EP0518894B1 - Trailing nozzle device for fast paper feeders - Google Patents

Trailing nozzle device for fast paper feeders Download PDF

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Publication number
EP0518894B1
EP0518894B1 EP91904420A EP91904420A EP0518894B1 EP 0518894 B1 EP0518894 B1 EP 0518894B1 EP 91904420 A EP91904420 A EP 91904420A EP 91904420 A EP91904420 A EP 91904420A EP 0518894 B1 EP0518894 B1 EP 0518894B1
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EP
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Prior art keywords
feed
nozzle device
axis
rubber
end region
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EP91904420A
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German (de)
French (fr)
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EP0518894A1 (en
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Georg Binnen
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H3/00—Separating articles from piles
    • B65H3/08—Separating articles from piles using pneumatic force
    • B65H3/0808—Suction grippers
    • B65H3/0816—Suction grippers separating from the top of pile
    • B65H3/0825—Suction grippers separating from the top of pile and acting on the rear part of the articles relatively to the final separating direction

Definitions

  • the invention relates to a drag nozzle device according to claim 1.
  • a drag nozzle device for high-speed sheet feeders has become known from the generic US Pat. No. 2,722,416. Which essentially applies to what is said in detail below regarding a previously known drag nozzle device.
  • the drag nozzles In order to form a scale in the running direction of the sheet feed, the drag nozzles have to make a back and forth movement. In addition, the drag nozzles must also be able to carry out a deflection movement, since the stacks or the individual sheets of such a stack are not completely aligned with the insertion direction of a printing press. The suction heads must therefore also have a so-called oblique arc correction.
  • a known drag nozzle device of the type mentioned at the outset has a rocker arm which can carry out an oscillating back and forth movement.
  • This pendulum movement is by means of a swing arm attached cam roller generated, which is connected to a cam disc tensile and pressure resistant.
  • In the lower end point of the rocker arm there is an approximately horizontally aligned bridge girder, which carries out the approximately horizontally oscillating back and forth movement together with the rocker arm.
  • This bridge girder is in its rear End supported by means of rollers so that it is also supported at its rear end point during its back and forth movement.
  • these rollers can be deflected laterally so that the bridge girder can also perform a lateral deflection movement.
  • the lateral deflection movement causes the required oblique arc correction if the sheet position is not exact.
  • the front end of this bridge girder is rotatably connected to the rocker via a first bearing so as to enable the back and forth movement of the bridge girder together with the rocker.
  • the front end of the bridge girder is additionally attached to the rocker arm via a second bearing, which enables the required lateral deflection movement of the bridge girder.
  • So-called plain or roller bearings are used to form these bearings. Due to the very high cycle frequency of sheet feeders, which can be around 12,000 reciprocations per hour in known sheet feeders, the direction of rotation of these roller bearings must be reversed accordingly often. These very rapid changes in the direction of rotation cause high acceleration forces on the rotating parts present in the bearing and degrade the lubricant supply into the bearing, so that these bearings tend to form pits. Due to the bearing design between the rocker and the bridge girder in the form of two mutually independent bearings, this node has a relatively large weight, so that correspondingly large vibrations and great wear must be expected. Clock frequencies over 15,000 reciprocations per hour are therefore not possible.
  • the invention has for its object to provide a drag nozzle device for high-speed sheet feeder, which does not have the disadvantages known from the prior art and which thus allows a long service life and the highest possible clock frequencies.
  • the drag nozzle device mentioned at the outset and known from the prior art is accordingly characterized in that rubber-metal elements, in particular rubber-metal bushings, are present as bearings for jointly receiving both the back and forth movements and the additional deflection movements.
  • Such bushings are bearing elements which consist of an inner and an outer sleeve which are firmly connected to one another by an elastically deformable mass.
  • Such bushings are known as construction elements.
  • Such bushes damp radially and axially acting vibrations. They can be subjected to twisting and absorb cardanic deflections.
  • the invention is thus based on the finding that sheet feeders can be constructed using such bushings, in which the vibrations which occur increasingly at high clock frequencies are minimized and which permit a wear-free and maintenance-free pendulum movement without any lubrication. With the aid of these sockets, an inclined arc correction is also possible without additional moving elements.
  • a construction for a trailing nozzle device of the type mentioned at the outset has proven to be structurally simple, in which two rockers are present, the front rocker being mounted on its one end with a swinging around a first axis and on the other hand with its lower one End region is connected to the front end region of the bridge girder via at least one rubber-metal socket.
  • the rear end of these two rockers is connected with its lower end region to the rear end region of the bridge girder via a rubber-metal bushing, and its upper end region is mounted so as to oscillate about a second axis.
  • This upper end region can also perform a rotary movement together with the second axis about a third axis, which is aligned transversely to the second axis. It has proven useful if rubber-metal bushings are also available as bearings on the first axis.
  • each of the two rockers is provided with a cam roller and between these two cam rollers there is a cam plate designed as a double cam plate.
  • One of these double cam discs lies against one of the two cam rollers. Due to the existing rubber-metal bushes, an elastically resilient mounting of the cam rollers outside of the two cam disks is ensured without necessarily existing deviation tolerances of the two complementary curves could have a disadvantageous effect and additional design measures were necessary.
  • the two rockers therefore always lie firmly on the double cam disc via the two cam rollers.
  • a lever is attached to the yoke of the rear rocker, which can be adjusted with its free end transversely to its longitudinal extent either manually or by a motor drive.
  • the yoke can be pivoted and thus the desired or required oblique arc correction of the drag nozzle device can be achieved.
  • this back and forth movement of the lever takes place along a circular arc, the center of the circle of which lies in the bearing axis, due to the relatively very small pivoting movement of this lever, the same can be adjusted so that its free end along a threaded rod with which its end is in meshing engagement , is adjusted.
  • the threaded rod is adjusted either manually or by a motorized linear drive.
  • This threaded rod is freely cantilevered so that its cantilever arm can perform a slightly oscillating movement. So constraining forces can practically not occur between the threaded rod and the lever.
  • the bearing is positioned between the bridge girder and the rear rocker in the extreme rear position exactly in the extension of the pivot axis for the yoke on which the rear rocker is pivotably mounted. This ensures that an inclined arch in the non-pivoted state of the bridge girder and thus the crossbar is taken up with suction nozzles and is aligned by pivoting during the towing process.
  • the front end region of the bridge girder is designed like a fork with two head pieces.
  • the crossbar is attached to each of these two head pieces with its suction cups.
  • the rubber-metal bushing is present between the front rocker and the crossbar.
  • the lower end regions of the front rocker also end in a cross member which is connected in its central region to said rubber-metal bushing and is supported by its two end regions on the two head pieces.
  • the mutual bearing surfaces of the cross member and of the two head pieces each have a fillet such that the two contact surfaces can roll on one another when the rocker moves back and forth.
  • the crossbar is therefore always present in parallel in every position of the rocker above the sheet stack.
  • the invention is described and explained in more detail below with reference to the embodiment shown in the drawing.
  • the single figure shows a schematic, perspective view of a detail of a drag nozzle device for a high-speed sheet stacker.
  • the frame 14 of a drag nozzle device is mounted above the rear region of a stack 10 with sheets 12 lying one above the other.
  • the drag nozzle device is part of a high-speed sheet feeder, not shown in the drawing. With the help of this sheet feeder, sheets 12 are laid out one after the other in a scale-like manner, as is illustrated with the sheets 12.1, 12.2, 12.3. These sheets are then fed in the transport direction 16 to an offset printing machine, not shown.
  • a shaft 18 protrudes from the frame 14 and is arranged with its axis of rotation 20 parallel above the plane 22 of the stack 10.
  • two cams 24, 26 are attached in a rotationally fixed manner at a distance from one another.
  • a cam roller 28 bears against rotation, which in turn is attached to the rear link 30 of a rocker 34 consisting of two links 30, 32 in a rotationally fixed manner.
  • the two links 30, 32 and thus the rocker 34 are rotatably mounted on a shaft 36.
  • the axis 38 of this shaft 36 runs perpendicular to the longitudinal extent of the two rod-shaped members 30, 32.
  • the shaft 36 is fixedly mounted on the frame 14 in a left and right bearing bush 40, 42.
  • the rocker arm can therefore perform a pendulum-type reciprocating movement around the shaft 38 (arrow 44).
  • the lower end regions 46, 48 of the two rod-shaped members 30, 32 are connected to one another in a rigid manner via a cross member 50 which is aligned parallel to the shaft 38.
  • the end regions of this cross member 50 have a respective lower rounding 52 with which they rest on a corresponding rounding 54 of a left and right head piece 56, 58 in the drawing.
  • the fillets 52, 54 are such that when the rocker arm 34 oscillates back and forth, the fillet 52 remains rolling on the fillet 54.
  • a cross bar 60 to which drag vacuums 62 are fastened, runs through the two head pieces 56, 58. These drag vacs 62 are used to lift d. H. Suction of sheet 12. In the drawing, the drag suction devices 62 are just present for sucking the sheet 12.1 above the stack 10.
  • the cross member 50 is fastened in the area between the two head pieces 56, 58 to a bearing bush 66 which is present on the cross bar 60.
  • the two head pieces 56, 58 are connected to one another via a yoke 68.
  • This yoke 68 is the left front end of a bridge girder 70 in the drawing.
  • This bridge girder 70 is arranged at right angles to the cross bar 60 with its suction cups 62 via the head pieces 56, 58.
  • This bridge girder 70 has a bearing bush 72 in which a rear rocker 74 is mounted.
  • This rear rocker 74 like the front rocker 34, has two parallel rod-shaped members 76, 78 which are fastened to the two ends of the bushing.
  • On the right 78 in the drawing is one Cam roller 80 rotatably attached. This cam roller 80 bears against the front cam 26 in a rotationally fixed manner. The cam rollers 28, 80 are thus on both sides of the two cams 24 and 26 against rotation.
  • the upper ends of the two rod-shaped members 76, 78 are rotatably mounted on a shaft 82.
  • the shaft 82 of the rear rocker 74 is rotatably supported with its end points in two bearing bushes 84, 86.
  • the two bearing bushings 84, 86 are part of a yoke 88.
  • This yoke 88 is pivotally mounted in a bearing 90, the axis 110 of which is oriented perpendicular to the plane 22 of the stack 10, in a plane parallel to the plane 22.
  • This bearing 90 is fixedly attached to the frame 14 via a web 92.
  • the yoke 88 projects with a partial area beyond the bearing 90 - in the drawing - beyond.
  • This rear part is designed as an angle lever 94. At the free end of this angle lever 94 there is a bore 96.
  • the threaded rod 100 is rotatable in this bore 96, but is mounted in a bearing 98 so that it cannot be displaced in its longitudinal direction.
  • the threaded rod 100 is displaced in its longitudinal direction by a linear drive 102 fixedly mounted on the frame 14.
  • the angle lever 94 is adjusted along the arrow 104 to the left or right in the drawing. Due to the cantilevered construction of this threaded rod 100 and its relatively flexible design and, moreover, due to the only very small required movements along the arrow 104, there are no constraining forces during the linear adjustment along the threaded rod 100 in the camp 90.
  • the angle lever 94 can thus be adjusted along the arrow 106.
  • the yoke 88 can thus also be pivoted along the arrow 106.
  • This pivoting of the yoke 88 leads to a pivoting of the bearing bush 72 and thus to a lateral adjustment of the bridge girder 70.
  • the bushing 72 like the bushing 66, is also designed as a so-called rubber-metal bushing.
  • These bushings consist of an inner and outer sleeve, between which an elastically deformable mass is arranged, which is firmly connected to the two sleeves.
  • Such a bearing can be loaded in the radial and axial direction as well as on rotation and can thus also absorb cardanic deflections.
  • the bridge support 70 can thus also pivot in the plane parallel to the plane 22. Since the bushing 72 is present exactly vertically below the bearing 90, this bushing 72 will only rotate about the vertical axis 110 of the bearing 90 when the yoke 88 is pivoted about the bearing 90; lateral adjustment of the socket 72 will not take place.
  • the two cam rollers 28, 80 rest against the respective cam plates 24 and 26 without play and in a rotationally fixed manner. Any pressing mechanisms for these cam rollers are not required.
  • the drag nozzle device shown works in the following way.
  • the bridge girder 70 In the position shown in the drawing, the bridge girder 70 is in its maximum rear position. It remains in this position for a while in order to give lifting nozzles (not shown) the possibility of lifting the uppermost sheet 12.1. After lifting it, the take over Drag vacuum 62 the raised sheet to move it further in the transport direction 16 by the dimension s.
  • the sheet 12.1 also has the same distance and the same orientation to the sheet 12.2 as this sheet 12.2 has to the sheet 12.3 after its position shifted by the dimension s.
  • the front and rear rocker arms 34, 74 carry out a corresponding pendulum movement along the arc arrow 44.
  • the bridge girder 70 sweeps over a corresponding arcuate curved path. Due to the relatively small pendulum deflections, this curved path is sufficiently straightforward in practice so that the different height of the transverse rod 60 in the vertical direction with respect to the arch 12.1 can be neglected.
  • the skew alignment must be compensated for during the transport of the sheet along the path s.
  • the crossbar 60 is now pivoted with the suction cups 62 by pivoting the yoke 88 around the bearing 90 in a plane parallel to the plane 22 such that the crossbar 60 is again parallel to the respectively not exactly aligned sheet to be received is available; the rear rocker 74 has accordingly pivoted laterally with the bridge girder 70.
  • the bearing bushes 40, 42, 84, 86 are also designed as rubber-metal bush bearings. This means that these bearings are also free of wear, maintenance and free of maintenance with simple design measures.
  • these six rubber-metal bushes 66, 72, 40, 42, 84, 86 are installed in the vertical position of the two rockers 34, 74, these bushes have a braking effect on the rockers during rapid pendulum movements of the rockers, as a result of which the latter become one quiet pendulum run are forced.
  • the rubber-metal bushings used transmit the required twisting and cardanic deflection movements in a play-free, maintenance-free and wear-free manner.
  • the required inclination of the bridge girder 70 is generated without additional rollers and rolling planes.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Sheets, Magazines, And Separation Thereof (AREA)
  • Catching Or Destruction (AREA)
  • Loading And Unloading Of Fuel Tanks Or Ships (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Advancing Webs (AREA)
  • Soil Working Implements (AREA)

Abstract

PCT No. PCT/DE91/00160 Sec. 371 Date Sep. 2, 1992 Sec. 102(e) Date Sep. 2, 1992 PCT Filed Feb. 27, 1991 PCT Pub. No. WO91/13822 PCT Pub. Date Sep. 19, 1991.A tractor nozzle device for fast running sheet feeders is distinguished in that rubber-metal bushings (66, 72) are provided for the bearings between the support bridge and the rocker as bearings for the mutual absorption of the back-and-forth movements (44) as well as the additional deflection movements (106).

Description

Die Erfindung betrifft eine Schleppdüseneinrichtung gemäß dem Patentanspruch 1.The invention relates to a drag nozzle device according to claim 1.

STAND DER TECHNIKSTATE OF THE ART

Durch die gattungsgemäße US-PS 27 22 416 ist eine Schleppdüseneinrichtung für schnellaufende Bogenanleger bekannt geworden. Auf die im wesentlichen das zutrifft, was weiter unten ausführlich zu einer vorbekannten Schleppdüseneinrichtung gesagt wird.A drag nozzle device for high-speed sheet feeders has become known from the generic US Pat. No. 2,722,416. Which essentially applies to what is said in detail below regarding a previously known drag nozzle device.

Um eine Schuppe in Laufrichtung der Bogenzuführung zu bilden, müssen die Schleppdüsen eine Hin- und Herbewegung machen. Außerdem müssen die Schleppdüsen zusätzlich eine Auslenkbewegung durchführen können, da die Stapel bzw. die einzelnen Bogen eines solchen Stapels nicht völlig exakt zur Einschubrichtung einer Druckmaschine ausgerichtet sind. Die Saugköpfe müssen daher auch eine sogenannte Schrägbogenkorrektur besitzen.In order to form a scale in the running direction of the sheet feed, the drag nozzles have to make a back and forth movement. In addition, the drag nozzles must also be able to carry out a deflection movement, since the stacks or the individual sheets of such a stack are not completely aligned with the insertion direction of a printing press. The suction heads must therefore also have a so-called oblique arc correction.

Eine bekannte Schleppdüseneinrichtung der eingangs genannten Art weist eine Schwinge auf, die eine pendelnde Hin- und Herbewegung durchführen kann. Diese Pendelbewegung wird mittels einer an der Schwinge befestigten Kurvenrolle erzeugt, die zug- und druckfest mit einer Kurvenscheibe verbunden ist. Im unteren Endpunkt der Schwinge ist ein etwa horizontal ausgerichteter Brückenträger vorhanden, der die in etwa horizontal pendelnde Hin- und Herbewegung zusammen mit der Schwinge durchführt. Dieser Brückenträger ist in seinem rückwärtigen Ende mittels Rollen so abstützend gelagert, daß er bei seiner Hin- und Herbewegung auch an seinem hinteren Endpunkt abstützend gelagert ist. Zusätzlich können diese Rollen seitlich ausgelenkt werden, so daß der Brückenträger auch eine seitliche Auslenkbewegung durchführen kann. Die seitliche Auslenkbewegung bewirkt die bei nicht exakter Bogenlage die erforderliche Schrägbogenkorrektur. Das vordere Ende dieses Brückenträgers ist über eine erste Lagerung drehbar mit der Schwinge verbunden, um so die Hin- und Herbewegung des Brückenträgers zusammen mit der Schwinge zu ermöglichen. Über eine zweite Lagerstelle ist das vordere Ende des Brückenträgers zusätzlich an der Schwinge befestigt, welche die erforderliche seitliche Auslenkbewegung des Brückenträgers ermöglicht.A known drag nozzle device of the type mentioned at the outset has a rocker arm which can carry out an oscillating back and forth movement. This pendulum movement is by means of a swing arm attached cam roller generated, which is connected to a cam disc tensile and pressure resistant. In the lower end point of the rocker arm there is an approximately horizontally aligned bridge girder, which carries out the approximately horizontally oscillating back and forth movement together with the rocker arm. This bridge girder is in its rear End supported by means of rollers so that it is also supported at its rear end point during its back and forth movement. In addition, these rollers can be deflected laterally so that the bridge girder can also perform a lateral deflection movement. The lateral deflection movement causes the required oblique arc correction if the sheet position is not exact. The front end of this bridge girder is rotatably connected to the rocker via a first bearing so as to enable the back and forth movement of the bridge girder together with the rocker. The front end of the bridge girder is additionally attached to the rocker arm via a second bearing, which enables the required lateral deflection movement of the bridge girder.

Zur Ausbildung dieser Lager werden sogenannte Gleit- oder Wälzlager verwendet. Aufgrund der recht hohen Taktfrequenz von Bogenanlegern, die bei bekannten Bogenanlegern um die 12.000 Hin- und Herbewegungen pro Stunde betragen kann, muß sich die Rotationsrichtung dieser Wälzlager entsprechend oft umkehren. Diese sehr raschen Drehrichtungsänderungen verursachen hohe Beschleunigungskräfte auf die in dem Lager vorhandenen Drehteile und verschlechtern die Schmiermittelzuführung in das Lager hinein, so daß diese Lager zu Grübchenbildung neigen. Durch die Lagerausbildung zwischen der Schwinge und dem Brückenträger in Form von zwei voneinander unabhängigen Lagern besitzt dieser Knotenpunkt ein relativ großes Eigengewicht, so daß mit entsprechend großen Schwingungen und großem Verschleiß gerechnet werden muß. Taktfrequenzen über 15.000 Hin- und Herbewegungen pro Stunde sind daher nicht möglich. Aufgrund der bauteilsbedingt vorhandenen Toleranzen zwischen Lager und Schwinge bzw. Brückenträger reichen die Anpreßkräfte der Rollen an die Abrollebenen der Schrägverstellung nach einiger Zeit infolge des durch die Umkehrung der Lauf- bzw. Drehrichtung entstehenden Schlupfes nicht mehr aus, was zusätzlich zu einem raschen Verschleiß führt.So-called plain or roller bearings are used to form these bearings. Due to the very high cycle frequency of sheet feeders, which can be around 12,000 reciprocations per hour in known sheet feeders, the direction of rotation of these roller bearings must be reversed accordingly often. These very rapid changes in the direction of rotation cause high acceleration forces on the rotating parts present in the bearing and degrade the lubricant supply into the bearing, so that these bearings tend to form pits. Due to the bearing design between the rocker and the bridge girder in the form of two mutually independent bearings, this node has a relatively large weight, so that correspondingly large vibrations and great wear must be expected. Clock frequencies over 15,000 reciprocations per hour are therefore not possible. Due to the component-related tolerances between the bearing and the rocker or bridge girder, the pressure forces of the rollers on the rolling planes of the inclined adjustment are no longer sufficient after some time due to the slip resulting from the reversal of the direction of rotation or rotation, which additionally leads to rapid wear.

DARSTELLUNG DER ERFINDUNGPRESENTATION OF THE INVENTION

Ausgehend von diesem Stand der Technik liegt der Erfindung die Aufgabe zugrunde, eine Schleppdüseneinrichtung für schnellaufende Bogenanleger anzugeben, die die aus dem Stand der Technik bekannten Nachteile nicht aufweist und die damit eine lange Standzeit sowie möglichst hohe Taktfrequenzen zuläßt.Based on this prior art, the invention has for its object to provide a drag nozzle device for high-speed sheet feeder, which does not have the disadvantages known from the prior art and which thus allows a long service life and the highest possible clock frequencies.

Diese Erfindung ist für die eingangs genannte Schleppdüseneinrichtung durch die Merkmale des Patentanspruchs 1 gegeben. Die eingangs genannte und aus dem Stand der Technik bekannte Schleppdüseneinrichtung zeichnet sich dementsprechend dadurch aus, daß als Lager zur gemeinsamen Aufnahme sowohl der Hin- und Herbewegungen als auch der zusätzlichen Auslenkbewegungen jeweils Gummimetall-Elemente, insbesonder Gummimetall-Buchsen, vorhanden sind. Derartige Buchsen sind Lagerelemente, die aus einer inneren und einer äußeren Hülse bestehen, die durch eine elastisch verformbare Masse fest miteinander verbunden sind. Derartige Buchsen sind als Konstruktionselemente bekannt. Derartige Buchsen dämpfen radial und axial auf sie wirkende Schwingungen. Sie können auf Verdrehung beansprucht werden und kardanische Auslenkungen aufnehmen. Die Erfindung basiert damit auf der Erkenntnis, daß sich unter Verwendung derartiger Buchsen Bogenanleger konstruieren lassen, bei denen die bei hohen Taktfrequenzen verstärkt auftretenden Schwingungen minimiert vorhanden sind und die eine verschleiß- und wartungsfreie Pendelbewegung ohne jegliche Schmierung zulassen. Auch ist mit Hilfe dieser Buchsen eine Schrägbogenkorrektur ohne zusätzlich bewegliche Elemente möglich.This invention is given for the above-mentioned drag nozzle device by the features of claim 1. The drag nozzle device mentioned at the outset and known from the prior art is accordingly characterized in that rubber-metal elements, in particular rubber-metal bushings, are present as bearings for jointly receiving both the back and forth movements and the additional deflection movements. Such bushings are bearing elements which consist of an inner and an outer sleeve which are firmly connected to one another by an elastically deformable mass. Such bushings are known as construction elements. Such bushes damp radially and axially acting vibrations. They can be subjected to twisting and absorb cardanic deflections. The invention is thus based on the finding that sheet feeders can be constructed using such bushings, in which the vibrations which occur increasingly at high clock frequencies are minimized and which permit a wear-free and maintenance-free pendulum movement without any lubrication. With the aid of these sockets, an inclined arc correction is also possible without additional moving elements.

Bei mit einer derartigen Schleppdüseneinrichtung ausgerüsteten schnellaufenden Bogenanlegern haben sich Taktfrequenzen von über 18.000 Hin- und Herbewegungen pro Stunde realisieren lassen.In high-speed sheet feeders equipped with such a drag nozzle device, cycle frequencies of over 18,000 reciprocations per hour have been achieved to let.

Um die grundsätzlich störenden Schwingungen zu minimieren und eine verschleiß- und wartungsfreie Pendelbewegung zu ermöglichen hat es sich als vorteilhaft herausgestellt, auch die Lager, die nur zur Aufnahme von Hin- und Herbewegungen ausgelegt werden müssen, jeweils auch als Gummimetall-Buchse auszubilden.In order to minimize the generally disturbing vibrations and to enable a wear-free and maintenance-free pendulum movement, it has proven to be advantageous to also design the bearings, which only have to be designed to accommodate back and forth movements, as rubber-metal bushings.

Unter Verwendung derartiger Gummimetall-Buchsen hat sich eine Konstruktion für eine Schleppdüseneinrichtung der eingangs genannten Art als konstruktiv einfach herausgestellt, bei der zwei Schwingen vorhanden sind, wobei die vordere Schwinge einerseits mit ihrem oberen Ende um eine erste Achse pendelnd gelagert ist und andererseits mit ihrem unteren Endbereich über zumindest eine Gummimetall-Buchse mit dem vorderen Endbereich des Brückenträgers verbunden ist. Die hintere dieser beiden Schwingen ist mit ihrem unteren Endbereich über eine Gummimetall-Buchse mit dem hinteren Endbereich des Brückenträgers verbunden und mit ihrem oberen Endbereich um eine zweite Achse pendelnd gelagert. Dieser obere Endbereich kann ferner zusammen mit der zweiten Achse eine Drehbewegung um eine dritte Achse durchführen, die quer zur zweiten Achse ausgerichtet ist. Sinnvoll hat es sich dabei erwiesen, wenn auch als Lager der ersten Achse Gummimetall-Buchsen vorhanden sind.Using such rubber-metal bushes, a construction for a trailing nozzle device of the type mentioned at the outset has proven to be structurally simple, in which two rockers are present, the front rocker being mounted on its one end with a swinging around a first axis and on the other hand with its lower one End region is connected to the front end region of the bridge girder via at least one rubber-metal socket. The rear end of these two rockers is connected with its lower end region to the rear end region of the bridge girder via a rubber-metal bushing, and its upper end region is mounted so as to oscillate about a second axis. This upper end region can also perform a rotary movement together with the second axis about a third axis, which is aligned transversely to the second axis. It has proven useful if rubber-metal bushings are also available as bearings on the first axis.

Nach einem weiteren Merkmal der Erfindung hat sich für die obere Lagerung der zweiten Schwinge als sinnvoll herausgestellt, wenn deren zweite Achse in einem Joch gelagert ist, das um ein Lager schwenkbar befestigt ist, welches Lager senkrecht zur Hin- und Herbewegung der beiden Schwingen ausgerichtet ist.According to a further feature of the invention, it has been found to make sense for the upper mounting of the second rocker if its second axis is mounted in a yoke which is pivotably attached to a bearing, which bearing is oriented perpendicular to the reciprocating movement of the two rockers .

Um auf die elastischen Andrückelemente verzichten zu können, mit denen die an der Schwinge befestigte Kurvenrolle an die die Hin- und Herbewegung steuernden Komplementärkurven angedrückt werden, hat sich eine Konstruktion für die eingangs genannte Schleppdüseneinrichtung als sinnvoll herausgestellt, bei der jede der beiden Schwingen mit einer Kurvenrolle versehen ist und zwischen diesen beiden Kurvenrollen die als Doppelkurvenscheibe ausgebildete Kurvenscheibe vorhanden ist. Dabei liegt jeweils eine dieser Doppelkurvenscheiben an einer der beiden Kurvenrollen an. Aufgrund der vorhandenen Gummimetall-Buchsen ist eine elastisch nachgiebige Lagerung der Kurvenrollen außerhalb der beiden Kurvenscheiben sichergestellt, ohne daß notwendigerweise vorhandene Abweichtoleranzen der beiden Komplementärkurven sich nachteilig auswirken könnten und zusätzliche konstruktive Maßnahmen erforderlich machen wurden. Die beiden Schwingen liegen über die beiden Kurvenrollen damit immer fest an der Doppelkurvenscheibe an.In order to be able to dispense with the elastic pressing elements with which the cam roller attached to the rocker on the the complementary curves controlling the back and forth movement are pressed, a design for the above-mentioned trailing nozzle device has proven to be useful, in which each of the two rockers is provided with a cam roller and between these two cam rollers there is a cam plate designed as a double cam plate. One of these double cam discs lies against one of the two cam rollers. Due to the existing rubber-metal bushes, an elastically resilient mounting of the cam rollers outside of the two cam disks is ensured without necessarily existing deviation tolerances of the two complementary curves could have a disadvantageous effect and additional design measures were necessary. The two rockers therefore always lie firmly on the double cam disc via the two cam rollers.

Nach einem weiteren Merkmal der Erfindung ist an dem Joch der hinteren Schwinge ein Hebel befestigt, der mit seinem freien Ende quer zu seiner Längserstreckung entweder manuell oder durch einen motorischen Antrieb verstellt werden kann. Durch Verstellen dieses Hebels läßt sich das Joch verschwenken und damit die gewünschte bzw. geforderte Schrägbogenkorrektur der Schleppdüseneinrichtung erreichen. Obwohl diese Hin- und Herbewegung des Hebels längs eines Kreisbogens erfolgt, dessen Kreismittelpunkt in der Lagerachse liegt, kann aufgrund der relativ sehr geringen Schwenkbewegung dieses Hebels derselbe so verstellt werden, daß sein freies Ende längs eines Gewindestabes, mit dem sein Ende in kämmendem Eingriff steht, verstellt wird. Der Gewindestab wird dabei entweder manuell oder durch einen motorischen Linearantrieb verstellt. Dieser Gewindestab ist frei auskragend angeordnet, so daß sein Kragarm eine leicht pendelnde Bewegung ausführen kann. Zwängungskräfte können so zwischen dem Gewindestab und dem Hebel praktisch nicht auftreten.According to a further feature of the invention, a lever is attached to the yoke of the rear rocker, which can be adjusted with its free end transversely to its longitudinal extent either manually or by a motor drive. By adjusting this lever, the yoke can be pivoted and thus the desired or required oblique arc correction of the drag nozzle device can be achieved. Although this back and forth movement of the lever takes place along a circular arc, the center of the circle of which lies in the bearing axis, due to the relatively very small pivoting movement of this lever, the same can be adjusted so that its free end along a threaded rod with which its end is in meshing engagement , is adjusted. The threaded rod is adjusted either manually or by a motorized linear drive. This threaded rod is freely cantilevered so that its cantilever arm can perform a slightly oscillating movement. So constraining forces can practically not occur between the threaded rod and the lever.

Nach einem weiteren Merkmal der Erfindung ist das Lager zwischen dem Brückenträger und der hinteren Schwinge in extremer hinterer Stellung genau in Verlängerung der Schwenkachse für das Joch, an dem die hintere Schwinge schwenkbar gelagert ist, positioniert. Damit wird erreicht, daß ein schrägliegender Bogen in unverschwenktem Zustand des Brückenträgers und damit der Querstange mit Saugdüsen aufgenommen und während des Schleppvorganges durch Verschwenken ausgerichtet wird.According to a further feature of the invention, the bearing is positioned between the bridge girder and the rear rocker in the extreme rear position exactly in the extension of the pivot axis for the yoke on which the rear rocker is pivotably mounted. This ensures that an inclined arch in the non-pivoted state of the bridge girder and thus the crossbar is taken up with suction nozzles and is aligned by pivoting during the towing process.

Durch die fest ausgerichtete Drehachse der vorderen Schwinge wird sichergestellt, daß die Querstange, die parallel zur Pendelachse dieser Schwinge ausgerichtet ist, in der vorderen extremen Pendelstellung beider Schwingen immer genau ausgerichtet zu dieser Pendelachse ist. Diese Pendelachse der vorderen Schwinge ist daher parallel zur gewünschten Ausrichtung der Pendelstange beim Ablegen eines Bogens ausgerichtet. Um diese Anforderung mit einfachen Mitteln zu erfüllen, ist nach einem weiteren Merkmal der vordere Endbereich des Brückenträgers gabelartig mit zwei Kopfstücken ausgebildet. An jedem dieser beiden Kopfstücke ist die Querstange mit ihren Schleppsaugern befestigt. Ferner ist im Bereich zwischen diesen Kopfstücken die Gummimetall-Buchse zwischen der vorderen Schwinge und der Querstange vorhanden. Die unteren Endbereiche der vorderen Schwinge enden ferner in einem Querträger, der in seinem mittleren Bereich mit besagter Gummimetall-Buchse verbunden ist und mit seinen beiden stirnseitigen Endbereichen auf den beiden Kopfstücken auflagert. Die gegenseitigen Auflagerflächen vom Querträger und von den beiden Kopfstücken weisen jeweils eine Ausrundung auf dergesalt, daß die beiden Anlageflächen bei der Hin- und Herbewegung der Schwinge aufeinander abrollen können. Die Querstange ist damit in jeder Position der Schwinge immer parallel oberhalb des Bogenstapels vorhanden.The fixed axis of rotation of the front rocker ensures that the crossbar, which is aligned parallel to the swing axis of this rocker, is always precisely aligned with this swing axis in the extreme front swing position of both rockers. This pendulum axis of the front rocker is therefore aligned parallel to the desired orientation of the pendulum rod when depositing an arc. In order to meet this requirement with simple means, according to a further feature, the front end region of the bridge girder is designed like a fork with two head pieces. The crossbar is attached to each of these two head pieces with its suction cups. Furthermore, in the area between these head pieces, the rubber-metal bushing is present between the front rocker and the crossbar. The lower end regions of the front rocker also end in a cross member which is connected in its central region to said rubber-metal bushing and is supported by its two end regions on the two head pieces. The mutual bearing surfaces of the cross member and of the two head pieces each have a fillet such that the two contact surfaces can roll on one another when the rocker moves back and forth. The crossbar is therefore always present in parallel in every position of the rocker above the sheet stack.

Weitere Merkmale und Vorteile der Erfindung ergeben sich durch die in den Ansprüchen ferner angegebenen Merkmale sowie durch das nachstehende Ausführungsbeispiel.Further features and advantages of the invention result from the features further specified in the claims as well by the following embodiment.

KURZE BESCHREIBUNG DER ZEICHNUNGBRIEF DESCRIPTION OF THE DRAWING

Die Erfindung wird im folgenden anhand des in der Zeichnung dargestellten Ausführungsbeispiels näher beschrieben und erläutert. Die einzige Figur zeigt in schematischer, perspektivischer Ansicht eine ausschnittsweise Darstellung einer Schleppdüseneinrichtung für einen schnellaufenden Bogenableger.The invention is described and explained in more detail below with reference to the embodiment shown in the drawing. The single figure shows a schematic, perspective view of a detail of a drag nozzle device for a high-speed sheet stacker.

WEGE ZUR AUSFÜHRUNG DER ERFINDUNGWAYS OF CARRYING OUT THE INVENTION

Oberhalb des hinteren Bereichs eines Stapels 10 mit übereinanderliegenden Bogen 12 ist das Gestell 14 einer Schleppdüseneinrichtung montiert. Die Schleppdüseneinrichtung ist Teil eines zeichnerisch nicht näher dargestellten schnellaufenden Bogenanlegers. Mit Hilfe dieses Bogenanlegers werden Bogen 12 nacheinander schuppenartig aufgefächert abgelegt, wie es mit den Bogen 12.1, 12.2, 12.3 zeichnerisch dargestellt ist. Diese Bogen werden dann in Transportrichtung 16 einer nicht näher dargestellten Offset-Druckmaschine zugeführt.The frame 14 of a drag nozzle device is mounted above the rear region of a stack 10 with sheets 12 lying one above the other. The drag nozzle device is part of a high-speed sheet feeder, not shown in the drawing. With the help of this sheet feeder, sheets 12 are laid out one after the other in a scale-like manner, as is illustrated with the sheets 12.1, 12.2, 12.3. These sheets are then fed in the transport direction 16 to an offset printing machine, not shown.

Von dem Gestell 14 ragt eine Welle 18 aus, die mit ihrer Drehachse 20 parallel oberhalb der Ebene 22 des Stapels 10 angeordnet ist. Auf dieser Welle 18 sind im Abstand voneinander zwei Kurvenscheiben 24, 26 drehfest angebracht. Auf der in der Zeichnung hinteren Kurvenscheibe 24 liegt drehfest eine Kurvenrolle 28 an, die ihrerseits an dem hinteren Glied 30 einer aus zwei Gliedern 30, 32 bestehenden Schwinge 34 drehfest befestigt ist. An ihren in der Zeichnung oberen Enden sind die beiden Glieder 30, 32 und damit die Schwinge 34 auf einer Welle 36 drehbar gelagert. Die Achse 38 dieser Welle 36 verläuft senkrecht zu der Längserstreckung der beiden stabförmigen Glieder 30, 32. Die Welle 36 ist fest an dem Gestell 14 in einer linken und rechten Lagerbuchse 40, 42 gelagert.A shaft 18 protrudes from the frame 14 and is arranged with its axis of rotation 20 parallel above the plane 22 of the stack 10. On this shaft 18, two cams 24, 26 are attached in a rotationally fixed manner at a distance from one another. On the rear cam disk 24 in the drawing, a cam roller 28 bears against rotation, which in turn is attached to the rear link 30 of a rocker 34 consisting of two links 30, 32 in a rotationally fixed manner. At their upper ends in the drawing, the two links 30, 32 and thus the rocker 34 are rotatably mounted on a shaft 36. The axis 38 of this shaft 36 runs perpendicular to the longitudinal extent of the two rod-shaped members 30, 32. The shaft 36 is fixedly mounted on the frame 14 in a left and right bearing bush 40, 42.

Um die Welle 38 kann daher die Schwinge eine pendelartige Hin- und Herbewegung (Bogenpfeil 44) durchführen.The rocker arm can therefore perform a pendulum-type reciprocating movement around the shaft 38 (arrow 44).

Die unteren Endbereiche 46, 48 der beiden stabförmigen Glieder 30, 32 sind über einen Querträger 50, der parallel zur Welle 38 ausgerichtet ist, miteinander biegesteif verbunden. Die Endbereiche dieses Querträgers 50 weisen eine jeweilige untere Ausrundung 52 auf, mit der sie auf einer entsprechenden Ausrundung 54 eines in der Zeichnung linken und rechten Kopfstückes 56, 58 anliegen. Die Ausrundungen 52, 54 sind derart, daß beim Hin- und Herpendeln der Schwinge 34 die Ausrundung 52 auf der Ausrundung 54 abrollend vorhanden bleibt.The lower end regions 46, 48 of the two rod-shaped members 30, 32 are connected to one another in a rigid manner via a cross member 50 which is aligned parallel to the shaft 38. The end regions of this cross member 50 have a respective lower rounding 52 with which they rest on a corresponding rounding 54 of a left and right head piece 56, 58 in the drawing. The fillets 52, 54 are such that when the rocker arm 34 oscillates back and forth, the fillet 52 remains rolling on the fillet 54.

Durch die beiden Kopfstücke 56, 58 verläuft eine Querstange 60, an der Schleppsauger 62 befestigt sind. Diese Schleppsauger 62 dienen zum Anheben d. h. Ansaugen von Bogen 12. In der zeichnerischen Darstellung sind die Schleppsauger 62 gerade zum Ansaugen des Bogens 12.1 oberhalb des Stapels 10 vorhanden.A cross bar 60, to which drag vacuums 62 are fastened, runs through the two head pieces 56, 58. These drag vacs 62 are used to lift d. H. Suction of sheet 12. In the drawing, the drag suction devices 62 are just present for sucking the sheet 12.1 above the stack 10.

Der Querträger 50 ist im Bereich zwischen den beiden Kopfstücken 56, 58 an einer Lagerbuchse 66 befestigt, die auf der Querstange 60 vorhanden ist.The cross member 50 is fastened in the area between the two head pieces 56, 58 to a bearing bush 66 which is present on the cross bar 60.

Die beiden Kopfstücke 56, 58 sind über ein Joch 68 miteinander verbunden. Dieses Joch 68 ist das in der Zeichnung linke, vordere Ende eines Brückenträgers 70. Dieser Brückenträger 70 ist über die Kopfstücke 56, 58 rechtwinklig zu der Querstange 60 mit ihren Schleppsaugern 62 angeordnet.The two head pieces 56, 58 are connected to one another via a yoke 68. This yoke 68 is the left front end of a bridge girder 70 in the drawing. This bridge girder 70 is arranged at right angles to the cross bar 60 with its suction cups 62 via the head pieces 56, 58.

Das hintere Ende dieses Brückenträgers 70 besitzt eine Lagerbuchse 72, in der eine hintere Schwinge 74 gelagert ist. Diese hintere Schwinge 74 besitzt wie die vordere Schwinge 34 zwei parallel zueinander angeordnete stabförmige Glieder 76, 78, die an den beiden stirnseitigen Enden der Buchse befestigt sind. An dem in der Zeichnung rechten Glied 78 ist eine Kurvenrolle 80 drehbar befestigt. Diese Kurvenrolle 80 liegt drehfest an der vorderen Kurvenscheibe 26 an. Die Kurvenrollen 28, 80 liegen damit von beiden Seiten aus an den beiden Kurvenscheiben 24 bzw. 26 drehfest an.The rear end of this bridge girder 70 has a bearing bush 72 in which a rear rocker 74 is mounted. This rear rocker 74, like the front rocker 34, has two parallel rod-shaped members 76, 78 which are fastened to the two ends of the bushing. On the right 78 in the drawing is one Cam roller 80 rotatably attached. This cam roller 80 bears against the front cam 26 in a rotationally fixed manner. The cam rollers 28, 80 are thus on both sides of the two cams 24 and 26 against rotation.

Die oberen Enden der beiden stabförmigen Glieder 76, 78 sind auf einer Welle 82 drehbar gelagert.The upper ends of the two rod-shaped members 76, 78 are rotatably mounted on a shaft 82.

Bei paralleler Ausrichtung der Welle 82 mit der Welle 36 der vorderen Schwinge 34, vollführen diese beiden Schwingen 34, 74 eine in derselben Ebene liegende pendelartige Bewegung. Bei dieser Pendelbewegung vollführt der Brückenträger 70 eine langgestreckte Bogenlinie ebenfalls in dieser Ebene.With parallel alignment of the shaft 82 with the shaft 36 of the front rocker 34, these two rockers 34, 74 perform a pendulum-like movement lying in the same plane. During this pendulum movement, the bridge girder 70 also executes an elongated curved line in this plane.

Die Welle 82 der hinteren Schwinge 74 ist mit ihren Endpunkten in zwei Lagerbuchsen 84, 86 drehbar gelagert. Die beiden Lagerbuchsen 84, 86 sind Teil eines Joches 88. Dieses Joch 88 ist in einem Lager 90, deren Achse 110 senkrecht zur Ebene 22 des Stapels 10 ausgerichtet ist, in einer zur Ebene 22 parallelen Ebene schwenkbar gelagert. Dieses Lager 90 ist über einen Steg 92 an dem Gestell 14 ortsfest angebracht. Das Joch 88 ragt mit einem Teilbereich über das Lager 90 nach - in der Zeichnung - hinten hinaus. Dieses hintere Teil ist als Winkelhebel 94 ausgebildet. An dem freien Ende dieses Winkelhebels 94 ist eine Bohrung 96 vorhanden. In dieser Bohrung 96 ist der Gewindestab 100 drehbar, aber in seiner Längsrichtung unverschiebbar in einem Lager 98 gelagert. Der Gewindestab 100 wird von einem am Gestell 14 fest montierten Linearantrieb 102 in seiner Längsrichtung verschoben. Bei dieser Längsverschiebung des Gewindestabes 100 wird der Winkelhebel 94 längs des Pfeils 104 nach in der Zeichnung links oder rechts verstellt. Aufgrund der auskragenden Konstruktion dieses Gewindestabes 100 und seiner relativ biegeweichen Ausbildung und darüber hinaus infolge der nur recht kleinen erforderlichen Bewegungen längs des Pfeiles 104 treten bei der linearen Verstellung längs des Gewindestabes 100 keine Zwängungskräfte in dem Lager 90 auf. Der Winkelhebel 94 läßt sich somit längs des Bogenpfeils 106 verstellen. Damit kann das Joch 88 ebenfalls längs des Bogenpfeils 106 verschwenkt werden. Diese Verschwenkung des Jochs 88 führt zu einer Verschwenkung der Lagerbuchse 72 und damit zu einer seitlichen Verstellung des Brückenträgers 70. Die Buchse 72 ist ebenfalls wie die Buchse 66 als eine sogenannte Gummimetall-Buchse ausgeführt. Diese Buchsen bestehen aus einer inneren und äußeren Hülse, zwischen denen eine elastisch verformbare Masse angeordnet ist, die mit den beiden Hülsen fest verbunden ist. Ein derartiges Lager kann in radialer und axialer Richtung sowie auf Verdrehung belastet werden und kann so auch kardanische Auslenkungen aufnehmen.The shaft 82 of the rear rocker 74 is rotatably supported with its end points in two bearing bushes 84, 86. The two bearing bushings 84, 86 are part of a yoke 88. This yoke 88 is pivotally mounted in a bearing 90, the axis 110 of which is oriented perpendicular to the plane 22 of the stack 10, in a plane parallel to the plane 22. This bearing 90 is fixedly attached to the frame 14 via a web 92. The yoke 88 projects with a partial area beyond the bearing 90 - in the drawing - beyond. This rear part is designed as an angle lever 94. At the free end of this angle lever 94 there is a bore 96. The threaded rod 100 is rotatable in this bore 96, but is mounted in a bearing 98 so that it cannot be displaced in its longitudinal direction. The threaded rod 100 is displaced in its longitudinal direction by a linear drive 102 fixedly mounted on the frame 14. During this longitudinal displacement of the threaded rod 100, the angle lever 94 is adjusted along the arrow 104 to the left or right in the drawing. Due to the cantilevered construction of this threaded rod 100 and its relatively flexible design and, moreover, due to the only very small required movements along the arrow 104, there are no constraining forces during the linear adjustment along the threaded rod 100 in the camp 90. The angle lever 94 can thus be adjusted along the arrow 106. The yoke 88 can thus also be pivoted along the arrow 106. This pivoting of the yoke 88 leads to a pivoting of the bearing bush 72 and thus to a lateral adjustment of the bridge girder 70. The bushing 72, like the bushing 66, is also designed as a so-called rubber-metal bushing. These bushings consist of an inner and outer sleeve, between which an elastically deformable mass is arranged, which is firmly connected to the two sleeves. Such a bearing can be loaded in the radial and axial direction as well as on rotation and can thus also absorb cardanic deflections.

Bei einer Verschwenkung des Joches 88 kann sich somit der Brückenträger 70 ebenfalls in zur Ebene 22 paralleler Ebene verschwenken. Da die Buchse 72 genau senkrecht unterhalb des Lagers 90 vorhanden ist, wird sich diese Buchse 72 bei einem Verschwenken des Joches 88 um das Lager 90 nur um die vertikale Achse 110 des Lagers 90 verdrehen; eine seitliche Verstellung der Buchse 72 wird nicht erfolgen.When the yoke 88 is pivoted, the bridge support 70 can thus also pivot in the plane parallel to the plane 22. Since the bushing 72 is present exactly vertically below the bearing 90, this bushing 72 will only rotate about the vertical axis 110 of the bearing 90 when the yoke 88 is pivoted about the bearing 90; lateral adjustment of the socket 72 will not take place.

Aufgrund der beiden Lagerbuchsen 66, 72 in Form von Gummimetall-Buchsen liegen die beiden Kurvenrollen 28, 80 spielfrei und drehfest an der jeweiligen Kurvenscheibe 24 bzw. 26 an. Irgendwelche Andrückmechanismen für diese Kurvenrollen sind nicht erforderlich.Because of the two bearing bushes 66, 72 in the form of rubber-metal bushes, the two cam rollers 28, 80 rest against the respective cam plates 24 and 26 without play and in a rotationally fixed manner. Any pressing mechanisms for these cam rollers are not required.

Die dargestellte Schleppdüseneinrichtung funktioniert auf folgende Weise.The drag nozzle device shown works in the following way.

Bei der in der Zeichnung dargestellten Position befindet sich der Brückenträger 70 in seiner maximalen rückwärtigen Stellung. In dieser Stellung verharrt er eine Zeitlang, um nicht dargestellten Hubdüsen die Möglichkeit zu geben, den obersten Bogen 12.1 anzuheben. Nach dessen Anheben übernehmen dann die Schleppsauger 62 den angehobenen Bogen, um ihn um das Maß s in Transportrichtung 16 weiter zu bewegen. Der Bogen 12.1 hat nach seiner um das Maß s verschobenen Lage ebenfalls den gleichen Abstand und die gleiche Ausrichtung zum Bogen 12.2, die dieser Bogen 12.2 zum Bogen 12.3 hat.In the position shown in the drawing, the bridge girder 70 is in its maximum rear position. It remains in this position for a while in order to give lifting nozzles (not shown) the possibility of lifting the uppermost sheet 12.1. After lifting it, the take over Drag vacuum 62 the raised sheet to move it further in the transport direction 16 by the dimension s. The sheet 12.1 also has the same distance and the same orientation to the sheet 12.2 as this sheet 12.2 has to the sheet 12.3 after its position shifted by the dimension s.

Um diesen Weg s zu überbrücken, vollführen die vordere und hintere Schwinge 34, 74 eine entsprechende Pendelbewegung längs des Bogenpfeils 44. Bei dieser Pendelbewegung überstreicht der Brückenträger 70 eine entsprechende bogenförmige Kurvenbahn. Diese Kurvenbahn ist aufgrund der relativ kleinen Pendelausschläge für die Praxis ausreichend gradlinig, so daß die in vertikaler Richtung vorhandene unterschiedliche Höhe der Querstange 60 bezüglich des Bogens 12.1 vernachlässigt werden kann.In order to bridge this path s, the front and rear rocker arms 34, 74 carry out a corresponding pendulum movement along the arc arrow 44. During this pendulum movement, the bridge girder 70 sweeps over a corresponding arcuate curved path. Due to the relatively small pendulum deflections, this curved path is sufficiently straightforward in practice so that the different height of the transverse rod 60 in the vertical direction with respect to the arch 12.1 can be neglected.

In der nicht dargestellten extremen linken Stellung des Brückenträgers 70, in der die beiden Schwingen 34, 74 entsprechend extrem weit geschwungen sind, werden die Schleppsauger 62 deaktiviert und der Bogen 12.1 so losgelassen.In the extreme left position, not shown, of the bridge girder 70, in which the two rockers 34, 74 have correspondingly swung extremely far, the drag suction devices 62 are deactivated and the arch 12.1 is released.

Sofern der Stapel 10 nicht die exakt gleiche Ausrichtung wie beispielsweise der Bogen 12.3 aufweist, sondern etwas schiefwinklig zu demselben ausgerichtet ist - was in entsprechender Weise auch für jeden seiner Bogen gilt - muß die Schiefausrichtung während des Transports des Bogens längs der Wegstrecke s ausgeglichen werden. In der in der Figur dargestellten Position wird nun die Querstange 60 mit den Schleppsaugern 62 durch Verschwenken des Joches 88 um das Lager 90 so in einer zur Ebene 22 parallelen Ebene verschwenkt, daß die Querstange 60 wieder parallel zu dem jeweils aufzunehmenden, nicht exakt ausgerichteten Bogen vorhanden ist; die hintere Schwinge 74 hat sich dementsprechend mit dem Brückenträger 70 seitlich verschwenkt.If the stack 10 does not have the exact same orientation as, for example, the sheet 12.3, but is oriented somewhat obliquely to the same - which also applies in a corresponding manner to each of its sheets - the skew alignment must be compensated for during the transport of the sheet along the path s. In the position shown in the figure, the crossbar 60 is now pivoted with the suction cups 62 by pivoting the yoke 88 around the bearing 90 in a plane parallel to the plane 22 such that the crossbar 60 is again parallel to the respectively not exactly aligned sheet to be received is available; the rear rocker 74 has accordingly pivoted laterally with the bridge girder 70.

Nach Aufnahme dieses nicht exakt ausgerichteten Bogens - etwa des Bogens 12.1 - schwingen nun die beiden Schwingen 34, 74 um die jeweiligen Wellen 36, 82 im Uhrzeigersinn. Die hintere Schwinge 74 wird durch die feste Ausrichtung der vorderen Welle 36 und damit auch der vorderen Schwinge 34 während dieser Pendelbewegung im Uhrzeigersinn so seitlich verstellt, daß sie in ihrer ganz linken extremen Position, in der der Bogen 12.1 übergeben werden soll, verschwenkt zur vorderen Schwinge 34 liegt und dadurch der Bogen 12.1 parallel zum Bogen 12.2 zu liegen kommt.After picking up this not exactly aligned bow - for example bow 12.1 - the two rockers 34, 74 now swing clockwise around the respective shafts 36, 82. The rear rocker 74 is laterally adjusted by the fixed alignment of the front shaft 36 and thus also the front rocker 34 during this pendulum movement in such a way that it is pivoted to the front in its extreme left extreme position, in which the sheet 12.1 is to be transferred Swing arm 34 lies and thereby the arch 12.1 comes to lie parallel to the arch 12.2.

Beim Rückwärtsschwingen in ihre in der Zeichnung dargestellte Position wird die Schwinge 74 dann wegen entsprechende Verstellung des Joches 88 wieder so ausgerichtet, wie der aufzunehmende Bogen als im Raum positioniert festgestellt worden ist.When swinging backwards into its position shown in the drawing, the rocker 74 is then again aligned because of the corresponding adjustment of the yoke 88 in the manner in which the sheet to be recorded has been found to be positioned in space.

Aufgrund der Ausbildung der beiden Buchsen 66, 72 als Gummimetall-Buchsen ist eine spielfreie Lagerung der gesamten Wippe möglich, die eine extrem hohe Taktfrequenz von Hin- und Herbewegungen pro Stunde ermöglicht.Due to the design of the two bushings 66, 72 as rubber-metal bushings, a play-free mounting of the entire rocker is possible, which enables an extremely high clock frequency of back and forth movements per hour.

Auch die Lagerbuchsen 40, 42, 84, 86 sind als Gummimetall-Buchsenlager ausgebildet. Damit wird auch für diese Lager eine spiel- verschleiß- und wartungsfreie Lagerung mit einfachen konstruktiven Maßnahmen erreicht.The bearing bushes 40, 42, 84, 86 are also designed as rubber-metal bush bearings. This means that these bearings are also free of wear, maintenance and free of maintenance with simple design measures.

Da im dargestellten Beispielsfall diese sechs Gummimetall-Buchsen 66, 72, 40, 42, 84, 86 in vertikaler Stellung der beiden Schwingen 34, 74 eingebaut werden, wirken diese Buchsen bei schnellen Pendelbewegungen der Schwingen bremsend auf die Schwingen ein, wodurch letztere zu einem ruhigen Pendellauf gezwungen werden.Since in the example shown these six rubber-metal bushes 66, 72, 40, 42, 84, 86 are installed in the vertical position of the two rockers 34, 74, these bushes have a braking effect on the rockers during rapid pendulum movements of the rockers, as a result of which the latter become one quiet pendulum run are forced.

Das Einbauen der Gummimetall-Buchsen erfordert keine exakten koaxialen Bohrungen und Achsschenkel, was die Herstellung der Einbauteile erheblich vereinfacht.The installation of the rubber metal bushings does not require exact coaxial bores and steering knuckles, which is what the manufacture of the Installation parts considerably simplified.

Aufgrund ihres relativ geringen Eigengewichts übertragen die verwendeten Gummimetall-Buchsen die erforderlichen Verdreh- und kardanischen Auslenkbewegungen auf spielfreie, wartungsfreie und verschleißfreie Art und Weise. Darüber hinaus werden durch die kardanische Verkippbarkeit der zwei Gummimetall-Buchsen 66, 72 die erforderliche Schrägstellung des Brückenträgers 70 ohne zusätzliche Rollen und Abrollebenen erzeugt.Due to their relatively low weight, the rubber-metal bushings used transmit the required twisting and cardanic deflection movements in a play-free, maintenance-free and wear-free manner. In addition, due to the cardanic tiltability of the two rubber-metal bushings 66, 72, the required inclination of the bridge girder 70 is generated without additional rollers and rolling planes.

Claims (12)

  1. Feed-nozzle device for fast-running sheet feeders having
    - an oscillating link (34, 74) which is mounted in a reciprocating, pendulating fashion,
    - a cam roller (28; 80) which interacts with the oscillating link (34, 74) and which is acted on by a cam disc (24; 26) rotatably mounted around a drive axis (18),
    - a bridge beam (70) which is approximately horizontally aligned and is mounted by means of its front end region (68) in an articulated manner in the lower region (66) of the oscillating link (34, 74),
    - a supporting device (72) for the bridge beam (70) in its rear end region which makes both the reciprocating movement and a deflecting movement, transversely aligned thereto, of the bridge beam (70) possible, and
    - a cross-beam (60) for the mounting of feed suckers (62) which is pivotably mounted in the front end region (68) of the bridge beam (70) or in the lower end region (66) of the oscillating link (34),
    characterized in that rubber-metal bushes (66, 72, 40, 42, 84, 86) are present in each case as bearings for jointly absorbing the reciprocating movements and the additional deflecting movements.
  2. Feed-nozzle device according to Claim 1, characterized in that rubber-metal bushes (66, 72, 40, 42, 84, 86) are present in each case as bearings for absorbing only reciprocating movements or as bearings of only deflecting movements.
  3. Feed-nozzle device according to Claim 1 or 2, characterized in that
    - two oscillating links (34, 74) are present,
    - the front oscillating link (34)
    -- is mounted in a pendulating fashion about a first axis (36, 38) by means of its upper end,
    -- and is joined to the front end region of the bridge beam (70) via at least one rubber-metal bush (66) by means of its lower end region (46, 48) and to the transverse rod (60) with the feed suckers (62),
    - the rear oscillating link (74)
    -- is joined to the rearmost end region of the bridge beam (70) via a rubber-metal bush (72) by means of its lower end region,
    -- and is mounted in a pendulating fashion about a second axis (82) by means of its upper end region,
    - a rotary movement can be executed by said upper end region together with said second axis (82) around a third axis (90, 110) which is aligned transversely to the second axis (82).
  4. Feed-nozzle device according to Claim 3, characterized in that rubber-metal bushes (40, 42) are present as bearings of the first axis (36, 38).
  5. Feed-nozzle device according to Claim 3, characterized in that
    - the second axis (82) is mounted in a yoke (88),
    - said yoke (88) is pivotably attached to a bearing (90),
    - said bearing (90) is aligned perpendicularly to the reciprocating movements of the two oscillating links (34, 74).
  6. Feed-nozzle device according to Claim 5, characterized in that the bearing (90) around which the yoke (88) is pivotably mounted has a rigid mounting.
  7. Feed-nozzle device according to Claim 3, characterized in that
    - a first cam roller (28) is rotatably mounted on the front oscillating link (34),
    - a second cam roller (80) is rotatably mounted on the rear oscillating link (74),
    - the cam disc is constructed as a double cam disc (24, 26) with common axis (20) of rotation,
    - one (24) of said double cam discs rests in a pressure-free and rotation-free manner on the first cam roller (28) and the other double cam disc (26) on the second cam roller (80).
  8. Feed-nozzle device according to Claim 5 or 6, characterized in that
    - a lever (94) is attached to the yoke (88),
    - the free end of said lever (94) can be displaced transversely to its longitudinal extension (104) in such a way that the yoke (88) can be swivelled (106) around the bearing (90) as a result of this displacement.
  9. Feed-nozzle device according to Claim 8, characterized in that
    - there is present in the lever (94) a bore (96) in which a threaded rod (100) is rotatably mounted, and
    - the threaded rod (100) can be displaced in its longitudinal direction (104) by a linear motor drive (102) and/or a handwheel mounted on the threaded rod.
  10. Feed-nozzle device according to Claim 2, characterized in that
    - the front end region of the bridge beam (70) terminates in a fork-shaped manner in two head pieces (56, 58),
    - the transverse rod (60) with its feed suckers (62) is attached to each of said two head pieces (56, 58),
    - the rubber-metal bush (66) is present on the transverse rod (60) in the region between said head pieces (56, 58),
    - the lower end region (46, 48) of the front oscillating link (34) terminates in a cross-beam (50)
    -- which is linked to the transverse rod (60) in its central region by means of the rubber-metal bush (66) and
    - which rests on the two head pieces (60, 58) by means of its two outermost end regions,
    - the mutual contact surfaces of cross-beam (50) and head piece (56, 58) each have a rounding (52, 54) which is such that the two contact surfaces (52, 54) can roll on one another during the pendulum movement of the oscillating links (34, 74).
  11. Feed-nozzle device according to Claim 5 or 6, characterized in that the bearing (72) between the bridge beam (70) and the rear oscillating link (74) is aligned with respect to the swivel axis (110) for the swivel movement of the yoke (88) in such a way that, in the extreme rear pendulum position of the two oscillating links (34, 74), in which a sheet (12) is present in its position at the top of the stack (10), the swivel axis (110) passes through said bearing (72).
  12. Feed-nozzle device according to Claim 1, characterized in that the rubber-metal components (66, 72) are constructed as a rubber-metal bush.
EP91904420A 1990-03-03 1991-02-27 Trailing nozzle device for fast paper feeders Expired - Lifetime EP0518894B1 (en)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE4006635A DE4006635A1 (en) 1990-03-03 1990-03-03 TOW NOZZLE DEVICE FOR HIGH SPEED BOW FEEDER
DE4006635 1990-03-03
PCT/DE1991/000160 WO1991013822A1 (en) 1990-03-03 1991-02-27 Trailing nozzle device for fast paper feeders

Publications (2)

Publication Number Publication Date
EP0518894A1 EP0518894A1 (en) 1992-12-23
EP0518894B1 true EP0518894B1 (en) 1994-09-28

Family

ID=6401313

Family Applications (1)

Application Number Title Priority Date Filing Date
EP91904420A Expired - Lifetime EP0518894B1 (en) 1990-03-03 1991-02-27 Trailing nozzle device for fast paper feeders

Country Status (6)

Country Link
US (1) US5308055A (en)
EP (1) EP0518894B1 (en)
JP (1) JPH05504927A (en)
AT (1) ATE112232T1 (en)
DE (2) DE4006635A1 (en)
WO (1) WO1991013822A1 (en)

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US4641192A (en) * 1984-12-20 1987-02-03 Magnavox Government And Industrial Electronics Company Focus-corrected convergent beam scanner
IT1293588B1 (en) * 1997-07-08 1999-03-08 Maieron Natalina SHEET FEEDER FOR HANDLING AND SINGLE FEEDING OF STACKED SHEETS
DE19815104B4 (en) * 1998-04-04 2006-06-29 Koenig & Bauer Ag Sheet separator in sheet feeders
US6062807A (en) * 1998-04-08 2000-05-16 Tekmax, Inc. Battery plate feeder having oscillating pick-up head
US6168148B1 (en) * 1999-03-19 2001-01-02 Heidelberger Druckmaschinen Ag Sheet separating device
DE19947573A1 (en) * 1999-10-01 2001-04-05 Heidelberger Druckmasch Ag Lift-drag suction gear for sheet processing machine
ITMI20020460A1 (en) * 2002-03-06 2003-09-08 Sitma Spa AUTOMATIC FEEDER DEVICE FOR SINGLE PUBLISHING PRODUCTS
US8758707B2 (en) * 2008-06-16 2014-06-24 Leica Biosystems Melbourne Pty Ltd Staining instruments and methods
DE102021115423A1 (en) 2021-06-15 2022-12-15 Koenig & Bauer Ag Feeder of a sheet processing machine and method for separating sheets

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Publication number Priority date Publication date Assignee Title
US2238435A (en) * 1938-08-17 1941-04-15 Reeves Pulley Co Bearing bushing
US2251416A (en) * 1939-03-01 1941-08-05 Chrysler Corp Spring and method of making same
US2722416A (en) * 1950-05-10 1955-11-01 Backhouse Headley Townsend Separation of sheets of paper or the like from the top of a pile
BE518748A (en) * 1952-04-03
DE2163083C3 (en) * 1971-12-18 1974-05-16 Heidelberger Druckmaschinen Ag, 6900 Heidelberg Suction head of a sheet feeder for printing machines
US3893775A (en) * 1974-05-13 1975-07-08 Gen Tire & Rubber Co Resilient bushing with long fatigue life
DE3346661C2 (en) * 1983-12-23 1985-12-12 SKF GmbH, 8720 Schweinfurt Snap ring
CS253506B1 (en) * 1985-10-10 1987-11-12 Jaroslav Jiruse Loading equipment

Also Published As

Publication number Publication date
JPH05504927A (en) 1993-07-29
EP0518894A1 (en) 1992-12-23
DE59103122D1 (en) 1994-11-03
US5308055A (en) 1994-05-03
DE4006635A1 (en) 1991-09-05
ATE112232T1 (en) 1994-10-15
WO1991013822A1 (en) 1991-09-19

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