EP0480879B1 - 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

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Publication number
EP0480879B1
EP0480879B1 EP91810784A EP91810784A EP0480879B1 EP 0480879 B1 EP0480879 B1 EP 0480879B1 EP 91810784 A EP91810784 A EP 91810784A EP 91810784 A EP91810784 A EP 91810784A EP 0480879 B1 EP0480879 B1 EP 0480879B1
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EP
European Patent Office
Prior art keywords
axis
eccentric
rotation
housing
rotatably drivable
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
EP91810784A
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German (de)
English (en)
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EP0480879A1 (fr
EP0480879B2 (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
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Publication date
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Application filed by Wifag Maschinenfabrik AG filed Critical Wifag Maschinenfabrik AG
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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 has 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 above 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. Automatic adjustment or 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 reciprocating 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 width of the web to be printed can be printed with different colors on one page.
  • 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 that different colors are transferred from one zone to the other by the distribution rollers. Color will of course accumulate in the recesses and on the areas of the friction rollers, which never go beyond the recesses of the application rollers in production, which must be washed off when the color changes and production changes.
  • the axial stroke of the back and forth movement can be increased so that it is larger than the width of the punctures on the application rollers, so that all the ink residues accumulated on the Rubbing rollers are stripped.
  • 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 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.
  • the adjustment of the eccentric pin by turning the eccentric pin is advantageous way 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 and 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 determined by a fixed stop, corresponds to the wash 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.
  • an eccentric pin is available on both sides of the housing, from each of which a movement for the axial back and forth movement of two friction rollers can be taken off.
  • 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 stroke 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 engage directly in a sliding block which is attached to the shaft of the friction roller in a known manner. If the housing is equipped with two eccentric bolts, it can be placed between two friction roller shafts in such a way that the eccentric pins arranged on both sides can simultaneously move two friction rollers axially back and forth without the need for additional elements for transmitting motion. This results in a simple and space-saving design.
  • the rotatably drivable housing 3 is rotatably mounted in supports 4 and 5 fixed to the machine frame by means of bearings 6 and 7, respectively.
  • 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 rotationally drivable housing is rotated 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 planet 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 planet gear 16 is in engagement with the internal toothing 14 of the sleeve 10.
  • an eccentric pin 18 is rotatably mounted in the rotatably drivable housing 3.
  • 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 protrudes 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 forms a bearing 24 with an opening correspondingly shaped in the cover 21.
  • 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 that arise due to the reciprocating movement of the friction roller do not affect the toothing 25 and the planet gear 16 will be 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 rotating 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 to the axis of rotation 9 and having 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 almost abut one another in the middle in the rotatably drivable housing 3 with a small gap. 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 rotatably drivable housing 3 (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 slide 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 planet gear 16. By turning the sleeve 10, the two eccentric bolts 32 and 33 are jointly over the planet gear 16 rotates.
  • 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 sliding 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 caused by the Back and forth movement of the friction rollers 38 and 39 arise, can not be transferred to the teeth of the adjustment device.
  • the rotatably drivable housing 3 has a recess 15 in which the planet gear 16 is arranged.
  • the planet gear 16 is freely rotatable about the axis 17, which is fixedly connected to the rotatably drivable housing 3.
  • the sleeve 10 is rotatably mounted around the rotatably drivable housing 3.
  • the sleeve 10 has helical teeth 13 on the outside, while the inner straight teeth 14 are 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 bolt 32 is rotatably mounted at a distance a from the axis of rotation 9, while the second eccentric bolt 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.
  • a spur gear 52 is arranged which is in permanent engagement with the toothing 31 of the rotatably drivable housing 3.
  • a helical adjusting wheel 53 is seated, 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 sleeve 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 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 teeth 13 to the sleeve 10. Since the teeth 31 and helical teeth 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 rotary 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 through the fixed stop 59 of the piston 57 fixed. 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 from the other side by a pressure medium and moves against an adjustable stop 60.
  • the adjustable stop 60 is provided with a thread 61 so that it can be turned of the adjustable stop 60, the position of the same can be changed as a result of the thread 61.
  • the adjustable stop 60 is rotated via a toothed belt drive (not shown) onto the toothed belt pinion 62.
  • FIG. 7 shows the arrangement of the first eccentric bolt 32 and the second eccentric bolt 33 with respect to the axis of rotation 9 of the housing 3 which can be driven in rotation.
  • 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 rotatably drivable housing 3 with the two eccentric pins 36 and 37 between two rubbing rollers 38 and 39 of a printing press 65. From the rubbing rollers 38 and 39, the ink or dampening solution is applied via application rollers 66 and 67 to the Transfer plate cylinder 68. From there, the print image is transferred via the blanket cylinder 69 to the print carrier, not shown.

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  • Transmission Devices (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)

Claims (12)

1. Dispositif de réglage progressif du mouvement de va-et-vient axial des rouleaux baladeurs sur des machines rotatives d'imprimerie comportant
- un bloc tournant entraîné en rotation par le système d'entraînement de la machine,
- un doigt excentré disposé de manière coaxiale sur le bloc tournant,
- un système de réglage de l'écartement du doigt excentré par rapport à l'axe de rotation du bloc tournant,
- des moyens pour transformer le mouvement tournant du doigt excentré en un mouvement de va-et-vient et pour communiquer celui-ci aux rouleaux baladeurs,
caractérisé par les particularités suivantes :
- au moins un axe excentré (18) est prévu dans un boîtier tournant (3) monté à poste fixe sur des paliers, cet axe excentré étant parallèle à l'axe de rotation (9) du boîtier et pouvant pivoter,
- cet axe excentré (18) porte au moins à l'une de ses extrémités un doigt excentré (20) qui est écarté d'une distance (a) par rapport à l'axe géométrique (19) de l'axe excentré (18),
- l'axe géométrique (19) de l'axe excentré (18) est lui-même écarté de la même distance (a) par rapport à l'axe de rotation (9) du boîtier tournant (3),
- l'axe excentré (18) est associé à un système de réglage (10, 16,52,53) pouvant être manoeuvré de l'extérieur et permettant de faire pivoter l'axe excentré (18) d'un certain angle autour de son axe géométrique (19),
- dans l'une de ses positions extrêmes de réglage, l'axe géométrique du doigt excentré (20) coïncide avec l'axe de rotation (9) du boîtier tournant (3),
- dans son autre position extrême de réglage, l'axe géométrique du doigt excentré (20) est écarté, par rapport à l'axe de rotation (9) du boîtier tournant (3), d'une distance qui correspond à l'amplitude maximum du mouvement de va-et-vient.
2. Dispositif selon la revendication 1, caractérisé en ce que le système de réglage (10,16,52,53) prévu pour faire pivoter l'axe excentré (18) comporte une douille (10) montée de manière coaxiale sur le boîtier tournant (3) de manière à pouvoir tourner par rapport à celui-ci, cette douille (10)portant sur sa face interne une denture (14) en prise avec un pignon satellite (16) monté rotativement à poste fixe dans le boîtier tournant (3), ce pignon satellite (16) étant d'autre part en prise avec une denture (25) prévue sur l'axe excentré (18).
3. Dispositif selon la revendication 2, caractérisé en ce que la douille (10) montée sur le boîtier tournant (3) porte extérieurement une denture hélicoïdale (13) avec laquelle est en prise un pignon (53) pourvu d'une denture hélicoïdale correspondante et monté à l'extérieur du boîtier tournant (3), à coulisse sur un axe fixe (51) parallèle à l'axe de rotation du boîtier.
4. Dispositif selon la revendication 3, caractérisé en ce que le pignon (53) à denture hélicoïdale est solidaire en rotation d'un autre pignon (52) à denture droite, mais peut coulisser par rapport à cet autre pignon (52), celui-ci étant lui-même en prise avec une denture (31) qui est prévue sur le boîtier tournant (3) et qui peut tourner autour de l'axe de rotation (9).
5. Dispositif selon l'une des revendications 3 ou 4, caractérisé en ce que le coulissement du pignon (53) à denture hélicoïdale est commandé par le piston (57) d'un vérin pneumatique, dont on peut régler la course au moyen d'une butée réglable (60).
6. Dispositif selon l'une des revendications 1 à 5,caractérisé en ce que l'axe excentré (18) porte sur chacune de ses deux extrémités un doigt excentré (20), chacun des deux doigts excentrés ayant la même position par rapport à l'axe géométrique (19) de l'axe excentré (18).
7. Dispositif selon l'une des revendications 1 à 5, caractérisé en ce qu'il comporte un deuxième axe excentré (33) monté à côté d'un premier doigt excentré (32) dans le boitier tournant (3), de telle manière que, son doigt excentré (37), placé à l'opposé du doigt excentré (36) du premier axe excentré (32), étant écarté d'une distance (b) par rapport à l'axe géométrique (35) du deuxième axe excentré (33), cet axe géométrique (35) du deuxième axe excentré (33) soit écarté de la même distance (b) par rapport à l'axe de rotation (9) du boîtier tournant (3).
8. Dispositif selon la revendication 7, caractérisé en ce que les deux doigts excentrés (36,37) sont décalés d'un angle de 90 ° l'un par rapport à l'autre, et en ce que les deux écartements (a,b) des axes géométriques (34,35) du premier axe excentré (32) et du deuxième axe excentré (33) par rapport à l'axe de rotation (9) forment entre eux un angle de 90 °.
9. Dispositif selon la revendication 7 ou 8, caractérisé en ce que chacune des deux dentures (46,47) disposées à l'extrémité des deux axes excentrés (32,33) dans la région médiane du boîtier tournant est en prise avec le pignon satellite (16).
10. Dispositif selon l'une des revendications 7 à 9, caractérisé en ce que le palier extérieur (40,41) de chacun des deux axes excentrés (32,33) est un palier lisse à surface de portage conique, et en ce que les deux axes excentrés (32,33) sont pour vus de têtes tronconiques correspondantes, et associés à un ressort d'appui (50) prévu dans la partie médiane du boîtier pour pousser chaque axe excentré en appui contre la surface conique de son palier.
11. Dispositif selon l'une des revendications 1 à 10, caractérisé en ce que le montage du palier tournant (3) dans la machine rotative d'imprimerie (65) est tel que l'axe de rotation (9) du boîtier soit perpendiculaire aux axes de rotation des rouleaux baladeurs (30,38,39), et que chacun des doigts excentrés (20) et/ou (36,37) soit engagé dans un coulisseau qui assure la transformation du mouvement tournant en un mouvement de va-et-vient qui est transmis à chacun des rouleaux baladeurs (30 ; 38,39), dans la direction de l'axe de chacun de ces rouleaux.
12. Dispositif selon la revendication 11, caractérisé en ce qu'une roue dentée d'entraînement (8) est clavetée sur le boîtier tournant (3) pour en assurer la rotation sous l'action du système d'entraînement de la machine.
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
DE4032470 1990-10-12
DE4032470A DE4032470A1 (de) 1990-10-12 1990-10-12 Vorrichtung zur stufenlosen verstellung der axialen verreibungsbewegung von reibwalzen

Publications (3)

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

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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

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

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DE29503966U1 (de) * 1995-03-08 1995-06-14 MAN Roland Druckmaschinen AG, 63075 Offenbach Vorrichtung zur Verstellung des Verreibungseinsatzes
DE19736118C2 (de) 1997-08-20 2000-01-20 Koenig & Bauer Ag Kurbeltrieb
DE19756077A1 (de) * 1997-12-17 1999-06-24 Heidelberger Druckmasch Ag Verfahren zum Betrieb einer Rotationsdruckmaschine und Vorrichtung in einer Rotationsdruckmaschine
EP1938975A3 (fr) * 2001-11-08 2013-08-28 Koenig & Bauer AG Dispositif d'entrainement d'un groupe d'impression
DE202012004791U1 (de) * 2012-05-15 2012-07-03 Heidelberger Druckmaschinen Ag Reiberwalze mit separatem Antriebsmotor
CN120117449B (zh) * 2025-05-10 2025-08-01 太谷县祥鑫智能机械制造有限公司 一种用于再生聚乙烯材料生产的上料装置

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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
US3077159A (en) * 1961-02-10 1963-02-12 Samuel M Langston Co Variable stroke reciprocating mechanism
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

Also Published As

Publication number Publication date
DE59103035D1 (de) 1994-10-27
DE4032470A1 (de) 1992-04-30
EP0480879A1 (fr) 1992-04-15
DE4032470C2 (fr) 1992-09-24
US5158019A (en) 1992-10-27
EP0480879B2 (fr) 1999-02-03

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