

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES;WARNING: LAPSES OF ITALIAN PATENTS WITH EFFECTIVE DATE BEFORE 2007 MAY HAVE OCCURRED AT ANY TIME BEFORE 2007. THE CORRECT EFFECTIVE DATE MAY BE DIFFERENT FROM THE ONE RECORDED.

Effective date: 20051008

Ref country code: GB

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20051008

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: SE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20051009

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: DE

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060503

EUG Se: european patent has lapsed
GBPC Gb: european patent ceased through non-payment of renewal fee

Effective date: 20051008

PG25 Lapsed in a contracting state [announced via postgrant information from national office to epo]

Ref country code: FR

Free format text: LAPSE BECAUSE OF NON-PAYMENT OF DUE FEES

Effective date: 20060630

REG Reference to a national code

Ref country code: FR

Ref legal event code: ST

Effective date: 20060630

PLAB Opposition data, opponent's data or that of the opponent's representative modified

Free format text: ORIGINAL CODE: 0009299OPPO