EP0340428B1 - Intermediate drive for the transfer of a rotary motion to a reciprocating motion of a roller in the inking and/or damping unit of a rotary offset press - Google Patents

Intermediate drive for the transfer of a rotary motion to a reciprocating motion of a roller in the inking and/or damping unit of a rotary offset press Download PDF

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Publication number
EP0340428B1
EP0340428B1 EP89104455A EP89104455A EP0340428B1 EP 0340428 B1 EP0340428 B1 EP 0340428B1 EP 89104455 A EP89104455 A EP 89104455A EP 89104455 A EP89104455 A EP 89104455A EP 0340428 B1 EP0340428 B1 EP 0340428B1
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EP
European Patent Office
Prior art keywords
roller
drive
gear
drive shaft
rollers
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
EP89104455A
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German (de)
French (fr)
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EP0340428A2 (en
EP0340428A3 (en
Inventor
Peter Hummel
Roland Höll
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Manroland AG
Original Assignee
MAN Roland Druckmaschinen AG
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Publication date
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Priority to AT89104455T priority Critical patent/ATE73050T1/en
Publication of EP0340428A2 publication Critical patent/EP0340428A2/en
Publication of EP0340428A3 publication Critical patent/EP0340428A3/en
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Publication of EP0340428B1 publication Critical patent/EP0340428B1/en
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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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/16—Alternating-motion driven device with means during operation to adjust stroke
    • Y10T74/1625—Stroke adjustable to zero and/or reversible in phasing
    • Y10T74/1658—Eccentric and strap drive, shiftable eccentric
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/16—Alternating-motion driven device with means during operation to adjust stroke
    • Y10T74/1625—Stroke adjustable to zero and/or reversible in phasing
    • Y10T74/1675—Crank pin drive, shiftable pin
    • 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
    • Y10T—TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
    • Y10T74/00—Machine element or mechanism
    • Y10T74/18—Mechanical movements
    • Y10T74/18056—Rotary to or from reciprocating or oscillating
    • Y10T74/18272—Planetary gearing and slide

Definitions

  • the invention relates to an intermediate gear for transmitting a rotary motion in a reciprocating motion of a part to be driven mounted outside the gear with a variable phase position from drive to output, in particular a roller in inking and / or dampening units of offset printing presses according to the preamble of the first claim.
  • An intermediate gear of the type specified above is known from DE-PS 800 264.
  • the gearbox uses a pair of cardan circles (see FIGS. 3 and 4) with an adjustable ring which has internal teeth.
  • the intermediate gear allows the deflection of a back and forth movement to be changed in a particularly space-saving manner and, at the same time, the phase position to be changed from drive to drive.
  • a planet gear driven by a crank pin is accommodated to save space.
  • the disadvantage is that the reduction ratio of the intermediate gear is fixed at 1: 2.
  • Intermediate gear with variable phase position from drive to output which different gear ratios and exclusively Have rotatably arranged gear members, which can be stored free of play and wear-free, are known per se, for example from DE-OS 2 228 939.
  • This intermediate gear is a gear with a variable phase position for the axial displacement movement of two mutually oscillating friction rollers in inking units .
  • the disadvantage is that the drive part of such an intermediate gear requires a large amount of space, so that it cannot be accommodated on the drive side of an offset printing machine.
  • the intermediate gear according to the invention has significant advantages. First of all, it is particularly space-saving and can therefore be accommodated on the drive side of an offset printing machine. Furthermore, due to the possibility of using only backlash-free, wear-resistant bearings, i.e. by dispensing with the sliding guide on the gearbox output part and the fact that the drive and output directions of rotation remain the same, it is particularly suitable for high-speed machines, with a variable (e.g. integer) reduction of the rotary movement , e.g. 1: 2, 1: 3, 1: 4, 1: 8 can be realized.
  • a variable (e.g. integer) reduction of the rotary movement e.g. 1: 2, 1: 3, 1: 4, 1: 8 can be realized.
  • a pendulum-like reciprocating siphon roller 16 takes fresh printing ink and transfers it to a distribution roller 15.
  • the ink flow leads via an ink supply roller 14 to another distribution roller 12.
  • This distribution roller 12 divides the ink flow in two ink streams, one of which is guided onto a branch roller 11 and the other onto a branch roller 13.
  • the first partial ink flow is passed via the branch roller 13 and an ink transport roller 8 to two front inking rollers 3, 4.
  • the second ink stream is passed via the branch roller 11 and a friction roller 7 to the first application roller 3 and additionally to a further ink application roller 2.
  • the inking rollers 2 to 4 ink an offset printing plate, which is clamped on the plate cylinder 1.
  • the second applicator roller 4 is followed in the direction of rotation of the plate cylinder 1 by a rear inking roller 5 and optionally another inking roller 6.
  • Another inking roller 9 rolls on the inking rollers 4 and 5, and a plastic-coated inking roller 10 is mounted on the inking rollers 5, 6 as a rider roller.
  • the friction rollers 7, 9, 12 are rotated by a central gear 38 arranged between them, which was then driven by the plate cylinder 1.
  • the friction roller 15 is also driven via a further central gear, not shown.
  • a toothed ring 44 is also rotatably arranged via bearings, which is adjustable via a toothing provided on its outer contour and a toothed pinion 45 engaging in it.
  • the toothed pinion 45 is fastened on an adjusting shaft 46 which is rotatably mounted in a holding plate 75 of the machine frame 41, the adjusting shaft being designed to be rotatable from the outside by hand or also by means of a motor in the machine barrel and can be locked in this position.
  • a worm can be used, which cooperates with a worm gear teeth on the ring gear 44 self-locking. It is also conceivable to use a sprocket instead of the pinion 45 to drive the adjusting shaft 46.
  • bores 61 to 63 are located on the ring gear 44 at a distance a around the drive axis 56 of the coaxial shaft journal 39 of the drive shaft 37. These are offset by the same angular amount, e.g. the three bores shown in FIG. 3 are each offset by 120 °.
  • the planet gear 43 is firmly seated on a stepped collar of a disk 48 which is rotatably mounted on the eccentric pin 40 of the drive shaft 37.
  • a plurality of rollers 50 to 52 are located on the disk 48 at the same distance a around the center of the pin 49.
  • the rollers are supported on the inner surface of the bores 61 to 63 and roll on the surface thereof, the axes 53 to 55 of which move on a circular path 58 to 60.
  • the distance between the axes 64 to 66 of each bore 61 to 63 to the axes 53 to 55 of each roller 50 to 52 must be selected equal to the distance e of the drive axis 56 of the drive shaft 37 to the center of the pin 49 of the eccentric pin 40 in order to ensure a perfect transmission quality of the transmission to guarantee.
  • the radius of the bores 61 to 63 is thus calculated from the sum of the eccentricity of the planet gear 43 and the radius of the cam rollers 50 to 52.
  • a sun gear 42 provided with an internal toothing 47 is rotatably mounted as a gear output part, in which the planet gear 43 engages.
  • a sliding block 23 is adjustable and lockable in a groove 22 of the sun gear 42 by a screw 21.
  • a rocker arm 20 is rotatably received via a bearing, the movement of which is transmitted via coupling elements 24 to 29, 31 to 36 in a manner known per se to the stub axles 70 to 72, 76 of the friction rollers 7, 9, 12, 15.
  • the rotation of the planet gear 43 on the eccentric pin 40 is prevented by the rollers 50 to 52.
  • the rollers 50 to 52 are supported in the bores 61 to 63 of the gear 44 and roll evenly on their surface. This means that the center of the planet gear 43, at the same time the center of the pin 49 of the eccentric pin 40, rotates on a circular path 57, the radius of which corresponds to the eccentricity e (crank circle).
  • the axes 53 to 55 of the rollers 50 to 51 also describe a circular path 58 to 60, the radius of which also corresponds to the eccentricity e.
  • the phase position changes from drive to output.
  • the crank drive 18 coupled to the rotating sun gear 42 on the output side or a comparable output generating a reciprocating movement is not influenced with regard to the deflection of the movement.
  • the Phase position and a stroke or the deflection of the reciprocating movement can be set independently of one another. The meaning of such an adjustment possibility is described in DE-OS 2 228 939.
  • the intermediate gear according to the invention with a variable phase position from drive to output can be replaced by replacing the crank mechanism 18 with a known cam mechanism not shown in the drawing, also for converting a rotary movement into the pendulum movement of a lifting roller with a variable phase position, e.g. use in inking units.
  • the cam disc is attached to the sun gear 42 and its movement is transmitted in a known manner to a roller lever (not shown) connected to the roller axis of the lifting roller.
  • Another application would be the control of switching movements of parts, e.g. the gradual switching of a duct roller in inking units.
  • the gimbal-type intermediate gear according to the invention can be used for applications with large ratios in which the working time of a device connected to the intermediate gear is to be adjusted while the machine is running in an extremely space-saving design, without the deflection or stroke of the oscillating movement being adjusted by the adjustment to influence.

Landscapes

  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Transmission Devices (AREA)
  • Friction Gearing (AREA)
  • Gear Transmission (AREA)
  • Rotary Presses (AREA)
  • Retarders (AREA)
  • Wet Developing In Electrophotography (AREA)

Abstract

The object of the invention is, in an intermediate gear for transferring a rotational movement into the to-and-fro movement of a roller with a variable phase relation from drive to output in inking units of offset printing machines, to make it possible, in an extremely space-saving design, to obtain a rotatable arrangement of all the gear members and a variable reduction of the rotational movement. <??>For this, bores (61 to 63) are located on a crown gear (44) at a distance a about the driving axis (56) of the drive shaft (37) and are arranged offset relative to one another by the same angular amount alpha . A planet wheel (43) sits on a stepped collar of a disc (48) which is mounted rotatably on the eccentric journal (40) of the drive shaft (37). Located on the disc (48) at a distance a around the journal centre (49) are a plurality of rollers (50 to 52) which are likewise arranged offset relative to one another by the same angular amount alpha and which roll on the inner face of the bores (61 to 63). <??>Rotatably mounted as a gear output part in line with the crown gear (44) is a sun wheel (42) which is equipped with an internal toothing (47) and into which the planet wheel (43) engages. <IMAGE>

Description

Die Erfindung betrifft ein Zwischengetriebe zur Übertragung einer Drehbewegung in eine Hin- und Herbewegung eines außerhalb des Getriebes gelagerten anzutreibenden Teiles mit veränderlicher Phasenlage von Antrieb zu Abtrieb, insbesondere einer Walze in Farb- und/oder Feuchtwerken von Offsetdruckmaschinen nach dem Oberbegriff des ersten Patentanspruches.The invention relates to an intermediate gear for transmitting a rotary motion in a reciprocating motion of a part to be driven mounted outside the gear with a variable phase position from drive to output, in particular a roller in inking and / or dampening units of offset printing presses according to the preamble of the first claim.

Ein Zwischengetriebe vorstehend spezifizierter Gattung ist aus der DE-PS 800 264 bekannt. Das Getriebe verwendet ein Kardankreispaar (siehe Fig. 3 und 4) mit einem einstellbaren Kranz, der eine Innenverzahnung aufweist. Das Zwischengetriebe erlaubt in besonders platzsparender Weise die Veränderung des Ausschlages einer Hin- und Herbewegung und zugleich die Veränderung der Phasenlage von Antrieb zu Abtrieb. In dem einstellbaren Kranz mit Innenverzahnung wird ein über einen Kurbelzapfen angetriebenes Planetenrad platzsparend aufgenommen. Von Nachteil ist jedoch, daß das Untersetzungsverhältnis des Zwischengetriebes mit 1:2 gleich konstant festliegt. Nur so beschreibt der als Abtriebszapfen des Kardankreispaares ausgebildete Punkt am einfach großen Planetenrad eine durch die Mitte des doppelt großen innenverzahnten Kranzes gehende Gerade, wobei mittels eines Gleitsteines der als Abtriebszapfen des Kardankreispaares am Planetenrad ausgebildete Punkt mittels eines Gleitsteines in einem Längsschlitz eines Schwinghebels gleitet. Durch den Ausschlag der so erzeugten, hin- und herschwingenden Bewegung mit gleitender Führung tritt Unruhe und infolge Spiel Verschleiß auf. Für schnelle Maschinen ist dieses gattungsbildende Zwischengetriebe mit veränderlicher Phasenlage von Antrieb zu Abtrieb deshalb nicht geeignet.An intermediate gear of the type specified above is known from DE-PS 800 264. The gearbox uses a pair of cardan circles (see FIGS. 3 and 4) with an adjustable ring which has internal teeth. The intermediate gear allows the deflection of a back and forth movement to be changed in a particularly space-saving manner and, at the same time, the phase position to be changed from drive to drive. In the adjustable ring with internal teeth, a planet gear driven by a crank pin is accommodated to save space. The disadvantage, however, is that the reduction ratio of the intermediate gear is fixed at 1: 2. This is the only way the point designed as the output pin of the pair of cardan circles on the single large planet gear describes a straight line passing through the middle of the double large internally toothed ring, whereby the point designed as the output pin of the pair of cardan circles on the planet gear slides in a longitudinal slot of a rocker arm by means of a slide block. As a result of the deflection of the oscillating movement with sliding guidance generated in this way, unrest occurs and wear arises as a result of play. This generic intermediate gearbox with variable phase position from drive to drive is therefore not suitable for fast machines.

Zwischengetriebe mit veränderlicher Phasenlage von Antrieb zum Abtrieb, welche unterschiedliche Übersetzungsverhältnisse und ausschließlich drehbar angeordnete Getriebeglieder aufweisen, die spielfrei und verschleißfrei lagerbar sind, sind an sich bekannt, z.B. aus der DE-OS 2 228 939. Bei diesem Zwischengetriebe handelt es sich um ein Getriebe mit veränderlicher Phasenlage für die axiale Verreibebewegung von zwei gegeneinander changierenden Reibwalzen in Farbwerken. Von Nachteil ist, daß das Antriebsteil derartiger Zwischengetriebe einen hohen Platzaufwand erfordert, so daß es nicht auf der Antriebsseite einer Offsetdruckmaschine untergebracht werden kann.Intermediate gear with variable phase position from drive to output, which different gear ratios and exclusively Have rotatably arranged gear members, which can be stored free of play and wear-free, are known per se, for example from DE-OS 2 228 939. This intermediate gear is a gear with a variable phase position for the axial displacement movement of two mutually oscillating friction rollers in inking units . The disadvantage is that the drive part of such an intermediate gear requires a large amount of space, so that it cannot be accommodated on the drive side of an offset printing machine.

Es ist Aufgabe der Erfindung, das besonders wenig Platz beanspruchende Zwischengetriebe genannter Gattung so zu einem kardanähnlichen Rädergetriebe weiterzubilden, daß bei drehbarer Anordnung sämtlicher Getriebeglieder die Untersetzung abweichend von 1:2 vorgebbar ist.It is an object of the invention to further develop the intermediate gear of the type mentioned, which takes up particularly little space, to form a gimbal-like gear transmission in such a way that, with a rotatable arrangement of all the gear members, the reduction ratio can be predetermined to deviate from 1: 2.

Erfindungsgemäß wird die Aufgabe gemäß dem Kennzeichen des ersten Patenanspruches gelöst. Weiterbildungen ergeben sich aus den Unteransprüchen.According to the invention the object is achieved according to the characterizing part of the first patent claim. Further training results from the subclaims.

Das erfindungsgemäße Zwischengetriebe weist wesentliche Vorteile auf. Zunächst ist es besonders platzsparend und kann deshalb auf der Antriebsseite einer Offsetdruckmaschine untergebracht werden. Ferner ist es durch die Möglichkeit der Verwendung ausschließlich spielfreier, verschleißfester Lager, d.h. durch Verzicht auf die gleitende Führung am Getriebeabtriebsteil und dadurch daß die An- und Abtriebsdrehrichtungen gleich bleiben, für schnellaufende Maschinen besonders geeignet, wobei eine variable (z.B. ganzzahlige) Untersetzung der Drehbewegung, z.B. 1:2, 1:3, 1:4, 1:8 realisierbar ist.The intermediate gear according to the invention has significant advantages. First of all, it is particularly space-saving and can therefore be accommodated on the drive side of an offset printing machine. Furthermore, due to the possibility of using only backlash-free, wear-resistant bearings, i.e. by dispensing with the sliding guide on the gearbox output part and the fact that the drive and output directions of rotation remain the same, it is particularly suitable for high-speed machines, with a variable (e.g. integer) reduction of the rotary movement , e.g. 1: 2, 1: 3, 1: 4, 1: 8 can be realized.

Die Erfindung soll nachstehend anhand der Zeichnungen an einem Ausführungsbeispiel näher beschrieben werden.The invention will be described below with reference to the drawings of an embodiment.

Es zeigt:

  • Fig. 1 eine Seitenansicht eines Druckwerkes mit einem Reibwalzenantrieb in einem Farbwerk einer Offsetdruckmaschine,
  • Fig. 2 das erfindungsgemäße Zwischengetriebe in einem Längsschnitt,
  • Fig. 3 den Schnitt A-A nach Fig. 2.
It shows:
  • 1 is a side view of a printing unit with a friction roller drive in an inking unit of an offset printing machine,
  • 2 the intermediate gear according to the invention in a longitudinal section,
  • 3 shows section AA according to FIG. 2.

Von einer angetriebenen Farbkastenwalze 17 einer Offsetdruckmaschine nimmt eine pendelartig hin- und herschwingende Heberwalze 16 frische Druckfarbe ab und übergibt diese an eine Reibwalze 15. Von der Reibwalze 15 führt der Farbfluß über eine Farbzuführwalze 14 auf eine weitere Reibwalze 12. Diese Reibwalze 12 teilt den Farbfluß in zwei Farbströme auf, von denen der eine auf eine Abzweigwalze 11 und der andere auf eine Abzweigwalze 13 geführt wird. Der erste Teilfarbfluß wird über die Abzweigwalze 13 und eine Farbtransportwalze 8 auf zwei vordere Farbauftragwalzen 3, 4 geleitet. Der zweite Farbstrom wird über die Abzweigwalze 11 und eine Reibwalze 7 auf die erste Auftragwalze 3 und zusätzlich auf eine weitere Farbauftragwalze 2 geleitet. Die Farbauftragwalzen 2 bis 4 färben eine Offsetdruckplatte, die auf dem Plattenzylinder 1 aufgespannt ist, ein. Der zweiten Auftragwalze 4 folgt in Drehrichtung des Plattenzylinders 1 gesehen eine hintere Farbauftragwalze 5 und wahlweise eine weitere Farbauftragwalze 6. Auf den Farbauftragwalzen 4 und 5 rollt eine weitere Reibwalze 9 und auf den Farbauftragwalzen 5, 6 ist eine kunststoffbeschichtete Farbtransportwalze 10 als Reiterwalze aufgesetzt. Die Reibwalzen 7, 9, 12 werden durch ein zwischen diesen angeordnetes Zentralzahnrad 38 in Drehung versetzt, daß seinerzeit vom Plattenzylinder 1 angetrieben ist. Die Reibwalze 15 wird über ein weiteres nicht dargestelltes Zentralzahnrad ebenfalls angetrieben.From a driven ink fountain roller 17 of an offset printing machine, a pendulum-like reciprocating siphon roller 16 takes fresh printing ink and transfers it to a distribution roller 15. From the distribution roller 15, the ink flow leads via an ink supply roller 14 to another distribution roller 12. This distribution roller 12 divides the ink flow in two ink streams, one of which is guided onto a branch roller 11 and the other onto a branch roller 13. The first partial ink flow is passed via the branch roller 13 and an ink transport roller 8 to two front inking rollers 3, 4. The second ink stream is passed via the branch roller 11 and a friction roller 7 to the first application roller 3 and additionally to a further ink application roller 2. The inking rollers 2 to 4 ink an offset printing plate, which is clamped on the plate cylinder 1. The second applicator roller 4 is followed in the direction of rotation of the plate cylinder 1 by a rear inking roller 5 and optionally another inking roller 6. Another inking roller 9 rolls on the inking rollers 4 and 5, and a plastic-coated inking roller 10 is mounted on the inking rollers 5, 6 as a rider roller. The friction rollers 7, 9, 12 are rotated by a central gear 38 arranged between them, which was then driven by the plate cylinder 1. The friction roller 15 is also driven via a further central gear, not shown.

Aus den Figuren 2 und 3 ist erkennbar, daß das durch einen Stift 30 befestigte Zentralzahnrad 38 zur Übertragung seiner Drehbewegung in die achsiale Hin- und Herbewegung der Reibwalzen 7, 9, 12 und 15 auf dem koaxialen Wellenzapfen 39 einer parallel zu den Achsstummeln 72 bis 74, 76 der Reibwalzen 7, 9, 12, 15 verlaufenden Antriebswelle 37 sitzt, während auf einem exzentrischen Zapfen 40 der Antriebswelle 37 ein Planetenrad 43 sitzt.From Figures 2 and 3 it can be seen that the central gear 38 fastened by a pin 30 to transmit its rotational movement in the axial back and forth movement of the friction rollers 7, 9, 12 and 15 on the coaxial shaft journal 39 one parallel to the stub axles 72 to 74, 76 of the friction rollers 7, 9, 12, 15 extending drive shaft 37 is seated, while a planet gear 43 is seated on an eccentric pin 40 of the drive shaft 37.

Auf dem koaxialen Wellenzapfen 39 der Antriebswelle 37 ist über Lager ferner ein Zahnkranz 44 drehbar angeordnet, der über eine an seiner Außenkontur vorgesehende Verzahnung und ein in diese eingreifendes Zahnritzel 45 verstellbar ist. Das Zahnritzel 45 ist auf einer in einer Halteplatte 75 des Maschinengestells 41 drehbar gelagerten Verstellwelle 46 befestigt, wobei die Stellwelle von außerhalb von Hand oder auch motorisch im Maschinenlauf verdrehbar ausgebildet und in dieser Position blockierbar ist.On the coaxial shaft journal 39 of the drive shaft 37, a toothed ring 44 is also rotatably arranged via bearings, which is adjustable via a toothing provided on its outer contour and a toothed pinion 45 engaging in it. The toothed pinion 45 is fastened on an adjusting shaft 46 which is rotatably mounted in a holding plate 75 of the machine frame 41, the adjusting shaft being designed to be rotatable from the outside by hand or also by means of a motor in the machine barrel and can be locked in this position.

Anstelle des Zahnritzels 45 kann auch ein anderes selbsthemmendes oder dgl. Teil, z.B. eine Schnecke, eingesetzt werden, die mit einer Schneckenradverzahnung am Zahnkranz 44 selbsthemmend zusammenwirkt. Ebenso ist es denkbar, ein Kettenrad anstelle des Zahnritzels 45 zum Antrieb der Verstellwelle 46 einzusetzen.Instead of the pinion 45, another self-locking or similar part, e.g. a worm can be used, which cooperates with a worm gear teeth on the ring gear 44 self-locking. It is also conceivable to use a sprocket instead of the pinion 45 to drive the adjusting shaft 46.

Erfindungsgemäß befinden sich am Zahnkranz 44 im Abstand a um die Antriebsachse 56 des koaxialen Wellenzapfens 39 der Antriebswelle 37 Bohrungen 61 bis 63. Diese sind um den gleichen Winkelbetrag zueinander versetzt angeordnet, z.B. sind die in der Fig. 3 zu erkennenden drei Bohrungen jeweils um 120° versetzt.According to the invention, bores 61 to 63 are located on the ring gear 44 at a distance a around the drive axis 56 of the coaxial shaft journal 39 of the drive shaft 37. These are offset by the same angular amount, e.g. the three bores shown in FIG. 3 are each offset by 120 °.

Das Planetenrad 43 sitzt fest auf einem abgesetzten Bund einer Scheibe 48, die drehbar auf dem exzentrischen Zapfen 40 der Antriebswelle 37 gelagert ist. An der Scheibe 48 befinden sich im gleichen Abstand a um die Zapfenmitte 49 mehrere Rollen 50 bis 52. Die Rollen 50 bis 52 sind ebenfalls um den gleichen Winkelbetrag α = 120° zueinander versetzt angeordnet. Die Rollen stützen sich auf der Innenfläche der Bohrungen 61 bis 63 ab und rollen auf deren Oberfläche, wobei sich deren Achsen 53 bis 55 auf einer Kreisbahn 58 bis 60 bewegen.The planet gear 43 is firmly seated on a stepped collar of a disk 48 which is rotatably mounted on the eccentric pin 40 of the drive shaft 37. A plurality of rollers 50 to 52 are located on the disk 48 at the same distance a around the center of the pin 49. The rollers 50 to 52 are also offset by the same angular amount α = 120 °. The rollers are supported on the inner surface of the bores 61 to 63 and roll on the surface thereof, the axes 53 to 55 of which move on a circular path 58 to 60.

Der Abstand der Achsen 64 bis 66 jeder Bohrung 61 bis 63 zu den Achsen 53 bis 55 jeder Rolle 50 bis 52 muß gleich dem Abstand e der Antriebsachse 56 der Antriebswelle 37 zur Zapfenmitte 49 des exzentrischen Zapfens 40 gewählt werden, um eine einwandfreie Übertragungsgüte des Getriebes zu gewährleisten. Der Radius der Bohrungen 61 bis 63 errechnet sich somit aus der Summe der Exzentrizität des Planetenrades 43 und dem Radius der Kurvenrollen 50 bis 52.The distance between the axes 64 to 66 of each bore 61 to 63 to the axes 53 to 55 of each roller 50 to 52 must be selected equal to the distance e of the drive axis 56 of the drive shaft 37 to the center of the pin 49 of the eccentric pin 40 in order to ensure a perfect transmission quality of the transmission to guarantee. The radius of the bores 61 to 63 is thus calculated from the sum of the eccentricity of the planet gear 43 and the radius of the cam rollers 50 to 52.

Fluchtend zum Zahnkranz 44 ist als Getriebeabtriebsteil ein mit einer Innenverzahnung 47 versehenes Sonnenrad 42 drehbar gelagert, in welche das Planetenrad 43 eingreift.Aligned with the gear rim 44, a sun gear 42 provided with an internal toothing 47 is rotatably mounted as a gear output part, in which the planet gear 43 engages.

Zur Übertragung der Drehbewegung des Sonnenrades 42 in die Hin- und Herbewegung von Reibwalzen in Achsrichtung mit veränderlichem Hub, z.B. Reibwalzen in Feucht- und Farbwerken von Offsetdruckmaschinen, ist durch eine Schraube 21 verstellbar und feststellbar in einer Nut 22 des Sonnenrades 42 ein Nutenstein 23 geführt. Auf der Schraube 21 ist über ein Lager ein Schwinghebel 20 drehbar aufgenommen, dessen Bewegung über Koppelelemente 24 bis 29. 31 bis 36 in an sich bekannter Weise auf die Achsstummel 70 bis 72, 76 der Reibwalzen 7, 9, 12, 15 übertragen wird.To transmit the rotary motion of the sun gear 42 into the reciprocating motion of friction rollers in the axial direction with a variable stroke, e.g. Friction rollers in dampening and inking units of offset printing machines, a sliding block 23 is adjustable and lockable in a groove 22 of the sun gear 42 by a screw 21. On the screw 21, a rocker arm 20 is rotatably received via a bearing, the movement of which is transmitted via coupling elements 24 to 29, 31 to 36 in a manner known per se to the stub axles 70 to 72, 76 of the friction rollers 7, 9, 12, 15.

Bei Rotation der Antriebswelle 37 und Blockieren des Zahnkranzes 44 mittels des Zahnritzels 45 wird eine gleichmäßige Untersetzung im Zwischengetriebe erzielt. Die Größe der Untersetzung errechnet sich dabei aus 1 minus dem Quotienten aus der Zähnezahl Z₂ des Planetenrades 43 und der Zähnezahl Z₁ des Sonnenrades 42. Beträgt beispielsweise Z₁=32 und Z₂=24, wird eine Untersetzung von 1:4 erreicht, die sich errechnet aus 1 minus 24:32 = 0,25.When the drive shaft 37 rotates and the ring gear 44 is blocked by means of the pinion 45, a uniform reduction in the intermediate gear is achieved. The size of the reduction is calculated from 1 minus the quotient of the number of teeth Z₂ of the planet gear 43 and the number of teeth Z₁ of the sun gear 42. For example, Z₁ = 32 and Z₂ = 24, a reduction of 1: 4 is achieved, which is calculated from 1 minus 24:32 = 0.25.

Sobald zunächst geringfügig vorhandes Spiel beim Anlaufen der Rollen 50 bis 52 auf die Oberfläche der Bohrungen 61 bis 63 beseitigt ist, läuft das Innengetriebe mit konstanter Untersetzung spielfrei bei ruhigem Bewegungsablauf.As soon as a slight amount of play on the surface of the holes 61 to 63 is eliminated when the rollers 50 to 52 start up, the internal gear runs with constant reduction without play and with a smooth movement.

Andere Untersetzungsverhältnisse sind wählbar, ohne daß die Übertragungsgüte des extrem raumsparenden kardanähnlichen Rädergetriebes nachteilig beeinflußt wird.Other reduction ratios can be selected without the transmission quality of the extremely space-saving gimbal-like gear transmission being adversely affected.

Während der Rotation der Antriebswelle 37 wird das Verdrehen des Planetenrades 43 auf dem exzentrischen Zapfen 40 durch die Rollen 50 bis 52 verhindert. Die Rollen 50 bis 52 stützen sich nämlich in den Bohrungen 61 bis 63 des Zahnrades 44 ab und rollen gleichmäßig auf deren Oberfläche. Das bedeutet, daß der Mittelpunkt des Planetenrades 43, zugleich Zapfenmitte 49 des exzentrischen Zapfens 40 auf einer Kreisbahn 57 rotiert, deren Radius der Exzentrizität e entspricht (Kurbelkreis).During the rotation of the drive shaft 37, the rotation of the planet gear 43 on the eccentric pin 40 is prevented by the rollers 50 to 52. The rollers 50 to 52 are supported in the bores 61 to 63 of the gear 44 and roll evenly on their surface. This means that the center of the planet gear 43, at the same time the center of the pin 49 of the eccentric pin 40, rotates on a circular path 57, the radius of which corresponds to the eccentricity e (crank circle).

Außer der Zapfenmitte 49 des exzentrischen Zapfens 40 beschreiben auch die Achsen 53 bis 55 der Rollen 50 bis 51 eine Kreisbahn 58 bis 60, deren Radius ebenfalls der Exzentrizität e entspricht.In addition to the center of the pin 49 of the eccentric pin 40, the axes 53 to 55 of the rollers 50 to 51 also describe a circular path 58 to 60, the radius of which also corresponds to the eccentricity e.

Mit gleicher Drehrichtung wird die Bewegung des so umlaufenden Planetenrades 43 auf das Sonnenrad 42 übertragen.With the same direction of rotation, the movement of the planet gear 43 rotating in this way is transmitted to the sun gear 42.

Wird der Zahnkranz 44 durch Verdrehen des Zahnritzels 45 mittels der Verstellwelle 46 in eine andere Winkellage gegenüber dem Zentralzahnrad 38, d.h. auch gegenüber dem mit dem Zentralzahnrad 38 kämmenden Antriebszahnrad des Plattenzylinders 1 gebracht, so ändert sich die Phasenlage von Antrieb zu Abtrieb. Der an das umlaufende Sonnenrad 42 abtriebsseitig angekoppelte Kurbeltrieb 18 oder ein vergleichbarer eine Hin- und Herbewegung erzeugender Abtrieb wird dabei hinsichtlich des Ausschlages der Bewegung nicht beeinflußt. Somit können die Phasenlage und ein Hub bzw. der Ausschlag der hin- und hergehenden Bewegung unabhängig voneinander eingestellt werden. Die Bedeutung einer derartigen Verstellmöglichkeit ist in der DE-OS 2 228 939 beschrieben.If the ring gear 44 is brought into a different angular position with respect to the central gear 38, ie also with respect to the drive gear of the plate cylinder 1 meshing with the central gear 38, by rotating the pinion 45 by means of the adjusting shaft 46, the phase position changes from drive to output. The crank drive 18 coupled to the rotating sun gear 42 on the output side or a comparable output generating a reciprocating movement is not influenced with regard to the deflection of the movement. Thus, the Phase position and a stroke or the deflection of the reciprocating movement can be set independently of one another. The meaning of such an adjustment possibility is described in DE-OS 2 228 939.

In der in Fig. 2 und 3 dargestellten Lage des Kurbeltriebes 18 erfolgt kein Ausschlag am Schwinghebel 20, d.h. es kann keine Hin- und Herbewegung erzeugt werden. Grund dafür ist, daß in dieser Nullstellung des Getriebes die Abtriebsachse 19 der Schraube 21 so angeordnet ist, daß sie mit der Antriebsachse 56 der Antriebswelle 37 fluchtet. Durch Verschieben und Feststellen der Antriebsachse 19 des auf der Schraube 21 drehbar gelagerten Lagerhebels 20 gemeinsam mit dem auf der Schraube 21 sitzenden Nutenstein 23 in der Nut 22 des Sonnrades 42 kann die Lage der Abtriebsachse 19 zur Antriebsachse 37 geändert werden. Je nach Größe der Exzentrizität im Kurbeltrieb 18 bzw. des gewählten Kurbelradius wird die Hin- und Herbewegung unabhängig von der jeweils eingestellten Phasenlage des Zwischengetriebes verstellbar eingeleitet.In the position of the crank mechanism 18 shown in FIGS. 2 and 3, there is no deflection on the rocker arm 20, i.e. no reciprocation can be generated. The reason for this is that in this zero position of the transmission, the output axis 19 of the screw 21 is arranged so that it is aligned with the drive axis 56 of the drive shaft 37. By moving and locking the drive shaft 19 of the bearing lever 20 rotatably mounted on the screw 21 together with the sliding block 23 seated on the screw 21 in the groove 22 of the sun gear 42, the position of the driven shaft 19 relative to the drive shaft 37 can be changed. Depending on the size of the eccentricity in the crank mechanism 18 or the selected crank radius, the reciprocating movement is initiated in an adjustable manner, regardless of the phase position of the intermediate gear set in each case.

Die Übertragung der Bewegung des Schwinghebels 20 auf die Achsstummel 70 bis 72, 76 der Reibwalzen 7, 9, 12, 15 zu deren Hin- und Herbewegung entspricht dem üblichen Stand der Technik und wird nachstehend nur kurz erläutert. Als Antrieb für die Hin- und Herbewegung sind die als Koppelelemente 24 bis 36 vorstehend bezeichneten Teile, nämlich übliche Kipphebel 25 bis 27 vorgesehen, welche über Lagerzapfen 24, 28, 29 und Lager am Maschinengestelle 41 gelagert sind. Die Kipphebel 25 und 26 werden über zugeordnete Hebelsysteme 31, 32 und der Kipphebel 27 direkt vom Lagerzapfen 24 bewegt, an welchem der Schwinghebel 20 angreift. An den Kipphebeln 25 bis 27 sind Rollen 33 bis 36 gelagert, die in ein nicht näher dargestelltes Führungsscheibenpaar in bekannter Weise angreifen, das auf jedem Achsstummel 70 bis 72, 76 der Reibwalzen 7, 9, 12, 15 angeordnet ist.The transmission of the movement of the rocker arm 20 to the stub axles 70 to 72, 76 of the friction rollers 7, 9, 12, 15 for their back and forth movement corresponds to the usual state of the art and is only briefly explained below. As a drive for the back and forth movement, the parts referred to as coupling elements 24 to 36 above, namely conventional rocker arms 25 to 27, are provided, which are mounted on journals 24, 28, 29 and bearings on the machine frame 41. The rocker arms 25 and 26 are moved via associated lever systems 31, 32 and the rocker arm 27 directly from the bearing journal 24 on which the rocker arm 20 engages. Rollers 33 to 36 are mounted on the rocker arms 25 to 27 and engage in a known manner in a pair of guide disks, not shown, which is arranged on each stub shaft 70 to 72, 76 of the friction rollers 7, 9, 12, 15.

Das erfindungsgemäße Zwischengetriebe mit veränderbarer Phasenlage von Antrieb zu Abtrieb läßt sich durch Austausch des Kurbeltriebes 18 gegen ein in der Zeichnung nicht dargestelltes, bekanntes Kurvenscheibengetriebe auch zur Umwandlung einer Drehbewegung in die Pendelbewegung einer Heberwalze mit veränderlicher Phasenlage, z.B. in Farbwerken einsetzen. Hierzu wird die Kurvenscheibe am Sonnenrad 42 befestigt und deren Bewegung in bekannter Weise auf einen mit der Walzenachse der Heberwalze verbundenen, nicht dargestellten Rollenhebel übertragen.The intermediate gear according to the invention with a variable phase position from drive to output can be replaced by replacing the crank mechanism 18 with a known cam mechanism not shown in the drawing, also for converting a rotary movement into the pendulum movement of a lifting roller with a variable phase position, e.g. use in inking units. For this purpose, the cam disc is attached to the sun gear 42 and its movement is transmitted in a known manner to a roller lever (not shown) connected to the roller axis of the lifting roller.

Eine weitere Anwendungsmöglichkeit wäre die Steuerung von Schaltbewegungen von Teilen, z.B. die schrittweise Schaltung einer Duktorwalze in Farbwerken.Another application would be the control of switching movements of parts, e.g. the gradual switching of a duct roller in inking units.

Ganz allgemein ist das erfindungsgemäße kardanähnliche Zwischengetriebe für Anwendungsfälle mit großen Übersetzungen einsetzbar, in denen in extrem raumsparender Bauweise der Arbeitszeitpunkt einer mit dem Zwischengetriebe verbundenen Vorrichtung bei laufender Maschine verstellt werden soll, ohne durch die Verstellung den Ausschlag bzw. Hub der hin- und herschwingenden Bewegung zu beeinflussen.In general, the gimbal-type intermediate gear according to the invention can be used for applications with large ratios in which the working time of a device connected to the intermediate gear is to be adjusted while the machine is running in an extremely space-saving design, without the deflection or stroke of the oscillating movement being adjusted by the adjustment to influence.

BezugszeichenlisteReference symbol list

  • 1 Plattenzylinder1 plate cylinder
  • 2 Farbauftragwalze2 inking roller
  • 3 Farbauftragwalze3 inking roller
  • 4 Farbauftragwalze4 inking roller
  • 5 Farbauftragwalze5 inking roller
  • 6 Farbauftragwalze6 inking roller
  • 7 Reibwalze7 distribution roller
  • 8 Farbtransportwalze8 ink feed roller
  • 9 Reibwalze9 distribution roller
  • 10 Farbtransportwalze10 ink transport roller
  • 11 Abzweigwalze11 branch roller
  • 12 Reibwalze12 distribution roller
  • 13 Abzweigwalze13 branch roller
  • 14 Farbzuführwalze14 ink feed roller
  • 15 Reibwalze15 distribution roller
  • 16 Heberwalze16 lifter roller
  • 17 Duktorwalze17 duct roller
  • 18 Kurbeltrieb18 crank mechanism
  • 19 Abtriebsachse19 output axis
  • 20 Schwinghebel20 rocker arms
  • 21 Schraube21 screw
  • 22 Nut22 groove
  • 23 Nutenstein23 sliding block
  • 24 Lagerzapfen24 journals
  • 25 Kipphebel25 rocker arms
  • 26 Kipphebel26 rocker arm
  • 27 Kipphebel27 rocker arm
  • 28 Lagerzapfen28 journals
  • 29 Lagerzapfen29 journals
  • 30 Stift30 pen
  • 31 Hebelsystem31 lever system
  • 32 Hebelsystem32 lever system
  • 33 Rolle33 roll
  • 34 Rolle34 roll
  • 35 Rolle35 roll
  • 36 Rolle36 roll
  • 37 Antriebswelle37 drive shaft
  • 38 Zentralzahnrad38 central gear
  • 39 Wellenzapfen39 shaft journals
  • 40 exzentrischer Zapfen40 eccentric pins
  • 41 Maschinengestell41 machine frame
  • 42 Sonnenrad42 sun gear
  • 43 Planetenrad43 planet gear
  • 44 Zahnkranz44 ring gear
  • 45 Zahnritzel45 sprockets
  • 46 Verstellwelle46 adjusting shaft
  • 47 Innenverzahnung47 internal teeth
  • 48 Scheibe48 disc
  • 49 Zapfenmitte49 center of pin
  • 50 Rolle50 roll
  • 51 Rolle51 roll
  • 52 Rolle52 roll
  • 53 Achse53 axis
  • 54 Achse54 axis
  • 55 Achse55 axis
  • 56 Antriebsachse56 drive axle
  • 57 Kreisbahn57 circular path
  • 58 Kreisbahn58 circular path
  • 59 Kreisbahn59 circular path
  • 60 Kreisbahn60 circular path
  • 61 Bohrung61 hole
  • 62 Bohrung62 hole
  • 63 Bohrung63 hole
  • 64 Achse64 axis
  • 65 Achse65 axis
  • 66 Achse66 axis
  • 67 Kreisbahn67 circular path
  • 68 Kreisbahn68 circular path
  • 69 Kreisbahn69 circular path
  • 70 Achsstummel70 stub axles
  • 71 Achsstummel71 stub axles
  • 72 Achsstummel72 stub axles
  • 73 Feuchtwerkswalzen73 dampening rollers
  • 74 Feuchtwerkswalzen74 dampening unit rollers
  • 75 Halteplatte75 holding plate
  • 76 Achsstummel76 stub axles

Claims (3)

1. Intermediate drive for transfer of a rotational movement into the to and fro movement of a part mounted outside the drive which is to be driven with variable phase position from drive to drive, particularly a roller in inking and/or damping units of offset printing presses in which, on an eccentric pin of a drive shaft, a planet wheel sits while, on the coaxial roller pin of the drive shaft, a toothed ring is rotatably arranged which is adjustable by means of a toothing provided on the external contour and a pinion or the like engaging in this toothing, which is seated on an adjusting shaft rotationally mounted in the machine frame, which can be rotated and locked from outside by hand or by motor with machine running, characterised in that,
on the toothed ring (44) at a distance a from the drive axle (56) of the drive shaft (37) bores (61 to 63) are located which are arranged offset by the same angular amount α relative to one another, that the planet wheel (43) is seated on a reduced collar of a disc (48) which is mounted rotatably on the eccentric pin (40) of the drive shaft (37), that against the disc (48) there are located at a distance a about the centre of the pin (49) several rollers (50 to 52) which likewise are arranged offset relative to one another by the same angular amount α, and which roll off on the inner surface of the bores (61 to 63), that furthermore the distance of the axes (64 to 66) of the bores (61 to 63) to the axes (53 to 55) of the rollers (50 to 52) is chosen equal to the distance e of the drive axis (56) of the drive shaft (37) to the centre of the pin (49) of the eccentric pin (40) and that flush to the toothed ring (44) a sun wheel (42) provided with an interior toothing (47) is rotationally mounted as a drive output part in which the planet wheel (43) engages.
2. Intermediate drive according to Claim 1, characterised in that
for transfer of the rotational movement of the sun wheel (42) into the to and fro movement of vibrator rollers in the axial direction with variable stroke a slide block (23) is guided in a groove (22) of the sun wheel (42) and which can be adjusted and fixed by a screw (21) and that on the screw (21) via a bearing a rotating lever (20) is rotatably received, the movement of which can be transferred via coupling elements (24-29, 31-36) to the stub axle (70 to 72, 76) of the vibrator rollers (7, 9, 12, 15).
3. Intermediate drive according to Claim 1, characterised in that,
for transfer of the rotational movement of the sun wheel 42 into the pendulum movement of a vibrator roller, a cam disc is fixed to the front face of the circulating sun wheel (42) on which the roller of a roller lever connected with the roller axle rolls off.
EP89104455A 1988-05-03 1989-03-14 Intermediate drive for the transfer of a rotary motion to a reciprocating motion of a roller in the inking and/or damping unit of a rotary offset press Expired - Lifetime EP0340428B1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT89104455T ATE73050T1 (en) 1988-05-03 1989-03-14 INTERMEDIATE GEAR FOR TRANSMISSION OF ROTARY MOVEMENT INTO RECIPROCAL MOVEMENT OF A ROLLER IN INK AND/OR DAMPING UNITS OF OFFSET PRINTING MACHINES.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3814927 1988-05-03
DE3814927A DE3814927C1 (en) 1988-05-03 1988-05-03

Publications (3)

Publication Number Publication Date
EP0340428A2 EP0340428A2 (en) 1989-11-08
EP0340428A3 EP0340428A3 (en) 1990-01-10
EP0340428B1 true EP0340428B1 (en) 1992-03-04

Family

ID=6353443

Family Applications (1)

Application Number Title Priority Date Filing Date
EP89104455A Expired - Lifetime EP0340428B1 (en) 1988-05-03 1989-03-14 Intermediate drive for the transfer of a rotary motion to a reciprocating motion of a roller in the inking and/or damping unit of a rotary offset press

Country Status (7)

Country Link
US (1) US4914981A (en)
EP (1) EP0340428B1 (en)
JP (1) JP2557978B2 (en)
AT (1) ATE73050T1 (en)
BR (1) BR8902464A (en)
DE (2) DE3814927C1 (en)
ES (1) ES2030546T3 (en)

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Publication number Priority date Publication date Assignee Title
DE4032470A1 (en) * 1990-10-12 1992-04-30 Wifag Maschf DEVICE FOR CONTINUOUSLY ADJUSTING THE AXIAL FRICTION MOVEMENT OF FRICTION ROLLERS
DE4231260C2 (en) * 1992-09-18 1996-05-23 Heidelberger Druckmasch Ag Print drive for ink transport rollers of a rotary printing machine
DE19504426C2 (en) * 1995-02-10 2000-05-11 Heidelberger Druckmasch Ag Drive for friction rollers in the inking unit of rotary printing machines
DE29503966U1 (en) * 1995-03-08 1995-06-14 Roland Man Druckmasch Device for adjusting the trituration insert
DE19516087C2 (en) * 1995-05-03 2000-07-13 Koenig & Bauer Ag Inking unit for printing machines
DE19625083C1 (en) * 1996-06-22 1997-11-13 Koenig & Bauer Albert Ag Gear for adjusting offset printing machine drive phase
DE19756077A1 (en) * 1997-12-17 1999-06-24 Heidelberger Druckmasch Ag Method for operating a rotary printing press and device in a rotary printing press
DE10014853C2 (en) 2000-03-24 2002-02-07 Koenig & Bauer Ag Axial stroke roller
JP2007211905A (en) * 2006-02-09 2007-08-23 Seiko Precision Inc Reduction gear
DE102006035713B4 (en) * 2006-08-01 2013-09-05 manroland sheetfed GmbH Inking unit drive in a processing machine
DE102009001475B4 (en) * 2009-03-11 2011-05-12 Koenig & Bauer Aktiengesellschaft Printing unit of a printing machine with at least one printing unit
CN102501120A (en) * 2011-11-02 2012-06-20 田农 Method for adding change gears of existing lathe to replace imported pointing machine
DE102013015470A1 (en) * 2012-10-04 2014-04-10 Heidelberger Druckmaschinen Ag Printing machine for plano-graphic offset printing on sheet, has functional elements that are arranged on mutually different sides of axial center of roller, such that elements are moved in two mutually opposite working directions
CN106626722B (en) * 2016-09-19 2020-09-04 上海炫仁机械设备有限公司 Offset press with novel ink distributing mechanism and application thereof
DE102020105599A1 (en) * 2019-04-01 2020-10-01 Heidelberger Druckmaschinen Aktiengesellschaft Dampening system
JP6760674B1 (en) * 2019-09-05 2020-09-23 昌幸 池田 Gear transmission

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DE1248682B (en) * 1967-08-31 VEB Druckmaschmenwerk Planeta Radebeul Lifter gearboxes? N inking units of printing machines, in particular offset printing machines
US2548217A (en) * 1945-10-03 1951-04-10 Hoe & Co R Doctor blade reciprocating mechanism for intaglio printing machines
DE800264C (en) * 1948-10-02 1950-10-25 Maschf Augsburg Nuernberg Ag Stepless control of the deflection of a back and forth movement, especially for printing machines
GB926266A (en) * 1960-02-23 1963-05-15 Fichtel & Sachs Ag Improvements in or relating to eccentric gears
US3077159A (en) * 1961-02-10 1963-02-12 Samuel M Langston Co Variable stroke reciprocating mechanism
DE2228939A1 (en) * 1972-06-14 1974-01-03 Roland Offsetmaschf ADJUSTMENT FOR DISTRIBUTION ON PRINT MACHINES
US4235129A (en) * 1978-03-30 1980-11-25 Isamu Takasu Speed reduction mechanism
US4261228A (en) * 1978-12-13 1981-04-14 Eagan Joseph A Sen Stroke adjustment for reciprocating mechanism
DE3203803C1 (en) * 1982-02-04 1983-04-07 M.A.N.- Roland Druckmaschinen AG, 6050 Offenbach Drive device for the friction rollers of an inking and dampening unit of a rotary printing machine
DE3502863A1 (en) * 1985-01-29 1986-07-31 M.A.N.- Roland Druckmaschinen AG, 6050 Offenbach CHANGING DRIVE FOR THE FRICTION ROLLERS OF AT LEAST ONE INK OF A PRINTING UNIT OF AN OFFSET ROTATION PRINTING MACHINE

Also Published As

Publication number Publication date
ES2030546T3 (en) 1992-11-01
JP2557978B2 (en) 1996-11-27
ATE73050T1 (en) 1992-03-15
EP0340428A2 (en) 1989-11-08
US4914981A (en) 1990-04-10
DE58900892D1 (en) 1992-04-09
EP0340428A3 (en) 1990-01-10
BR8902464A (en) 1990-01-16
DE3814927C1 (en) 1989-12-14
JPH01317771A (en) 1989-12-22

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