EP0392205B1 - Rotary printing machine for sheets with several units for printing recto and recto-verso - Google Patents

Rotary printing machine for sheets with several units for printing recto and recto-verso Download PDF

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Publication number
EP0392205B1
EP0392205B1 EP90104860A EP90104860A EP0392205B1 EP 0392205 B1 EP0392205 B1 EP 0392205B1 EP 90104860 A EP90104860 A EP 90104860A EP 90104860 A EP90104860 A EP 90104860A EP 0392205 B1 EP0392205 B1 EP 0392205B1
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EP
European Patent Office
Prior art keywords
sheet
printing machine
gearwheel
machine according
fed rotary
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
EP90104860A
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German (de)
French (fr)
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EP0392205A2 (en
EP0392205A3 (en
Inventor
Willi Becker
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Heidelberger Druckmaschinen AG
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Heidelberger Druckmaschinen AG
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Publication of EP0392205A3 publication Critical patent/EP0392205A3/en
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
    • B41F—PRINTING MACHINES OR PRESSES
    • B41F21/00—Devices for conveying sheets through printing apparatus or machines
    • B41F21/10—Combinations of transfer drums and grippers
    • B41F21/106—Combinations of transfer drums and grippers for reversing sheets, e.g. for perfecting machine

Definitions

  • the invention relates to a sheet-fed rotary printing press with a plurality of printing units for straight printing and surface printing, in which a turning device with generic features is provided according to the preamble of patent claim 1.
  • the prior art for this invention results from DE-PS 26 20 392 and JP-Sho 63-53037.
  • the sheet that is fed through the printing units with the leading edge of the sheet in front of the printer is fed in the perfecting in the turning device with its front edge past the tangent point between a storage drum and a subsequent turning drum, and as soon as the trailing edge of the sheet has reached the mentioned tangent point, it is used by the reversing grippers the turning drum detected.
  • the front edge of the sheet is released by the grippers of the storage drum, so that the sheet is now fed to the next printing unit with the rear edge of the sheet ahead.
  • To set up the machine from face to face it is necessary to adjust a whole range of individual functions.
  • a gear pair arranged in the chain of the drive gearwheels consisting of a fixed gearwheel on the turning drum and an adjusting gearwheel, is provided concentrically to the turning drum axis, both of which can be locked together by clamping, in order to continuously adjust an angle of rotation between the printing units in front of the turning device and to enable the printing units behind the turning device, with electrical protection only permitting machine operation if the clamping is correct.
  • the gripper changeover is carried out according to DE-PS 26 20 392 by an actuator which can be axially displaced in the turning drum and which, by means of an eccentric which can be rotated by hand with a tool, between two end positions, one of which is the gripper position in face printing and the other is the gripper position in fine and Back pressure corresponds, is movable.
  • the end positions are generally not electrically protected.
  • the change of gripper requires climbing the machine and removing and re-attaching a cover in a special operation.
  • JP-Sho 63-53037 discloses a control shaft for the gripper changeover, which is guided concentrically out of the shaft of the turning drum on the drive side and can be rotated here by an attachable tool, the rotation of which causes the gripper changeover.
  • the gripper is changed either by lifting the drive roller for the grippers of the gripper set for gripping the front edge of the sheet from the drive curve controlling the gripper movement and lowering of the drive roller for the grippers of the set of grippers to detect the rear edge of the sheet on an associated control curve or vice versa or by moving the drive roller from one to another drive curve.
  • the invention has for its object to simplify, accelerate the changeover process on the turning device and, above all, to make it safer.
  • the invention solves this problem by training features according to the characterizing part of claim 1 in a sheet-fed rotary printing press with features according to the generic term.
  • a general idea of the invention is thus to combine and switch the gripper changeover from reversing gripper controls from straight printing to reversing gripper controls for perfecting with the printing unit adjustment required for changing the operating mode from straight printing to perfecting. This eliminates the need for a special operation for changing the gripper. At the same time the considerable advantage is achieved that the gripper changeover falls under the electrical protection of the printing unit adjustment. This considerably reduces set-up times, simplifies machine operation and increases the safety of machine operation.
  • a mechanical design is preferred, in which a transmission gear is either by means of a Gearing or by means of a lever transmission causes the relative movements of the adjusting gear relative to the fixed gear in a certain angle of rotation range on the selector shaft to convert the gripper control.
  • the claims 4 to 8 contain training features of an advantageous mechanical implementation of the inventive concept, in which on the front side of the turning drum, in particular on the front side of the turning drum pin on the drive side, a toothed segment is pivotally mounted about an axis parallel to the drum axis, the toothing of which in a Switching shaft arranged pinion engages, and which is pivoted by a driver link on the adjusting gear only in a predetermined angular range. It is thereby achieved that the adjusting gear can be rotated as desired beyond the angular range required for the gripper reversal in order to carry out the further printing unit adjustment in accordance with the format sizes to be processed.
  • claims 9 to 11 relate to a structural design in which the relative movement between the adjusting gear and the fixed gear is transmitted in a predetermined angular range by means of a lever gear to the selector shaft and is converted into rotary motion by the latter.
  • Claims 12 to 14 relate to advantageous design features for converting the rotary movement of the control shaft into axial movements of an actuator for gripper changeover.
  • claims 15 to 18 contain the combination of the features of the invention with electrical switching elements either for the gripper switch and / or for the electrical protection of the turning device.
  • the turning drum 1 is rotatably mounted both on the operating side (not shown) and on the drive side shown with drum pins 2 in the frame 4 of the machine.
  • the grippers, not shown in the drawing, are arranged in a pit 3 on the turning drum 1 which is open to the outside and has an axis-parallel configuration.
  • a fixed gear 6 is connected to the end face of the bearing journal 2 by screws 5 and engages with its toothing in a gear 7 of the drive chain of the gears.
  • an adjusting gear 10 is mounted on a shoulder 9, which can be firmly clamped to the fixed gear 6 and the teeth of which mesh with another gear 11 in the drive chain of the gears.
  • the adjusting gear 10 and the fixed gear 6 are clamped, for example, by a clamping piece 12 which can be screwed against the fixed gear 6 with screws 13 and presses with a collar edge 14 against the outer side surface of the adjusting gear 10. Since the clamping between the adjusting gear 10 and the fixed gear 6 is not the subject of the invention, only an example of the design of such a clamping is to be given herewith.
  • the movement of the grippers movably mounted in the pit 3 is controlled by a cam roller 16 via control levers and a bridge 15.
  • the cam roller lies in front printing against a drive curve 17 fastened to the frame 4 and in perfecting against a drive curve 18 also fastened to the frame.
  • the cam roller 16 can be converted from the drive curve 17 to the drive curve 18 and back.
  • an eccentric 19 is mounted in the reversing drum shaft 1, which engages with its eccentric pin 20 in a bearing on the bridge 15.
  • the eccentric 19 is rotated via an angular gear by the selector shaft 21, which is rotatably mounted in the turning drum shaft 1 eccentrically to its central longitudinal axis 8 and with its free end passes through the fixed gear 6 and the clamping piece 12.
  • the outwardly directed free end of the control shaft 21 is connected by a transmission gear to the adjusting gear 10, so that at a printing unit adjustment in which the angle of rotation of the adjustment gear 10 relative to the fixed gear 6 is changed, the gripper control is simultaneously changed over the control shaft 21.
  • this transmission gear consists of a toothed segment 22, which is eccentric to the central longitudinal axis 8 on a drum-proof part, for example on the pressure piece 12, the fixed gear 6 or the like, around a pin 23 aligned parallel to the axis 8 is pivotable and engages with its toothing in the toothing of a pinion 24 fastened on the free end of the control shaft 21.
  • the toothed segment is designed as a double lever and carries on its arm opposite the toothing a driver pin 25 which interacts with a driver link 26 which is fastened to the adjusting gear 10 and has a groove which is delimited by walls of different heights.
  • the eccentric mounting of the control shaft 21 in the turning drum 1 ensures that the groove of the driving link 26 releases the driving pin 25 after a certain angle of rotation. Since the driver pin 25 when pivoting the Tooth segment 22 moves about the axis of the pin 23, it approaches the central longitudinal axis 8 on its path of movement, while the driver link 26 moves at the same distance from the central longitudinal axis. The lower limitation of the groove of the driving link releases the driving pin at a certain point. On the way back, the longer limitation of the groove ensures that the driver pin 25 is returned to the starting position.
  • the driving link 26 attached to the adjusting gear 10 can also be adjustable in the circumferential direction of the adjusting gear.
  • the formation of the driving link 26 in a special component is advantageous, which is screwed to the adjusting gear 10. Since the parts of the transmission gear transmitting the relative movement between the adjusting gear and the fixed gear remain in frictional engagement, the gripper changeover can be secured simultaneously via the electrical securing of the clamping between the adjusting gear and the fixed gear.
  • the gripper changeover is carried out by stopping the cam roller 16, for example by holding it in an apex position of the drive curve, or by lifting the cam roller 16 off the associated drive curve 17, so that a pivoting movement is sufficient for the gripper changeover .
  • the switching shaft 21 is fixedly connected at its inner end to a lever 27 which is in a lateral recess 28 in the Turning drum 1 led out and cooperates with a component on the gripper bridge shaft in such a way that it supports the gripper shaft in the rest position of the gripper in the position shown.
  • the cam roller 16 is lifted from the drive cam 17 and held in an apex position by a rotary movement of the control shaft 21, so that the grippers remain in a rest position which does not impede machine operation.
  • This also allows a simplification of the transmission gear for the transmission of the relative movement of the adjusting gear 10 relative to the fixed gear 6.
  • a lever 29 is connected in a rotationally fixed manner to the free end of the selector shaft 21 and is biased by a spring 30 against a stop 31 on the adjusting gear 10.
  • Another stop 32 is arranged drum-tight. When adjusting the printing unit, the stop 31 moves with the adjusting gear 10 relative to the fixed gear 6 and other drum-proof parts.
  • the tensioning force of the spring 30 overcomes the torque required for the gripper changeover in the control shaft 21 and initially holds the lever 29 against the stop 31 until the lever 29 comes to rest against the stop 32. On this former part of the path, the gripper changeover takes place in the manner described. On the way there is an adaptation to smaller formats in particular.
  • the lever 29 is returned from the stop 31 to the starting position.
  • a compression spring or another spring element can also be provided.
  • the exemplary embodiment in FIGS. 5 and 6 also shows instead of a simple rigid lever Stops a lever transmission from an articulated toggle.
  • This toggle lever which is formed from two tabs 34 and 35 which are connected to one another in a joint 33, is fastened at one end in a rotationally fixed manner on the selector shaft 21 and at the other end in a rotatable manner on a bearing pin 36 on the adjusting gear 10.
  • a rotary movement is transmitted to the selector shaft 21, by means of which the gripper control is changed over the lever 27, so that the cam roller 16 is lifted off the drive cam 17.
  • Such a design can preferably be used if the movement component for gripper changeover is not limited.
  • the coupling of the printing unit adjustment to the gripper changeover takes place essentially by the same means that were described for FIGS. 1 and 2.
  • the selector shaft acts on a link control, by means of which, in contrast to the illustration in FIGS. 1, 3 and 5, the cam roller 16 is not implemented, but rather the drive cams 17 and 18 are axially displaced, so that they also interact alternately with the cam roller 16 .
  • the lever 27 described in the examples in FIGS. 3 and 5 on the inner end of the selector shaft 21 is hereafter equipped with a head piece 37 — advantageously with a rotatably mounted roller that forms the head piece — which engages in a link guide 38 with an axial offset.
  • This link guide 38 is arranged in an axially displaceable component 39 on which the drive curves 17 and 18 are formed.
  • the axial offset of the link guide 38 results from the illustration in FIG. 9.
  • Lever 27 is an axial displacement of component 39 according to the axial offset of the link guide.
  • the transmission gear from the components 22 to 26 is designed so that the lever 27 with the head piece 37 performs a predetermined pivoting (in the example shown, it is approximately 180 degrees) and is thus in the end positions of the gripper changeover in a recessed position within the recess 28 is located in the drum pin 2.
  • the link guide is provided at the ends with sections that run in a radial plane in order to enable the lever 27 with the head piece 37 to be immersed and immersed in the link guide without axial displacement of the component 39.
  • An axial displacement thus only takes place in the area of the oblique transition of the two parallel parts of the link guide, as can be clearly seen from the illustration in FIG. 9.
  • FIGS 10 to 13 show a constructive design form of the inventive concept, in which electrical switching elements are used.
  • the rocker arm 40 shown in Figure 10 is used to actuate an electrical switch. It is moved by a switching pin 42, which is guided in the adjusting gear 10 parallel to the central longitudinal axis 8 and is loaded by a spring 41 against the fixed gear 6. In the end positions of the Gripper switch engages this switching pin 42 with a tapered tip in recesses 43 on the side surface of the fixed gear 6. As soon as an adjustment of the angle of rotation of the adjusting gear 10 with respect to the fixed gear 6 takes place, the switching pin 42 is pressed out of the recess 43 assigned to an end position due to the conical configuration of its tip and moved axially against the rocker arm 40.
  • This can be used both for the switching of an electrical fuse, and can also be arranged in the circuit of an electrical adjusting device for the gripper changeover or other necessary changes. Since the rocker arm 40 is fixed in position, the duty cycle of the actuator can be determined by a predetermined width of the rocker arm. After the gripper switch, the switching pin 42 can dip into a longer ring segment-shaped recess 43, so that the circuit is interrupted again.
  • the rocker arm 40 can also act on switching elements for hydraulically or pneumatically moved actuators, make the necessary changes or initiate such changes.

Landscapes

  • Supply, Installation And Extraction Of Printed Sheets Or Plates (AREA)
  • Inking, Control Or Cleaning Of Printing Machines (AREA)
  • Rotary Presses (AREA)
  • Discharge By Other Means (AREA)

Description

Die Erfindung bezieht sich auf eine Bogenrotationsdruckmaschine mit mehreren Druckwerken zum Schöndruck und Schön- und Widerdruck, bei der eine Wendeeinrichtung mit Gattungsmerkmalen nach dem Oberbegriff des Patentanspruches 1 vorgesehen ist.The invention relates to a sheet-fed rotary printing press with a plurality of printing units for straight printing and surface printing, in which a turning device with generic features is provided according to the preamble of patent claim 1.

Der Stand der Technik zu dieser Erfindung ergibt sich aus der DE-PS 26 20 392 und der JP-Sho 63-53037. Der beim Schöndruck mit der Bogenvorderkante voraus durch die Druckwerke geführte Bogen wird im Schön- und Widerdruck in der Wendeeinrichtung mit seiner Vorderkante am Tangentenpunkt zwischen einer Speichertrommel und einer nachfolgenden Wendetrommel vorbeigeführt, und sobald die Bogenhinterkante den erwähnten Tangentenpunkt erreicht hat, wird sie von den Wendegreifern der Wendetrommel erfaßt. Gleichzeitig erfolgt die Freigabe der Bogenvorderkante von den Greifern der Speichertrommel, so daß der Bogen nunmehr mit der Bogenhinterkante voraus dem nächsten Druckwerk zugeführt wird. Für die Einrichtung der Maschine von Schöndruck auf Schön- und Widerdruck ist die Verstellung einer ganzen Reihe von Einzelfunktionen erforderlich. An der Wendetrommel erfolgt eine Druckwerksverstellung zur Anpassung an die durch die Bogenwendung veränderte Lage der Bogenkante und in einem eigenen Arbeitsgang eine Greiferumstellung von der Vorderkantenerfassung auf die Hinterkantenerfassung des Bogens. In gleicher Weise muß eine Umstellung erfolgen, wenn die Maschine nur im Schöndruck arbeiten soll.The prior art for this invention results from DE-PS 26 20 392 and JP-Sho 63-53037. The sheet that is fed through the printing units with the leading edge of the sheet in front of the printer is fed in the perfecting in the turning device with its front edge past the tangent point between a storage drum and a subsequent turning drum, and as soon as the trailing edge of the sheet has reached the mentioned tangent point, it is used by the reversing grippers the turning drum detected. At the same time, the front edge of the sheet is released by the grippers of the storage drum, so that the sheet is now fed to the next printing unit with the rear edge of the sheet ahead. To set up the machine from face to face, it is necessary to adjust a whole range of individual functions. On the turning drum there is a printing unit adjustment to adapt to the position of the sheet edge changed by the sheet turning and in a separate operation a gripper changeover from the front edge detection to the rear edge detection of the Bow. In the same way, a change must be made if the machine should only work in face printing.

Für die Druckwerkeverstellung ist nach dem genannten Stand der Technik ein in der Kette der Antriebszahnräder angeordnetes Zahnradpaar aus einem Festzahnrad an der Wendetrommel und einem Verstellzahnrad konzentrisch zur Wendetrommelachse vorgesehen, die beide durch Klemmung miteinander verriegelbar sind, um stufenlos eine Drehwinkelverstellung zwischen den Druckwerken vor der Wendeeinrichtung und den Druckwerken hinter der Wendeeinrichtung zu ermöglichen, wobei eine elektrische Absicherung den Maschinenbetrieb nur bei einwandfreier Klemmung gestattet.For the printing unit adjustment, a gear pair arranged in the chain of the drive gearwheels, consisting of a fixed gearwheel on the turning drum and an adjusting gearwheel, is provided concentrically to the turning drum axis, both of which can be locked together by clamping, in order to continuously adjust an angle of rotation between the printing units in front of the turning device and to enable the printing units behind the turning device, with electrical protection only permitting machine operation if the clamping is correct.

Die Greiferumstellung erfolgt nach der DE-PS 26 20 392 durch ein axial in der Wendetrommel verschiebbares Stellglied, welches mittels eines von Hand mit einem Werkzeug verdrehbaren Exzenters zwischen zwei Endlagen, von denen eine der Greiferstellung im Schöndruck und die andere der Greiferstellung im Schön- und Widerdruck entspricht, beweglich ist. Eine elektrische Absicherung der Endlagen erfolgt regelmäßig nicht. Die Greiferumstellung erfordert eine Besteigung der Maschine, sowie das Entfernen und Wiederanbringen einer Abdeckung in einem besonderen Arbeitsgang.The gripper changeover is carried out according to DE-PS 26 20 392 by an actuator which can be axially displaced in the turning drum and which, by means of an eccentric which can be rotated by hand with a tool, between two end positions, one of which is the gripper position in face printing and the other is the gripper position in fine and Back pressure corresponds, is movable. The end positions are generally not electrically protected. The change of gripper requires climbing the machine and removing and re-attaching a cover in a special operation.

Alternativ ist aus der JP-Sho 63-53037 eine antriebsseitig aus der Welle der Wendetrommel konzentrisch herausgeführte und hier durch ein aufsetzbares Werkzeug verdrehbare Schaltwelle für die Greiferumstellung bekannt, deren Drehung die Greiferumstellung bewirkt.As an alternative, JP-Sho 63-53037 discloses a control shaft for the gripper changeover, which is guided concentrically out of the shaft of the turning drum on the drive side and can be rotated here by an attachable tool, the rotation of which causes the gripper changeover.

Die Greiferumstellung erfolgt entweder durch das Abheben der Antriebsrolle für die Greifer des Greifersatzes zur Erfassung der Bogenvorderkante von der die Greiferbewegung steuernden Antriebskurve und Absenken der Antriebsrolle für die Greifer des Greifersatzes zur Erfassung der Bogenhinterkante auf eine zugeordnete Steuerkurve bzw. umgekehrt oder durch Verschieben der Antriebsrolle von einer auf eine andere Antriebskurve.The gripper is changed either by lifting the drive roller for the grippers of the gripper set for gripping the front edge of the sheet from the drive curve controlling the gripper movement and lowering of the drive roller for the grippers of the set of grippers to detect the rear edge of the sheet on an associated control curve or vice versa or by moving the drive roller from one to another drive curve.

Der Erfindung liegt die Aufgabe zugrunde, den Umstellvorgang an der Wendeeinrichtung zu vereinfachen, zu beschleunigen und vor allem auch sicherer zu gestalten.The invention has for its object to simplify, accelerate the changeover process on the turning device and, above all, to make it safer.

Die Erfindung löst diese Aufgabe durch Ausbildungsmerkmale nach dem Kennzeichen des Patentanspruches 1 bei einer Bogenrotationsdruckmaschine mit Merkmalen nach dem Gattungsbegriff.The invention solves this problem by training features according to the characterizing part of claim 1 in a sheet-fed rotary printing press with features according to the generic term.

Ein allgemeiner Erfindungsgedanke besteht somit darin, die Greiferumstellung von Wendegreifersteuerungen von Schöndruck auf Wendegreifersteuerungen für Schön- und Widerdruck mit der für einen Betriebsartwechsel von Schöndruck auf Schön- und Widerdruck erforderlichen Druckwerksverstellung zu kombinieren und gleichzeitig zu schalten. Damit entfällt ein besonderer Arbeitsgang für die Greiferumstellung. Gleichzeitig wird der erhebliche Vorteil erreicht, daß die Greiferumstellung unter die elektrische Absicherung der Druckwerksverstellung fällt. Dadurch werden Rüstzeiten beträchtlich reduziert, die Maschinenbedienung vereinfacht und die Sicherheit des Maschinenbetriebes erhöht.A general idea of the invention is thus to combine and switch the gripper changeover from reversing gripper controls from straight printing to reversing gripper controls for perfecting with the printing unit adjustment required for changing the operating mode from straight printing to perfecting. This eliminates the need for a special operation for changing the gripper. At the same time the considerable advantage is achieved that the gripper changeover falls under the electrical protection of the printing unit adjustment. This considerably reduces set-up times, simplifies machine operation and increases the safety of machine operation.

Prinzipiell kann der Erfindungsgedanke auch dadurch realisiert werden, daß ein am Verstellzahnrad angeordnetes Element entsprechend dem Kennzeichen des Patentanspruches vorgesehen ist.In principle, the concept of the invention can also be realized in that an element arranged on the adjusting gear is provided in accordance with the characterizing part of the patent claim.

Bevorzugt wird eine mechanische konstruktive Ausgestaltung, bei der ein Übersetzungsgetriebe entweder mittels einer Verzahnung oder durch eine Hebelübersetzung die Relativbewegungen des Verstellzahnrades gegenüber dem Festzahnrad in einem bestimmten Drehwinkelbereich auf die Schaltwelle zur Umstellung der Greifersteuerung bewirkt.A mechanical design is preferred, in which a transmission gear is either by means of a Gearing or by means of a lever transmission causes the relative movements of the adjusting gear relative to the fixed gear in a certain angle of rotation range on the selector shaft to convert the gripper control.

Die Ansprüche 4 bis 8 enthalten Ausbildungsmerkmale einer vorteilhaften mechanischen Umsetzung des Erfindungsgedankens, bei der an der Stirnseite der Wendetrommel, insbesondere an der Stirnseite des Wendetrommelzapfens auf der Antriebsseite, ein Zahnsegment um eine Achse parallel zur Trommelachse schwenkbar gelagert ist, dessen Verzahnung in ein auf der Schaltwelle angeordnetes Ritzel eingreift, und welches durch eine Mitnehmerkulisse am Verstellzahnrad nur in einem vorbestimmten Winkelbereich verschwenkt wird. Dadurch wird erreicht, daß das Verstellzahnrad über den für die Greiferumsteuerung erforderlichen Winkelbereich hinaus beliebig verdreht werden kann, um die weitere Druckwerksverstellung entsprechend den zu verarbeitenden Formatgrößen durchzuführen.The claims 4 to 8 contain training features of an advantageous mechanical implementation of the inventive concept, in which on the front side of the turning drum, in particular on the front side of the turning drum pin on the drive side, a toothed segment is pivotally mounted about an axis parallel to the drum axis, the toothing of which in a Switching shaft arranged pinion engages, and which is pivoted by a driver link on the adjusting gear only in a predetermined angular range. It is thereby achieved that the adjusting gear can be rotated as desired beyond the angular range required for the gripper reversal in order to carry out the further printing unit adjustment in accordance with the format sizes to be processed.

Die Ausbildungsmerkmale der Ansprüche 9 bis 11 betreffen eine konstruktive Ausbildung, bei der die Relativbewegung zwischen dem Verstellzahnrad und dem Festzahnrad in einem vorbestimmten Winkelbereich mittels eines Hebelgetriebes auf die Schaltwelle übertragen und durch diese in Drehbewegung umgesetzt wird.The training features of claims 9 to 11 relate to a structural design in which the relative movement between the adjusting gear and the fixed gear is transmitted in a predetermined angular range by means of a lever gear to the selector shaft and is converted into rotary motion by the latter.

Die Ansprüche 12 bis 14 betreffen vorteilhafte Konstruktionsmerkmale für die Umsetzung der Drehbewegung der Schaltwelle in axiale Bewegungen eines Stellgliedes zur Greiferumstellung. Schließlich enthalten die Ansprüche 15 bis 18 die Kombination der Erfindungsmerkmale mit elektrischen Schaltelementen entweder für die Greiferumstellung und/oder für die elektrische Absicherung der Wendeeinrichtung.Claims 12 to 14 relate to advantageous design features for converting the rotary movement of the control shaft into axial movements of an actuator for gripper changeover. Finally, claims 15 to 18 contain the combination of the features of the invention with electrical switching elements either for the gripper switch and / or for the electrical protection of the turning device.

Auf der Zeichnung sind mehrere Ausführungsbeispiele bevorzugter Ausgestaltungen dargestellt.Several exemplary embodiments of preferred configurations are shown in the drawing.

Es zeigen:

Figur 1
ein Ausführungsbeispiel in einem Schnitt in einer Achshsebene durch das antriebsseitige Ende einer Wendetrommel,
Figur 2
eine Stirnansicht zu Figur 1,
Figur 3
ein anderes Ausführungsbeispiel in einem Schnitt entsprechend Figur 1,
Figur 4
eine Stirnansicht zu Figur 3,
Figur 5
ein weiteres Ausführungsbeispiel in einem Schnitt entsprechend Figur 1,
Figur 6
eine Stirnansicht zu Figur 5,
Figur 7
einen Schnitt entsprechend Figur 1, jedoch mit anderer Umsetzung der Schaltwellendrehung in eine lineare Axialbewegung,
Figur 8
einen Schnitt nach der Linie VIII - VIII in Figur 7,
Figur 9
eine Teildraufsicht zu Figur 8,
Figur 10
ein Ausführungsbeispiel mit elektrischen Schaltgliedern in einem Schnitt entsprechend Figur 1,
Figur 11
eine Stirnansicht zu Figur 10,
Figuren 12 u. 13
Teilschnitte nach der Linie XII - XII in Figur 11 bei unterschiedlichen Drehlagen der Zahnräder des Zahnradpaares.
Show it:
Figure 1
1 shows an exemplary embodiment in a section in an axis plane through the drive-side end of a turning drum,
Figure 2
2 shows a front view of FIG. 1,
Figure 3
another embodiment in a section corresponding to Figure 1,
Figure 4
3 shows a front view of FIG. 3,
Figure 5
another embodiment in a section corresponding to Figure 1,
Figure 6
5 shows an end view of FIG. 5,
Figure 7
2 shows a section corresponding to FIG. 1, but with a different conversion of the shift shaft rotation into a linear axial movement,
Figure 8
7 shows a section along the line VIII-VIII in FIG. 7,
Figure 9
8 shows a partial top view of FIG. 8,
Figure 10
1 shows an exemplary embodiment with electrical switching elements in a section corresponding to FIG. 1,
Figure 11
10 shows a front view of FIG. 10,
Figures 12 u. 13
Partial sections along the line XII - XII in Figure 11 at different rotational positions of the gears of the gear pair.

In den zur Erläuterung der Erfindungsmerkmale dargestellten Beispielen ist die Wendetrommel 1 sowohl auf der nicht dargestellten Bedienseite als auch auf der dargestellten Antriebsseite mit Trommelzapfen 2 in dem Gestell 4 der Maschine drehbar gelagert. Die auf der Zeichnung nicht dargestellten Greifer sind in einer nach außen offenen achsparallel verlaufenden Grube 3 an der Wendetrommel 1 angeordnet. Mit der Stirnseite des Lagerzapfens 2 ist durch Schrauben 5 ein Festzahnrad 6 verbunden, welches mit seiner Verzahnung in ein Zahnrad 7 der Antriebskette der Zahnräder eingreift. Konzentrisch zu diesem Festzahnrad und zur Längsachse 8 der Wendetrommel 1 ist auf einem Ansatz 9 ein Verstellzahnrad 10 gelagert, welches mit dem Festzahnrad 6 fest verklemmbar ist und dessen Verzahnung mit einem weiteren Zahnrad 11 in der Antriebskette der Zahnräder in Eingriff steht. Die Klemmung des Verstellzahnrades 10 und des Festzahnrades 6 erfolgt beispielsweise durch ein Klemmstück 12, welches mit Schrauben 13 gegen das Festzahnrad 6 schraubbar ist und mit einem Kragenrand 14 gegen die äußere Seitenfläche des Verstellzahnrades 10 drückt. Da die Klemmung zwischen dem Verstellzahnrad 10 und dem Festzahnrad 6 nicht Gegenstand der Erfindung ist, soll hiermit lediglich ein Beispiel für die konstruktive Ausbildung einer solchen Klemmung gegeben werden.In the examples shown to explain the features of the invention, the turning drum 1 is rotatably mounted both on the operating side (not shown) and on the drive side shown with drum pins 2 in the frame 4 of the machine. The grippers, not shown in the drawing, are arranged in a pit 3 on the turning drum 1 which is open to the outside and has an axis-parallel configuration. A fixed gear 6 is connected to the end face of the bearing journal 2 by screws 5 and engages with its toothing in a gear 7 of the drive chain of the gears. Concentric to this fixed gear and to the longitudinal axis 8 of the turning drum 1, an adjusting gear 10 is mounted on a shoulder 9, which can be firmly clamped to the fixed gear 6 and the teeth of which mesh with another gear 11 in the drive chain of the gears. The adjusting gear 10 and the fixed gear 6 are clamped, for example, by a clamping piece 12 which can be screwed against the fixed gear 6 with screws 13 and presses with a collar edge 14 against the outer side surface of the adjusting gear 10. Since the clamping between the adjusting gear 10 and the fixed gear 6 is not the subject of the invention, only an example of the design of such a clamping is to be given herewith.

Die Bewegung der in der Grube 3 beweglich gelagerten Greifer wird über Steuerhebel und eine Brücke 15 durch eine Kurvenrolle 16 gesteuert. Die Kurvenrolle liegt im Schöndruck gegen eine am Gestell 4 befestigte Antriebskurve 17 und im Schön- und Widerdruck gegen eine gleichfalls am Gestell befestigte Antriebskurve 18. Durch axiale Verschiebung der Brücke 15 kann die Kurvenrolle 16 von der Antriebskurve 17 auf die Antriebskurve 18 und zurück umgesetzt werden. Für die axiale Verschiebung der Brücke 15 ist im Beispiel der Figuren 1 und 2 in der Wendetrommelwelle 1 ein Exzenter 19 gelagert, der mit seinem Exzenterzapfen 20 in ein Lager an der Brücke 15 eingreift. Die Verdrehung des Exzenters 19 erfolgt über ein Winkelgetriebe durch die Schaltwelle 21, die in der Wendetrommelwelle 1 exzentrisch zu deren Mittellängsachse 8 drehbar gelagert ist und mit ihrem freien Ende das Festzahnrad 6 und das Klemmstück 12 durchsetzt. Das nach außen geführte freie Ende der Schaltwelle 21 ist durch ein Übersetzungsgetriebe mit dem Verstellzahnrad 10 verbunden, so daß bei einer Druckwerksverstellung, bei der der Drehwinkel des Verstellzahnrades 10 gegenüber dem Festzahnrad 6 verändert wird, gleichzeitig eine Umstellung der Greifersteuerung über die Schaltwelle 21 erfolgt.The movement of the grippers movably mounted in the pit 3 is controlled by a cam roller 16 via control levers and a bridge 15. The cam roller lies in front printing against a drive curve 17 fastened to the frame 4 and in perfecting against a drive curve 18 also fastened to the frame. By axial displacement of the Bridge 15, the cam roller 16 can be converted from the drive curve 17 to the drive curve 18 and back. For the axial displacement of the bridge 15 in the example of FIGS. 1 and 2, an eccentric 19 is mounted in the reversing drum shaft 1, which engages with its eccentric pin 20 in a bearing on the bridge 15. The eccentric 19 is rotated via an angular gear by the selector shaft 21, which is rotatably mounted in the turning drum shaft 1 eccentrically to its central longitudinal axis 8 and with its free end passes through the fixed gear 6 and the clamping piece 12. The outwardly directed free end of the control shaft 21 is connected by a transmission gear to the adjusting gear 10, so that at a printing unit adjustment in which the angle of rotation of the adjustment gear 10 relative to the fixed gear 6 is changed, the gripper control is simultaneously changed over the control shaft 21.

Nach dem Ausführungsbeispiel in den Figuren 1 und 2 besteht dieses Übersetzungsgetriebe aus einem Zahnsegment 22, welches exzentrisch zu der Mittellängsachse 8 an einem trommelfesten Teil, zum Beispiel an dem Druckstück 12, dem Festzahnrad 6 oder dergleichen, um einen parallel zur Achse 8 ausgerichteten Zapfen 23 schwenkbar ist und mit seiner Verzahnung in die Verzahnung eines auf dem freien Ende der Schaltwelle 21 befestigten Ritzels 24 eingreift. Das Zahnsegment ist als Doppelhebel ausgebildet und trägt an seinem der Verzahnung gegenüberliegenden Arm einen Mitnehmerzapfen 25, der mit einer Mitnehmerkulisse 26 zusammenwirkt, die an dem Verstellzahnrad 10 befestigt ist und eine Auskehlung aufweist, die durch Wandungen unterschiedlicher Höhe begrenzt wird. Durch die exzentrische Lagerung der Schaltwelle 21 in der Wendetrommel 1 wird erreicht, daß die Kehlung der Mitnehmerkulisse 26 den Mitnehmerzapfen 25 nach einem bestimmten Drehwinkel freigibt. Da der Mitnehmerzapfen 25 bei Verschwenkung des Zahnsegments 22 sich um die Achse des Zapfens 23 bewegt, nähert er sich auf seiner Bewegungsbahn der Mittellängsachse 8, während die Mitnehmerkulisse 26 sich mit gleichem Abstand von der Mittellängsachse bewegt. Die niedrigere Begrenzung der Kehlung der Mitnehmerkulisse gibt an einer bestimmten Stelle den Mitnehmerzapfen frei. Auf dem Rückweg wird durch die längere Begrenzung der Kehlung dafür gesorgt, daß der Mitnehmerzapfen 25 in die Ausgangslage zurückgeführt wird. Durch eine geeignete Wahl der Zahnradübersetzung und des Zahnkreisabstandes des Zahnsegmentes von der Schwenkachse des Zapfens 23 im Verhältnis zum Abstand des Mitnehmerzapfens 25 von der gleichen Achse wird erreicht, daß bei einer Druckwerksumstellung in einem vorbestimmten Winkelbereich der Relativbewegung des Verstellzahnrades gegenüber dem Festzahnrad eine sichere Greiferumstellung erfolgt. Die an dem Verstellzahnrad 10 befestigte Mitnehmerkulisse 26 kann in Umfangsrichtung des Verstellzahnrades ebenfalls einstellbar sein. Zu diesem Zweck ist die Ausbildung der Mitnehmerkulisse 26 in einem besonderen Bauteil vorteilhaft, welches mit dem Verstellzahnrad 10 verschraubt wird. Da die Teile des die Relativbewegung zwischen dem Verstellzahnrad und dem Festzahnrad übertragenden Übersetzungsgetriebes in kraftschlüssigem Eingriff verbleiben, kann über die elektrische Absicherung der Klemmung zwischen dem Verstellzahnrad und dem Festzahnrad gleichzeitig eine Absicherung der Greiferumstellung erfolgen.According to the exemplary embodiment in FIGS. 1 and 2, this transmission gear consists of a toothed segment 22, which is eccentric to the central longitudinal axis 8 on a drum-proof part, for example on the pressure piece 12, the fixed gear 6 or the like, around a pin 23 aligned parallel to the axis 8 is pivotable and engages with its toothing in the toothing of a pinion 24 fastened on the free end of the control shaft 21. The toothed segment is designed as a double lever and carries on its arm opposite the toothing a driver pin 25 which interacts with a driver link 26 which is fastened to the adjusting gear 10 and has a groove which is delimited by walls of different heights. The eccentric mounting of the control shaft 21 in the turning drum 1 ensures that the groove of the driving link 26 releases the driving pin 25 after a certain angle of rotation. Since the driver pin 25 when pivoting the Tooth segment 22 moves about the axis of the pin 23, it approaches the central longitudinal axis 8 on its path of movement, while the driver link 26 moves at the same distance from the central longitudinal axis. The lower limitation of the groove of the driving link releases the driving pin at a certain point. On the way back, the longer limitation of the groove ensures that the driver pin 25 is returned to the starting position. By a suitable choice of the gear ratio and the tooth circle distance of the toothed segment from the pivot axis of the pin 23 in relation to the distance of the driving pin 25 from the same axis, it is achieved that when changing the printing unit in a predetermined angular range of the relative movement of the adjusting gear relative to the fixed gear there is a safe gripper changeover . The driving link 26 attached to the adjusting gear 10 can also be adjustable in the circumferential direction of the adjusting gear. For this purpose, the formation of the driving link 26 in a special component is advantageous, which is screwed to the adjusting gear 10. Since the parts of the transmission gear transmitting the relative movement between the adjusting gear and the fixed gear remain in frictional engagement, the gripper changeover can be secured simultaneously via the electrical securing of the clamping between the adjusting gear and the fixed gear.

Bei dem Ausführungsbeispiel der Figuren 3 und 4 erfolgt die Greiferumstellung durch Stillsetzen der Kurvenrolle 16, z.B. dadurch, daß sie in einer Scheitellage der Antriebskurve festgehalten wird, oder durch Abheben der Kurvenrolle 16 von der zugehörigen Antriebskurve 17, so daß für die Greiferumstellung eine Schwenkbewegung ausreicht. Die Schaltwelle 21 ist an ihrem inneren Ende mit einem Hebel 27 fest verbunden, der in einer seitlichen Ausnehmung 28 der Wendetrommel 1 herausgeführt und mit einem Bauteil an der Greiferbrückenwelle in der Weise zusammenwirkt, daß er in der gezeichneten Stellung die Greiferwelle in einer Ruhelage der Greifer abstützt. Durch eine Drehbewegung der Schaltwelle 21 wird die Kurvenrolle 16 dazu von der Antriebskurve 17 abgehoben und in einer Scheitellage festgehalten, so daß die Greifer in einer den Maschinenbetrieb nicht behindernden Ruhestellung verharren. Dies läßt auch eine Vereinfachung des Übersetzungsgetriebes für die Übertragung der Relativbewegung des Verstellzahnrades 10 gegenüber dem Festzahnrad 6 zu. Mit dem freien Ende der Schaltwelle 21 ist ein Hebel 29 drehfest verbunden, der durch eine Feder 30 gegen einen Anschlag 31 am Verstellzahnrad 10 vorgespannt ist. Ein weiterer Anschlag 32 ist trommelfest angeordnet. Bei der Druckwerksverstellung wandert der Anschlag 31 mit dem Verstellzahnrad 10 relativ gegenüber dem Festzahnrad 6 und anderer trommelfester Teile. Die Spannkraft der Feder 30 überwindet das zur Greiferumstellung erforderliche Drehmoment in der Schaltwelle 21 und hält den Hebel 29 zunächst gegen den Anschlag 31 bis der Hebel 29 gegen den Anschlag 32 zur Anlage kommt. Auf diesem ersteren Teil des Weges erfolgt die Greiferumstellung in der beschriebenen Weise. Auf dem weiteren Weg erfolgt dann eine Anpassung an insbesondere kleinere Formate. Bei der Rückstellung des Verstellzahnrades 10 wird der Hebel 29 von dem Anschlag 31 in die Ausgangsposition zurückgeführt. Anstelle der in dem Beispiel der Figuren 3 und 4 dargestellten Zugfeder 30, welche mit dem einen Ende an einem festen Trommelteil verankert ist und mit dem anderen Ende an den Hebel 29 angreift, kann auch eine Druckfeder oder ein anderes Federelement vorgesehen sein.In the exemplary embodiment in FIGS. 3 and 4, the gripper changeover is carried out by stopping the cam roller 16, for example by holding it in an apex position of the drive curve, or by lifting the cam roller 16 off the associated drive curve 17, so that a pivoting movement is sufficient for the gripper changeover . The switching shaft 21 is fixedly connected at its inner end to a lever 27 which is in a lateral recess 28 in the Turning drum 1 led out and cooperates with a component on the gripper bridge shaft in such a way that it supports the gripper shaft in the rest position of the gripper in the position shown. For this purpose, the cam roller 16 is lifted from the drive cam 17 and held in an apex position by a rotary movement of the control shaft 21, so that the grippers remain in a rest position which does not impede machine operation. This also allows a simplification of the transmission gear for the transmission of the relative movement of the adjusting gear 10 relative to the fixed gear 6. A lever 29 is connected in a rotationally fixed manner to the free end of the selector shaft 21 and is biased by a spring 30 against a stop 31 on the adjusting gear 10. Another stop 32 is arranged drum-tight. When adjusting the printing unit, the stop 31 moves with the adjusting gear 10 relative to the fixed gear 6 and other drum-proof parts. The tensioning force of the spring 30 overcomes the torque required for the gripper changeover in the control shaft 21 and initially holds the lever 29 against the stop 31 until the lever 29 comes to rest against the stop 32. On this former part of the path, the gripper changeover takes place in the manner described. On the way there is an adaptation to smaller formats in particular. When the adjusting gear 10 is reset, the lever 29 is returned from the stop 31 to the starting position. Instead of the tension spring 30 shown in the example of FIGS. 3 and 4, which is anchored at one end to a fixed drum part and engages the lever 29 at the other end, a compression spring or another spring element can also be provided.

In Abweichung von dem Ausführungsbeispiel in den Figuren 3 und 4 zeigt das Ausführungsbeispiel in den Figuren 5 und 6 anstelle eines einfachen starren Hebels mit Anschlägen ein Hebelübersetzungsgetriebe aus einem gelenkigen Kniehebel. Dieser aus zwei in einem Gelenk 33 miteinander verbundenen Laschen 34 und 35 gebildeter Kniehebel ist mit dem einen Ende drehfest auf der Schaltwelle 21 und mit dem anderen Ende drehbar auf einem Lagerzapfen 36 am Verstellzahnrad 10 befestigt. Auch bei dieser Ausführungsform erfolgt bei einer Relativbewegung des Verstellzahnrades 10 gegenüber Festteilen der Maschine die Übertragung einer Drehbewegung auf die Schaltwelle 21, durch die die Umstellung der Greifersteuerung über den Hebel 27 bewirkt wird, so daß die Kurvenrolle 16 von der Antriebskurve 17 abgehoben wird. Bevorzugt kann eine solche Ausbildung zur Anwendung kommen, wenn die Bewegungskomponente zur Greiferumstellung nicht begrenzt ist.In a departure from the exemplary embodiment in FIGS. 3 and 4, the exemplary embodiment in FIGS. 5 and 6 also shows instead of a simple rigid lever Stops a lever transmission from an articulated toggle. This toggle lever, which is formed from two tabs 34 and 35 which are connected to one another in a joint 33, is fastened at one end in a rotationally fixed manner on the selector shaft 21 and at the other end in a rotatable manner on a bearing pin 36 on the adjusting gear 10. In this embodiment, too, with a relative movement of the adjusting gear 10 relative to fixed parts of the machine, a rotary movement is transmitted to the selector shaft 21, by means of which the gripper control is changed over the lever 27, so that the cam roller 16 is lifted off the drive cam 17. Such a design can preferably be used if the movement component for gripper changeover is not limited.

Bei dem Ausführungsbeispiel in den Figuren 7, 8 und 9 erfolgt die Kopplung der Druckwerkeverstellung mit der Greiferumstellung im wesentlichen durch die gleichen Mittel, die zu den Figuren 1 und 2 beschrieben wurden. Die Schaltwelle wirkt jedoch auf eine Kulissensteuerung ein, durch die im Gegensatz zu der Darstellung in Figuren 1,3 und 5 nicht die Kurvenrolle 16 umgesetzt wird, sondern die Antriebskurven 17 und 18 axial verschoben werden, so daß sie ebenfalls wechselweise mit der Kurvenrolle 16 zusammenwirken. Der zu den Beispielen in den Figuren 3 und 5 beschriebene Hebel 27 auf dem inneren Ende der Schaltwelle 21 ist hiernach mit einem Kopfstück 37 -vorteilhaft mit einer das Kopfstück bildenden drehbar gelagerten Rolle - ausgestattet, welches in eine Kulissenführung 38 mit axialem Versatz eingreift. Diese Kulissenführung 38 ist in einem axial verschiebbaren Bauteil 39 angeordnet, auf dem die Antriebskurven 17 und 18 ausgebildet sind. Der axiale Versatz der Kulissenführung 38 ergibt sich aus der Darstellung in der Figur 9. Durch eine in radialer Ebene stattfindende Schwenkbewegung des Kopfstückes 37 am freien Ende des Hebels 27 erfolgt eine axiale Verschiebung des Bauteiles 39 entsprechend dem axialen Versatz der Kulissenführung. Das Übersetzungsgetriebe aus den Bauteilen 22 bis 26 wird so ausgelegt, daß der Hebel 27 mit dem Kopfstück 37 eine vorbestimmte Schwenkung (im dargestellten Beispiel sind es etwa 180 Grad) ausführt und sich somit in den Endlagen der Greiferumstellung in einer versenkten Position innerhalb der Ausnehmung 28 in dem Trommelzapfen 2 befindet. Dazu ist die Kulissenführung an den Enden mit Teilstücken versehen, die in radialer Ebene verlaufen, um dem Hebel 27 mit dem Kopfstück 37 das Austauchen und Wiedereintauchen in die Kulisssenführung ohne Axialverschiebung des Bauteiles 39 zu ermöglichen. Eine Axialverschiebung erfolgt somit lediglich im Bereich des schrägen Überganges der beiden parallelen Teile der Kulissenführung, wie es sich deutlich aus der Darstellung in Figur 9 ergibt.In the exemplary embodiment in FIGS. 7, 8 and 9, the coupling of the printing unit adjustment to the gripper changeover takes place essentially by the same means that were described for FIGS. 1 and 2. However, the selector shaft acts on a link control, by means of which, in contrast to the illustration in FIGS. 1, 3 and 5, the cam roller 16 is not implemented, but rather the drive cams 17 and 18 are axially displaced, so that they also interact alternately with the cam roller 16 . The lever 27 described in the examples in FIGS. 3 and 5 on the inner end of the selector shaft 21 is hereafter equipped with a head piece 37 — advantageously with a rotatably mounted roller that forms the head piece — which engages in a link guide 38 with an axial offset. This link guide 38 is arranged in an axially displaceable component 39 on which the drive curves 17 and 18 are formed. The axial offset of the link guide 38 results from the illustration in FIG. 9. By means of a pivoting movement of the head piece 37 at the free end of the radial plane Lever 27 is an axial displacement of component 39 according to the axial offset of the link guide. The transmission gear from the components 22 to 26 is designed so that the lever 27 with the head piece 37 performs a predetermined pivoting (in the example shown, it is approximately 180 degrees) and is thus in the end positions of the gripper changeover in a recessed position within the recess 28 is located in the drum pin 2. For this purpose, the link guide is provided at the ends with sections that run in a radial plane in order to enable the lever 27 with the head piece 37 to be immersed and immersed in the link guide without axial displacement of the component 39. An axial displacement thus only takes place in the area of the oblique transition of the two parallel parts of the link guide, as can be clearly seen from the illustration in FIG. 9.

Allen vorstehenden Ausbildungen ist der Vorteil gemeinsam, daß eine relativ dünne Schaltwelle in einer Bohrung geringen Durchmessers exzentrisch zur Mittellängsachse 8 in der Wendetrommel 1 bzw. dem Lagerzapfen 2 gelagert sein und die seitliche Herausführung der Übertragungsglieder für die Drehbewegung der Schaltwelle 21 auf die Elemente zur Greiferumsteuerung in Ausnehmungen geringer Ausdehnung erfolgen kann, so daß keine die Stabilität der Wendetrommel und ihrer Lagerzapfen 2 beeinflussende Schwächung erfolgt.All of the above designs have the advantage in common that a relatively thin control shaft in a bore of small diameter is mounted eccentrically to the central longitudinal axis 8 in the turning drum 1 or the bearing journal 2 and the lateral lead-out of the transmission members for the rotary movement of the control shaft 21 on the elements for gripper reversal can take place in recesses of small extent, so that there is no weakening affecting the stability of the turning drum and its journal 2.

Die Figuren 10 bis 13 zeigen eine konstruktive Gestaltungsform des Erfindungsgedankens, bei der elektrische Schaltglieder zum Einsatz kommen. Der in Figur 10 dargestellte Kipphebel 40 dient zur Betätigung eines elektrischen Schalters. Er wird durch einen parallel zur Mittellängsachse 8 in dem Verstellzahnrad 10 beweglich geführten und durch eine Feder 41 gegen das Festzahnrad 6 belasteten Schaltstift 42 bewegt. In den Endlagen der Greiferumstellung greift dieser Schaltstift 42 mit einer kegeligen Spitze in Ausnehmungen 43 an der Seitenfläche des Festzahnrades 6 ein. Sobald eine Drehwinkelverstellung des Verstellzahnrades 10 gegenüber dem Festzahnrad 6 erfolgt, wird der Schaltstift 42 infolge der kegeligen Gestaltung seiner Spitze aus der einer Endlage zugeordneten Ausnehmung 43 herausgedrückt und axial gegen den Kipphebel 40 bewegt. Dieser kann sowohl für die Schaltung einer elektrischen Absicherung verwendet werden, als auch im Stromkreis einer elektrischen Verstelleinrichtung für die Greiferumstellung oder anderen gegebenenfalls erforderlichen Umstellungen angeordnet sein. Da der Kipphebel 40 ortsfest gelagert ist, kann durch eine vorbestimmte Breite des Kipphebels die Einschaltdauer des Stellantriebes bestimmt werden. Nach der Greiferumstellung kann der Schaltstift 42 in eine länger ausgeführte ringsegmentförmige Ausnehmung 43 eintauchen, so daß der Stromkreis wieder unterbrochen wird. Der Kipphebel 40 kann aber auch auf Schaltelemente für hydraulisch oder pneumatisch bewegte Betätigungsglieder einwirken, die erforderliche Umstellungen vornehmen oder solche Umstellungen einleiten.

Figure imgb0001
Figures 10 to 13 show a constructive design form of the inventive concept, in which electrical switching elements are used. The rocker arm 40 shown in Figure 10 is used to actuate an electrical switch. It is moved by a switching pin 42, which is guided in the adjusting gear 10 parallel to the central longitudinal axis 8 and is loaded by a spring 41 against the fixed gear 6. In the end positions of the Gripper switch engages this switching pin 42 with a tapered tip in recesses 43 on the side surface of the fixed gear 6. As soon as an adjustment of the angle of rotation of the adjusting gear 10 with respect to the fixed gear 6 takes place, the switching pin 42 is pressed out of the recess 43 assigned to an end position due to the conical configuration of its tip and moved axially against the rocker arm 40. This can be used both for the switching of an electrical fuse, and can also be arranged in the circuit of an electrical adjusting device for the gripper changeover or other necessary changes. Since the rocker arm 40 is fixed in position, the duty cycle of the actuator can be determined by a predetermined width of the rocker arm. After the gripper switch, the switching pin 42 can dip into a longer ring segment-shaped recess 43, so that the circuit is interrupted again. The rocker arm 40 can also act on switching elements for hydraulically or pneumatically moved actuators, make the necessary changes or initiate such changes.
Figure imgb0001

Claims (19)

  1. Sheet-fed rotary printing machine with a plurality of printing units for recto printing and for recto/verso printing, and with a turning device which is arranged between two printing units and in which a rotatable switching shaft is mounted in a turning drum for the gripper change-over and a pair of gearwheels arranged in the chain of the driving gearwheels and consisting of a fixed gearwheel on the turning drum and of an adjusting gearwheel concentric thereto and of adjustable rotary angle, which can be clamped with one another, is provided for the printing-unit adjustment, characterised in that arranged on the adjusting gearwheel (10) is at least one element (26, 31, 36) which, in a predetermined angular range of the relative movement of the adjusting gearwheel (10) relative to the fixed gearwheel (6) acts on members (24-26 or 29-32 or 33-36) to rotate the switching shaft (21) for the gripper change-over.
  2. Sheet-fed rotary printing machine with a plurality of printing units for recto printing and for recto/verso printing, and with a turning device which is arranged between two printing units and in which actuating members drivable from outside are provided on a turning drum for the change-over of a gripper control and a pair of gearwheels arranged in the chain of the driving gearwheels and consisting of a fixed gearwheel on the turning drum and of an adjusting gearwheel concentric thereto and of adjustable rotary angle, which can be clamped with one another, is provided for the printing-unit adjustment, characterised in that arranged on the adjusting gearwheel (10) is at least one element (42) which, in a predetermined rotary-angle range of the relative movement of the adjusting gearwheel (10) relative to the fixed gearwheel (6), acts on switching elements (40) for drives of the actuating members drivable from outside.
  3. Sheet-fed rotary printing machine according to Claim 1, characterised in that a step-up gear (24-26, 29-32, 33-36), the parts of which are mounted either on the fixed gearwheel (6) or on the adjusting gearwheel (10), converts the relative movement of the two gearwheels in relation to one another in a predetermined angular range into a rotational movement and transmits this to the switching shaft (21) for the gripper change-over.
  4. Sheet-fed rotary printing machine according to Claims 1 and 2, characterised in that the step-up gear consists of a toothed quadrant (22), which is mounted pivotably on the end face of the turning drum about a journal axis oriented parallel to the drum axis (8), but lying eccentrically to this, and the toothing of which engages into a pinion (24) arranged on the switching shaft (21), and of a slotted driving link (26) which is fastened to the adjusting gearwheel (10) and which moves, only in the predetermined angular range of the relative movement of the two gearwheels (6, 10) of the pair of gearwheels, in the pivoting range of an arm extending radially on the toothed quadrant (22).
  5. Sheet-fed rotary printing machine according to Claim 4, characterised in that the slotted driving link (26) on the adjusting gearwheel (10) cooperates with a driving pin (25) arranged on the arm of the toothed quadrant (22), the slotted driving link (26), during the adjustment, starting from the machine position for recto printing, surrounding the driving pin (25) over a curved path serving for the gripper change-over, thereby driving it and then releasing it in a predetermined position and, during the adjustment in the opposite direction, starting from the machine position for recto/verso printing, receiving it again in this position and returning it to the initial position.
  6. Sheet-fed rotary printing machine according to Claim 5, characterised in that the slotted driving link (26) cooperating with the driving pin (25) on the arm of the toothed quadrant (22) is limited by side sheets of differing height.
  7. Sheet-fed rotary printing machine according to Claim 5, characterised in that the step-up ratios of the toothing of the pinion (24) on the switching shaft (21) and of the toothing on the toothed quadrant (22) are coordinated on the rotary path of the switching shaft (21) necessary for the gripper change-over.
  8. Sheet-fed rotary printing machine according to Claim 4, characterised in that the slotted driving link (26) is fastened to the adjusting gearwheel (10) so as to be adjustable in the circumferential direction of the latter.
  9. Sheet-fed rotary printing machine according to Claims 1 and 2, characterised by a lever mechanism consisting of a lever (29) fastened on the switching shaft (21) mounted eccentrically in the turning drum (1) and of a spring (30) which loads this lever in the change-over direction and which tensions the lever (29) against a stop (31) arranged on the adjusting gearwheel (10).
  10. Sheet-fed rotary printing machine according to Claim 9, characterised in that there is provided a tension spring (30) which engages on the end face of the turning drum (1) on the one hand and on the lever (29) on the other hand and which pulls the lever (29) against a stop (31) on the adjusting gearwheel (10), and there is arranged fixedly relative to the drum a further stop (32), against which the lever (29) comes to bear after a predetermined pivoting.
  11. Sheet-fed rotary printing machine according to Claims 1, 2 and 9, characterised in that the lever mechanism is formed by a toggle lever consisting of straps (34, 35) which are connected to one another in an articulated manner, one end of the toggle lever being fastened on the switching shaft (21) and the other end being mounted movable on the adjusting gearwheel (10), and the lengths of the straps (34, 35) connected to one another in an articulated manner being coordinated with a step-up ratio which, from the adjusting travel of the adjusting gearwheel (10) relative to the fixed gearwheel (6) during the printing-unit adjustment, transmits a component of this movement, necessary for the gripper change-over, to the switching shaft (21).
  12. Sheet-fed rotary printing machine according to one of the preceding claims, characterised in that the switching shaft (21) is coupled via an angular gear to an eccentric (19) which is rotatable in the turning drum about a radial axis and which engages by means of an eccentric pin (20) into a bridge (15), guided axially displaceably on the turning drum, for the change-over of the gripper control.
  13. Sheet-fed rotary printing machine according to Claim 1 and one or more of Claims 2 to 12 for devices for the gripper change-over with axially displaceable actuating member, the linear movement component of which is derived from the rotational movement of the switching shaft, characterised in that fastened to the inner end of the switching shaft (21) is a radially extending pivoting lever (27), of which the free end, during its pivoting movement, travels through a slotted guide (38) which is designed with an axial offset corresponding to the displacement of the axially movable actuating member and which is provided in the actuating member.
  14. Sheet-fed rotary printing machine according to Claim 13, characterised in that a roller engaging into the slotted guide (38) is arranged at the free end of the pivoting lever (27).
  15. Sheet-fed rotary printing machine according to Claims 13 and 14, characterised in that the pivoting lever (27) assumes a countersunk position in the turning drum in the end positions of the gripper change-over.
  16. Sheet-fed rotary printing machine according to Claims 1, 3 and 15, characterised in that the element on the adjusting gearwheel (10) consists of a switching bolt (42) which is guided movably parallel to the axis (8) of the gearwheels and is sprung relative to a fixed part of the turning drum and the free outwardly guided end of which is effective against a further switching member (40) for initiating a change-over operation.
  17. Sheet-fed rotary printing machine according to Claims 3 and 16, characterised in that the switching bolt (42) is effective only over a limited portion of the relative movement of the adjusting gearwheel (10) relative to the fixed gearwheel (6) against a switching member (40) for a servomotor for the gripper change-over.
  18. Sheet-fed rotary printing machine according to Claim 17, characterised in that the switching bolt (42) engages by means of a conical tip into recesses (43) on a fixed part of the turning drum (1), in order to release the switching member (40).
  19. Sheet-fed rotary printing machine according to Claim 2, characterised in that the element consists of a switch which is located in the electrical circuit of the drive of the machine and interrupts the circuit outside the end positions and which is therefore part of an electrical protection of the machine.
EP90104860A 1989-04-08 1990-03-15 Rotary printing machine for sheets with several units for printing recto and recto-verso Expired - Lifetime EP0392205B1 (en)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE3911609 1989-04-08
DE3911609A DE3911609A1 (en) 1989-04-08 1989-04-08 ARCH ROTATION PRINTING MACHINE WITH SEVERAL PRINTING WORKS FOR BEAUTIFUL PRINTING AND BEAUTIFUL AND REPRINTING

Publications (3)

Publication Number Publication Date
EP0392205A2 EP0392205A2 (en) 1990-10-17
EP0392205A3 EP0392205A3 (en) 1991-04-24
EP0392205B1 true EP0392205B1 (en) 1993-07-28

Family

ID=6378282

Family Applications (1)

Application Number Title Priority Date Filing Date
EP90104860A Expired - Lifetime EP0392205B1 (en) 1989-04-08 1990-03-15 Rotary printing machine for sheets with several units for printing recto and recto-verso

Country Status (8)

Country Link
US (1) US5076164A (en)
EP (1) EP0392205B1 (en)
JP (1) JP2554186B2 (en)
CN (1) CN1021557C (en)
AU (1) AU631852B2 (en)
CA (1) CA2010495C (en)
DE (2) DE3911609A1 (en)
ES (1) ES2043150T3 (en)

Families Citing this family (17)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE4131273C1 (en) * 1991-09-20 1992-12-10 Heidelberger Druckmaschinen Ag, 6900 Heidelberg, De
FR2693946B1 (en) * 1992-07-15 1995-03-31 Heidelberger Druckmasch Ag Method and device for starting / stopping the turning of sheets and adjusting the format in the transport of sheets through a printing machine.
DE4223190C2 (en) * 1992-07-15 1995-12-07 Heidelberger Druckmasch Ag Device for turning the sheet turning on and off when conveying sheets through a printing machine
DE4322477C2 (en) * 1992-07-15 1995-12-21 Heidelberger Druckmasch Ag Method and device for starting and stopping the sheet turning and for setting the format when conveying sheets through a printing press
JP3074105B2 (en) * 1993-05-13 2000-08-07 株式会社桜井グラフィックシステムズ Sheet reversing mechanism of sheet-fed printing press
DE4401684C2 (en) * 1994-01-21 1998-04-09 Heidelberger Druckmasch Ag Adjustment device for a printing press
US5802920A (en) * 1995-11-15 1998-09-08 Heidelberger Druckmaschinen Aktiengesellschaft Double gear wheel of a turning device on printing presses
JP3539908B2 (en) * 2000-03-02 2004-07-07 リョービ株式会社 Sheet-fed printing press capable of double-sided printing
DE10254113A1 (en) 2001-12-12 2003-06-18 Heidelberger Druckmasch Ag Operating state changing apparatus for gripper controller in sheet reversing device of sheet processing machine, has adjusting component which serves to change position of actuator relative to cylinder when changing operating state
JP5140265B2 (en) * 2005-11-21 2013-02-06 ハイデルベルガー ドルツクマシーネン アクチエンゲゼルシヤフト Device for carrying out an operating process in a rotatable cylinder of a printing press
US7321212B2 (en) * 2006-02-01 2008-01-22 Innovative Motor Controls Inc. Restricted motion motor control with visual indication
US20070175344A1 (en) * 2006-02-01 2007-08-02 Innovative Motor Controls Quick disconnect motor mount
JP4981363B2 (en) * 2006-06-05 2012-07-18 株式会社小森コーポレーション Printing state automatic switching device and method
DE102007040694B4 (en) 2006-09-20 2018-07-05 Heidelberger Druckmaschinen Ag Device for converting the operating mode from beautiful to perfecting in a sheet-processing machine
US8253290B2 (en) * 2009-01-28 2012-08-28 Innovative Motor Controls, Inc. Electronic retrofit controller for hydraulically adjusted printing press
CN107160842B (en) * 2017-07-10 2023-11-03 江苏海迪威液压有限公司 Pattern position adjusting mechanism for vertical pad printing operation
CN111781333A (en) * 2020-07-20 2020-10-16 长江水利委员会长江科学院 Stepless speed change-based water-saving field rainfall system and method

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Publication number Priority date Publication date Assignee Title
DE2604895C3 (en) * 1976-02-07 1978-11-16 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Device for changing the gripper movement in a turning drum for perfecting presses
NL163466C (en) * 1976-05-08 Heidelberger Druckmasch Ag DEVICE FOR PROTECTING A PRESSURE MACHINE FOR CLEANING AND WEATHERING PRESSURE WHEN SWITCHING ON CLEANING AND WEATHERING PRESSURE
DD153864B1 (en) * 1980-11-05 1987-10-14 Roland Kuehn DEVICE FOR CLAMPING AND LOESEN TWO GEARS
DD232463A1 (en) * 1984-12-10 1986-01-29 Polygraph Leipzig DEVICE FOR OPERATING SWITCH SHAFTS IN ARC CYLINDERS
DE3611324A1 (en) * 1986-04-04 1987-10-08 Heidelberger Druckmasch Ag DEVICE FOR ADJUSTING THE RELATIVE ROTATION BETWEEN A GEAR WHEEL AND A GEAR WHEEL BEARING WITH THIS SIMULTANEOUSLY
JPH0696285B2 (en) * 1986-08-25 1994-11-30 株式会社小森コーポレーション Print switching device of sheet-fed printing machine with reversing mechanism
DE3814831C1 (en) * 1988-05-02 1989-10-26 Heidelberger Druckmaschinen Ag, 6900 Heidelberg, De
JP2827728B2 (en) * 1992-08-03 1998-11-25 日本電気株式会社 Semiconductor memory device and method of manufacturing the same

Also Published As

Publication number Publication date
JPH02286337A (en) 1990-11-26
CN1021557C (en) 1993-07-14
CN1046124A (en) 1990-10-17
AU631852B2 (en) 1992-12-10
EP0392205A2 (en) 1990-10-17
DE59002062D1 (en) 1993-09-02
US5076164A (en) 1991-12-31
EP0392205A3 (en) 1991-04-24
ES2043150T3 (en) 1993-12-16
CA2010495A1 (en) 1990-10-08
CA2010495C (en) 1994-01-11
DE3911609A1 (en) 1990-10-11
JP2554186B2 (en) 1996-11-13
DE3911609C2 (en) 1992-10-08
AU5005290A (en) 1990-10-11

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