EP1568495B1 - Machine for treating sheets to be printed - Google Patents
Machine for treating sheets to be printed Download PDFInfo
- Publication number
- EP1568495B1 EP1568495B1 EP05100276.4A EP05100276A EP1568495B1 EP 1568495 B1 EP1568495 B1 EP 1568495B1 EP 05100276 A EP05100276 A EP 05100276A EP 1568495 B1 EP1568495 B1 EP 1568495B1
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- EP
- European Patent Office
- Prior art keywords
- support
- sheet
- support segments
- sheets
- machine according
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B41—PRINTING; LINING MACHINES; TYPEWRITERS; STAMPS
- B41F—PRINTING MACHINES OR PRESSES
- B41F22/00—Means preventing smudging of machine parts or printed articles
Definitions
- the present invention relates to a machine for processing sheets of printing material, comprising a cylinder for transporting the sheets and with a sheet support rotatably mounted arch supports, which each comprise support segments for pressing the sheets to the cylinder, and was formed against the following background :
- Sheet-fed presses may have a sheet delivery, which includes in the transport direction leading gripper bars for holding leading end of the sheets to be interpreted and trailing gripper bars for simultaneous retention of trailing arc ends of the sheet.
- the set of leading gripper bars on one pair of chains and the set of trailing gripper bars can be attached to another pair of chains.
- the leading gripper bridges and the trailing gripper bridges run around an outfeed drum, which is equipped with said arch supports.
- the arch supports serve to press the respective sheet to an impression cylinder adjacent the impression cylinder when the respective leading gripper bridge has already taken the leading end of the sheet and the cooperating with this leading gripper bridge trailing gripper bridge has not yet taken the trailing end of the sheet.
- each of the leading gripper bridges runs at a certain distance relative to the trailing gripper bridge associated trailing gripper bridge latter. This distance depends on the arc length of the sheets, which may vary from job to job. A change in the arc length requires a correction of said distance in the context of a so-called format changeover of the cantilever. In this format change the leading gripper bridge is set to a greater or lesser distance relative to its associated trailing gripper bridge by the leading the Gripper bridge bearing pair of chains relative to the trailing gripper bridge bearing chain pair is adjusted.
- the arch supports are temporarily located between these two gripper bars during the circulation of the associated leading gripper bar and trailing gripper bar, an adjustment of the effective circumferential length of the arch supports to the changed distance between the gripper bars is required as part of the format change. For example, the arch supports must be shortened if in the format change the leading gripper bridge to the trailing gripper bridge must be adjusted out so that the arch supports this adjustment of the leading gripper bars do not hinder.
- the invention is therefore an object of the invention to provide a machine of the type mentioned above, the arch supports allow a comparatively small width contacted by them pressure-free corridors and have a long service life.
- the machine according to the invention for processing sheets of printing material with a cylinder for transporting the sheets and with a sheet support rotation axis rotatably mounted arch supports, which each support segments for pressing the sheet to the cylinder, is characterized in that the support segments relative to Bogen span-rotation axis skewed pivot axes are either pivotally mounted in an active position and in a passive position.
- the skewed pivot axes make it possible for the support segments to be lined up in the active position on one and the same alignment line, which is curved in a circular arc around the arch support rotation axis. Due to the aligned in the active position arrangement of the support segments whose track width or rolling line width and the corresponding width of the pressure-free corridor of the arc on which the support segments roll, be kept relatively narrow.
- a further advantage is the fact that the support segments can have segment heads for supporting pressure pads acting as treads.
- the segment heads are much more stable than that according to the prior art ( DE 100 14 417 A1 ) carrier tape used to carry the tread.
- the service life of the segment heads is practically unlimited and the service life of the pressure pads is comparatively high.
- the segment heads of the support segments in the passive position form an imbricated formation.
- the imbricated formation allows pivoting all in the passive position to be adjusted support segments of the sheet support on one and the same side of the sheet support, namely after the one of the sheet support nearest sprocket side facing away from the sheet support.
- the support segments would have to be pivoted alternately to one and the other side of the sheet support in the passive position, so that then some of the support segments between the sheet support and the sprocket and hinder the sprocket very close format setting of the sheet support would.
- Another advantage of the imbricated formation is to be seen in the fact that it makes it possible to arrange the skewed pivot axes of all the support segments at the same radial distance relative to the arch support rotation axis.
- the skewed pivot axes are accordingly on one and the same circular arc whose center of curvature is the arch support rotation axis.
- the support segments can be manufactured as identical parts that are not different from each other with respect to their segment length to be measured between the segment head and the pivot axis.
- the support segments each have a first stop and a second stop and the preferably designed as curves attacks are arranged offset from one another such that a relative to the support segments pivotable Shift lever for folding the respective support segment abuts the first stop and for unfolding this Support segment abuts the second stop.
- the adjustment of the respective support segment in the active position is thus effected by the same actuator as the adjustment of the support segment in the passive position, namely by the shift lever. Also, only a single drive is required for the two folding movements of the support segment.
- the supporting segments belong to bistable tilting jumpers, each of which has an indifferent dead position
- the tilting jumpers each comprise a spring with a spring force action line which runs in the indifferent dead position through the respective skewed pivot axes.
- the machine has a boom, the leading gripper bridges for holding leading end of the sheet and trailing gripper arms for simultaneous retention of trailing bow ends of the sheet comprises.
- the arch supports are components of a delivery drum of the serving for laying the sheet boom.
- the delivery drum presses with the sheet supports or their activated support segments the respective arc against the peripheral surface of the cylinder, so that the trailing gripper bridge can support the trailing end of the arm undisturbed by the cylinder support by a arranged on the delivery drum suction bridge.
- pawls are assigned to lock the support segments in the passive position and the pawls are lined up so that a pivotable relative to the pawls lever arm strikes in the course of its pivotal movement of the pawls successively to their operation.
- the pawls prevent an unintentional abutment of an operator to the present in the passive position support segments adjustment of these support segments in the active position.
- Such inadvertent erection of the support segments could otherwise result in a collision occurring between one of the leading gripper bars and the unintentionally erected support segments and resulting machine damage.
- the support segments an arrival and Ab Victoriainrauma assigned to each in a pivoting and thereby taking place in a parking position pivoting the support segments, wherein seen in the pivoting direction of the active position upstream of the passive position and the parking position is arranged downstream, and comprises the supply and Abstellinutter a rotatable relative to the support segments and coaxially mounted with the Bogen mon rotation axis switching ring.
- the Andschreibpolster preferably consist of a rubber-elastic and relatively soft plastic whose resistance to wear caused by abrasion (eraser effect) is inevitably relatively low.
- the cylinder to which the sheet supports press the sheet is preferably an impression cylinder whose peripheral surface is provided with a rough anti-smearing surface structure.
- the sheet to be pressed is located between the pressing pads and the anti-smearing surface structure, so that the latter can cause no abrasion on the pressure pads during printing operation.
- There is no arc between the anti-smearing surface structure and the Andschreibpolstern so that they would roll it directly on the anti-Abschmier surface structure and would be exposed by the latter a strong abrasion, when the Andschreibpolster for the Neutral would not be turned off by means of the arrival and Abstell Rhein of the impression cylinder and its anti-Abschmier surface structure.
- FIG. 1 a is a machine 1 for processing sheets 2 of substrate schematically and shown in plan view.
- the machine 1 is a sheet-fed printing press and comprises for the lithographic offset printing a printing unit 3 with a cylinder 4 and further comprises a boom 5 with a first chain conveyor 6 and a second chain conveyor 7.
- the cylinder is an impression cylinder 4.
- the endless chain 9 of the first chain conveyor 6 carry between them in a direction of transport 11 leading gripper bars 10 for holding leading end of the sheet 12 of the sheet second
- the second chain conveyor on the drive side and operator side Chain conveyor 7 also comprises on each of the two sides of the machine a sprocket 13 and an endless chain 14 circulating around the latter.
- the endless chains 14 of the second chain conveyor 7 carry trailing gripper bridges 15 for trailing arc ends 16 in the transport direction 11.
- Each of the trailing gripper bars 15 forms together with one of the leading gripper bridges 10, a pair of gripper bars, which holds the respective sheet 2 at both ends during its delivery to a delivery stack 17 toward transport.
- An arcuate support 18 to the side and a sheet support 19 located to the operator side are structurally identical to each other and serve to press the respective arch 2 against the circumferential surface of the impression cylinder 4.
- the arch supports 18, 19 are components of a skeletonized drum 20, namely a delivery drum 20, the boom 5 and are along their geometrical arch support rotation axis 21 continuously from a in FIG. 1a Format setting shown in full line for a maximum sheet width of sheet 2 in an in FIG. 1 a with phantom line indicated format setting for a minimum sheet width and also in between these two Extreme settings lying intermediate positions for medium bow widths adjustable.
- the drive-side sheet support 18 is aligned with a non-printing side edge and the operator-side sheet support 19 with the other non-printing side edge of the respective sheet 2.
- the sheet supports 18, 19 are arranged between the arranged on the drive side sprockets 8, 9 of the chain conveyor 6, 7 and their operated side sprockets motor axially displaceable.
- the optional to each other or away from each other taking place axial adjustment of the arch supports 18, 19 required drive (engine, transmission) is not shown in the drawing for reasons of clarity.
- the delivery drum 20 is a clawless support drum, i. H. it does not include a gripper system for clamping the sheets 2.
- FIG. 1b is the machine 1 in the side view and less schematic than in FIG. 1 a shown.
- FIG. 2a shows a provided for a maximum arc length of the sheet 2 format setting of the machine 1.
- the leading gripper bridge 10 is set to one of the arc length correspondingly large distance relative to the trailing gripper bar 15 of the respective gripper pair.
- This adjustment of the leading gripper bridge 10 is effected by a rotation of the sprocket 8 of the first chain conveyor 6 relative to the sprocket 13 of the second chain conveyor 7.
- This Radvertextung has one of correcting format difference corresponding phase shift of the endless chain 9, to which the leading gripper bar 10 is attached, relatively to the endless chain 14, to which the trailing gripper bridge 15 is attached, the result.
- the arch support 8 essentially comprises T-shaped support segments 22 which the respective sheet 2 in a common tangent point 23 (see.
- FIG. 1b of the delivery drum 20 and the impression cylinder 4 press on the latter.
- Segment heads 24 of the support segments 22 form a substantially from the leading gripper bridge 10 to the trailing gripper bridge 15 extending circumferential row. In the maximum format setting all support segments 22 are erected so that they protrude into the space between the two gripper bars 10, 15.
- FIG. 2b shows a format setting for a minimum arc length.
- the distance between the two gripper bars 10, 15 by a corresponding circulation angle adjustment of the first chain conveyor 6 relative to the second chain conveyor 7 relative to the in FIG. 2a shown format setting reduced by about half.
- the leading gripper bridge 10 is hineingaten in the region of the circumferential row of the support segments 22.
- This requires the folding of some of the support segments 22 in a proximal passive position 22.1, which is located radially retarded with respect to the delivery drum 20 and the first chain conveyor 6.
- By folding in the support segments 22 movement space for in parallel to the arch support axis of rotation 21 transverse direction across the sheet support 18 and the support segments 22 also extending leading gripper bar 10 is provided.
- the leading gripper bridge 10 can be moved over the retracted support segments 22 and unhindered by the latter to the remaining support segments 22 that are unfolded in a distal active position 22.2.
- the remaining in the active position 22.2 support segments 22 are still and opposite FIG. 2a unchanged aligned so that the segment heads 24 are in alignment and adjoin one another with a small gap width almost in bursts.
- the segment heads 24 are aligned unswept and form the segment heads 24 together with a concentric with the sprockets 8, 13 rolling surface, which is interrupted only by the very narrow gaps between the support segments 22.
- the misaligned in the passive position 22.1 support segments 22 are aligned so that their segment heads 24 overlap each other in a scaly formation S.
- the segment heads 24 of the folded support segments 22 each partially hide the segment head of the each adjacent support segment 22, if a basis for the arcuate axis of rotation 21 parallel line of sight is based.
- the positions 22.1, 22.2 correspondingly different orientations of the segment heads 24 are best in the three-dimensional FIG. 3 to recognize.
- the retracted support segments 22 of the drive-side sheet support 18 point to the operator-side sheet support 19 and the folded support segments 22 of the operator-side sheet support 19 point to the drive-side sheet support 18.
- All einzklappenden support segments 22 of the respective sheet support 18 and 19 are therefore folded in the same direction, namely inside the machine, so that the respective sheet support 18 and 19 after deactivation of some of their support segments 22 is still very narrow and compact and very wide along the arch support rotation axis 21 to the outside and close to the respective sprocket 13 zoom can be adjusted.
- FIG. 4 is shown using the example of the drive-side sheet support 18, that the sheet support 18, 19 are mounted in a drum frame 25 with traversal guide rails 26.
- the guide rails 26 are aligned parallel to the sheet support rotational axis 21.
- the delivery drum 20 has a suction bridge 29 for vacuum trapping the trailing arc ends 16.
- the suction bridge 29 takes over the trailing end of the sheet 16 of the respective sheet 2 from the impression cylinder 4, then the trailing gripper bridge 15 of the second chain conveyor 7 can safely detect the trailing end of the sheet 16 ,
- the arch support 18 includes a support plate 30, in which the support segments 22 about hinges 31 (see. FIG. 2a and FIGS. 5 to 7 ) are pivotally mounted around either in the passive position 22.1 and the active position 22.2.
- Each pivot 31 defines a pivot axis 32 of the respective support segment 22 as shown in FIG FIG. 5 is shown using the example of a support segment 22 shown as a detail therein.
- very tight juxtaposition of the support segments 22 in their active position 22.2 is particularly advantageous that the pivot axes 32 are skewed relative to the sheet support rotational axis 21.
- the pivot axes 32 are thus neither aligned parallel to the arcuate axis of rotation 21 nor perpendicular to the latter.
- FIG. 5 shows further that the segment head 24 is equipped with a rubber-elastic Andschreibpolster 33, which has a substantially triangular tapered, pointed profile.
- the Andschreibpolster 33 of the respective sheet support 18 and 19 contact the sheet 2 quasi along a circumferentially extending track line when they press the sheet 2 to the impression cylinder 4.
- Each support segment 22 has as stops a first curve 34 and a second curve 35.
- the support segment 22 and the curves 34, 35 are made of one and the same piece, for. B. as a casting made.
- a shift lever 36 with a cam roller 37 is pivotally mounted about the sheet support rotational axis 21 in the sheet support 18.
- the first curve 34 is substantially hook-shaped and begins at the segment head 24 opposite end of the support segment 22 and extends substantially curved to the segment head 24 out.
- the second curve 35 is substantially finger-shaped and arranged between the segment head 24 and the first curve 34.
- the shift lever 36 and its cam roller 37 occurs with one after the other of the first curves 34 in switching contact, so that the support segments 22 are folded one after the other.
- the shift lever 36 or its cam roller 37 With the second curves 35 successively in switching contact, so that one of the support segments 22 is unfolded after the other again.
- the first curves 34 are thus Einklappkurven or - attacks and serve to adjust the support segments 22 from the active position 22.2 in the passive position 22.1.
- the essentially radial erection of the support segments 22 On the other hand serve the second curves 35, which Ausklappkurven or stops are.
- Each support segment 22 forms together with its pivot 31 and a spring 38, a bistable K-jump (over-center device) K.
- the spring 38 is a tension spring and with its one spring end to the support plate 30 in a first attachment point 39 and with its other spring end attached to the support segment 22 in a second attachment point 40.
- the attachment points 39, 40 are retaining pins for suspending spring eyes of the spring 38.
- the spring 38 is permanently biased and has, as in FIG. 6 is shown, a spring force line of action 41 on which the attachment points 39, 40 are located.
- the Figures 5 and 7 show the two stable positions of the Kippsprungwerkes K, namely FIG. 5 said asset item 22.2 and FIG. 7 said passive position 22.1.
- the direction of action of the spring force action line 41 changes when the latter passes through the swivel joint 31 during the folding over of the support segment 22.
- the shift lever 36 needs with its cam roller 37, the first curve 34 in the adjustment of the support segment 22 from the active position 22.2 (see. FIG. 5 ) into the liability position 22.1 (cf. FIG. 7 ) only until the spring force line of action 41 has just happened during its side change relative to the rotary joint 31 and thus the support segment 22 its Dead position 22.3 has exceeded. Thereafter, the maintenance of the contact between the first curve 34 and the shift lever 36 is no longer required and the support segment 22 is pulled only by the spring 38 alone in the passive position 22.1; the support segment 22 automatically jumps to the selected stable position.
- Each support segment 22 is equipped with a safety device that prevents inadvertent folding and unfolding of the respective support segment 22.
- the securing devices are designed as a locking mechanism and hold the support segments 22 firmly both in the active position 22.2 and in the passive position 22.1.
- Each locking mechanism comprises a two-armed pawl 42, which locks the respective support segment 22 in the active position 22.2 on a first latching surface 43 of the support segment 22 by means of a locking hook 48, as shown in FIG FIG. 8 is shown, and locked in the passive position 22.1 to a second locking surface 44, as shown in FIG. 9 is shown.
- Each pawl 42 is sprung with a spring 45 which holds the pawl 42 in the locked position.
- the spring 45 is a leg spring seated on a pivot pin of the pawl 42. All pawls 42 of the respective support segment series are by means of one and the same actuator successively and against the effects of the springs 45 at Folding the support segments 22 unlocked.
- this actuator is the aforementioned shift lever 36, which in its multi-part and fork-shaped training except his the cam roller 37 supporting lever arm provided with a wedge surface 49 and with the latter the pawl 42 at its the pawl 48 opposite ratchet lever actuated lever arm 47.
- the lever arm 47 is pivoted about the arch support rotational axis 21 so that it abuts one after the other of the pawls 42 and just before the cam roller 37 begins to press against the first curve 34, the respective pawl 42 against the return action of the spring 45 except disabling engagement swings.
- FIGS. 10a to 10c show an arrival and Abstell driving A for selectively hiring and stopping the support segments 22 to and from the impression cylinder 4.
- the arrival and Abstell driving A includes as a central actuator a switching ring 50 with switching rollers 51, each of which another from the active position 22.2 in which the support segment 22 is employed against the counter-pressure cylinder 4 or the sheet 2 conveyed thereon, into a set-down position 22.4, in which the support segment 22 is out of rolling contact with the sheet 2 on the counter-pressure cylinder 4, and moved back.
- the segment heads 24 are closer by a few millimeters radial distance a than in the active position 22.2 on the Bogen viten rotation axis 21. Seen radially is the active position 22.2 between the Abstellposition 22.4 and the passive position 22.1, closer to the former than to the latter.
- the switching ring 50 is mounted substantially coaxially with the sheet support rotational axis 21 and rotatable relative to the support plate 30 in the latter.
- FIGS. 10a and 11a The around the arch support rotation axis 21 around taking place and depending on the rotation of the hiring or stopping the support segments 22 to or from the impression cylinder 4 serving rotational movement of the switching ring 50 is in the FIGS. 10a and 11a indicated by an arrow 52.
- Roller shafts 53 of the circumferentially equidistant from each other as the support segments 22 arranged switching rollers 51 have with respect to the delivery drum 20 radial orientations.
- Each support segment 22 has a first contact surface 54 with which it rests in the active position 22.2 on the respective switching roller 51, as shown in FIG FIG. 10b is shown, and a second contact surface 55, with which the support segment 22 abuts in the Abstellposition 22.4 on the scarf roller 51, as the latter in FIG. 11b is shown.
- the spring 38 (see. FIG. 5 ) of the Kippsprungwerkes K holds in the two positions (active position 22.2, Abstellposition 22.4), the respective contact surface 54, 55 in contact with the scarf roller 51.
- the second contact surface 55 forms a relative to the switching ring 50 inclined wedge surface and forms together with the first contact surface 54th a cam track for the switching roller 51.
- An anti-clockwise rotation of the switching ring 50 from its in FIG. 10a As a result, the rotational angle position shown results in the second contact surfaces 55 coming into opposition with the switching rollers 51 and the springs 38 of the tilting jumpers K being able to pivot the support segments 22 out of the active position 22.2 into the parking position 22.4.
- a clockwise turning back of the switching ring 50 has the consequence that the switching rollers 51 run up on the second contact surfaces 55 up to the first contact surfaces 54 and get back in the opposite with the latter, so that the support segments 22 of the contact surfaces 54, 55 against the Effect of the springs 38 are pivoted from the parking position 22.4 in the active position 22.2 and held in the latter.
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- Discharge By Other Means (AREA)
- Feeding Of Articles By Means Other Than Belts Or Rollers (AREA)
- Separation, Sorting, Adjustment, Or Bending Of Sheets To Be Conveyed (AREA)
Description
Die vorliegende Erfindung bezieht sich auf eine Maschine zum Verarbeiten von Bogen aus Bedruckstoff, mit einem Zylinder zum Transportieren der Bogen und mit um eine Bogenstützen-Rotationsachse drehbar gelagerten Bogenstützen, welche jeweils Stützsegmente zum Andrücken der Bogen an den Zylinder umfassen, und entstand vor folgendem Hintergrund:The present invention relates to a machine for processing sheets of printing material, comprising a cylinder for transporting the sheets and with a sheet support rotatably mounted arch supports, which each comprise support segments for pressing the sheets to the cylinder, and was formed against the following background :
Bogendruckmaschinen können einen Bogenausleger aufweisen, der in Transportrichtung vorlaufende Greiferbrücken zum Festhalten vorlaufender Bogenenden der auszulegenden Bogen und nachlaufende Greiferbrücken zum gleichzeitigen Festhalten nachlaufender Bogenenden der Bogen umfasst. Bei einem solchen Ausleger kann der Satz vorlaufender Greiferbrücken an einem Kettenpaar und der Satz nachlaufender Greiferbrücken an einem anderen Kettenpaar befestigt sein. Zusammen mit den Kettenpaaren laufen die vorlaufenden Greiferbrücken und die nachlaufenden Greiferbrücken um eine Auslagetrommel um, welche mit besagten Bogenstützen ausgestattet ist. Die Bogenstützen dienen dazu, den jeweiligen Bogen an einen mit der Auslagetrommel benachbarten Gegendruckzylinder anzudrücken, wenn die jeweilige vorlaufende Greiferbrücke das vorlaufende Bogenende bereits ergriffen hat und die mit dieser vorlaufenden Greiferbrücke kooperierende nachlaufende Greiferbrücke das nachlaufende Bogenende noch nicht ergriffen hat. Das durch die Bogenstützen erfolgende Andrücken des Bogens gegen den Gegendruckzylinder ist erforderlich, damit besagte nachlaufende Greiferbrücke das nachlaufende Bogenende sicher ergreifen kann. Jede der vorlaufenden Greiferbrücken läuft in einem bestimmten Abstand relativ zu der besagter vorlaufenden Greiferbrücke zugeordneten nachlaufenden Greiferbrücke letzterer vor. Dieser Abstand hängt von der Bogenlänge der Bogen ab, die sich von Druckauftrag zu Druckauftrag ändern kann. Eine Veränderung der Bogenlänge erfordert eine Korrektur besagten Abstandes im Rahmen einer sogenannten Formatumstellung des Auslegers. Bei dieser Formatumstellung wird die vorlaufende Greiferbrücke auf einen größeren oder kleineren Abstand relativ zur ihr zugeordneten nachlaufenden Greiferbrücke eingestellt, indem das die vorlaufende Greiferbrücke tragende Kettenpaar relativ zu dem die nachlaufende Greiferbrücke tragenden Kettenpaar verstellt wird. Da sich die Bogenstützen während des Umlaufes der einander zugeordneten vorlaufenden Greiferbrücke und nachlaufenden Greiferbrücke vorübergehend zwischen diesen beiden Greiferbrücken befindet, ist im Rahmen der Formatumstellung eine Anpassung der wirksamen Umfangslänge der Bogenstützen an den veränderten Abstand zwischen den Greiferbrücken erforderlich. Beispielsweise müssen die Bogenstützen verkürzt werden, falls bei der Formatumstellung die vorlaufende Greiferbrücke zur nachlaufenden Greiferbrücke hin verstellt werden muss, damit die Bogenstützen diese Verstellung der vorlaufenden Greiferbrücken nicht behindern.Sheet-fed presses may have a sheet delivery, which includes in the transport direction leading gripper bars for holding leading end of the sheets to be interpreted and trailing gripper bars for simultaneous retention of trailing arc ends of the sheet. In such a boom, the set of leading gripper bars on one pair of chains and the set of trailing gripper bars can be attached to another pair of chains. Together with the pairs of chains, the leading gripper bridges and the trailing gripper bridges run around an outfeed drum, which is equipped with said arch supports. The arch supports serve to press the respective sheet to an impression cylinder adjacent the impression cylinder when the respective leading gripper bridge has already taken the leading end of the sheet and the cooperating with this leading gripper bridge trailing gripper bridge has not yet taken the trailing end of the sheet. Pressing the sheet against the impression cylinder through the sheet supports is required to allow said trailing gripper bridge to securely grasp the trailing end of the sheet. Each of the leading gripper bridges runs at a certain distance relative to the trailing gripper bridge associated trailing gripper bridge latter. This distance depends on the arc length of the sheets, which may vary from job to job. A change in the arc length requires a correction of said distance in the context of a so-called format changeover of the cantilever. In this format change the leading gripper bridge is set to a greater or lesser distance relative to its associated trailing gripper bridge by the leading the Gripper bridge bearing pair of chains relative to the trailing gripper bridge bearing chain pair is adjusted. Since the arch supports are temporarily located between these two gripper bars during the circulation of the associated leading gripper bar and trailing gripper bar, an adjustment of the effective circumferential length of the arch supports to the changed distance between the gripper bars is required as part of the format change. For example, the arch supports must be shortened if in the format change the leading gripper bridge to the trailing gripper bridge must be adjusted out so that the arch supports this adjustment of the leading gripper bars do not hinder.
In
Deshalb liegt der Erfindung die Aufgabe zugrunde, eine der eingangs genannten Gattung entsprechende Maschine zu schaffen, deren Bogenstützen eine vergleichsweise geringe Breite der von ihnen kontaktierten druckfreien Korridore ermöglichen und eine hohe Standzeit haben.The invention is therefore an object of the invention to provide a machine of the type mentioned above, the arch supports allow a comparatively small width contacted by them pressure-free corridors and have a long service life.
Diese Aufgabe wird durch eine Maschine mit den Merkmalen des Anspruchs 1 gelöst. Die erfindungsgemäße Maschine zum Verarbeiten von Bogen aus Bedruckstoff, mit einem Zylinder zum Transportieren der Bogen und mit um eine Bogenstützen-Rotationsachse drehbar gelagerten Bogenstützen, welche jeweils Stützsegmente zum Andrücken der Bogen an den Zylinder umfassen, ist dadurch gekennzeichnet, dass die Stützsegmente um relativ zur Bogenstützen-Rotationsachse windschiefe Schwenkachsen wahlweise in eine Aktivposition und in eine Passivposition schwenkbar gelagert sind.This object is achieved by a machine having the features of
Die windschiefen Schwenkachsen ermöglichen es, dass die Stützsegmente in der Aktivposition auf ein und derselben Fluchtlinie aufgereiht sind, die kreisbogenförmig um die Bogenstützen-Rotationsachse herum gekrümmt verläuft. Aufgrund der in der Aktivposition miteinander fluchtenden Anordnung der Stützsegmente kann deren Spurbreite bzw. Wälzlinienbreite und die dementsprechende Breite des druckfreien Korridors des Bogens, auf dem die Stützsegmente abwälzen, vergleichsweise schmal gehalten werden. Ein weiterer Vorteil ist darin zu sehen, dass die Stützsegmente Segmentköpfe zum Tragen von als Laufstreifen fungierenden Andrückpolstern aufweisen können. Die Segmentköpfe sind wesentlich stabiler als das gemäß des Standes der Technik (
In den Unteransprüchen genannte Weiterbildungen werden nachfolgend im Einzelnen kurz erläutert.Further developments mentioned in the subclaims will be briefly explained in detail below.
Bei einer hinsichtlich der Bogenformatvariabilität und der Gleichteilefertigung vorteilhaften Weiterbildung bilden die Segmentköpfe der Stützsegmente in der Passivposition eine Schuppenformation. Die Schuppenformation ermöglicht ein Schwenken sämtlicher in die Passivposition zu verstellender Stützsegmente der Bogenstütze nach ein und derselben Seite der Bogenstütze, nämlich nach der einem der Bogenstütze nächstgelegenen Kettenrad abgewandten Seite der Bogenstütze. Da somit kein Stützsegment zu besagtem Kettenrad hin geschwenkt werden muss und sich kein in der Passivposition befindliches Stützsegment zwischen der Bogenstütze und dem nächstgelegenen Kettenrad befindet, kann die Bogenstütze entlang der Bogenstützen-Rotationsachse sehr dicht an das Kettenrad heran verstellt werden, falls eine große Bogenbreite der zu verarbeitenden Bogen eine derartige Formateinstellung der Bogenstütze erfordert. Wäre die Schuppenformation nicht vorhanden, müssten die Stützsegmente abwechselnd nach der einen und nach der anderen Seite der Bogenstütze in die Passivposition geschwenkt werden, so dass sich danach einige der Stützsegmente zwischen der Bogenstütze und dem Kettenrad befänden und eine dem Kettenrad sehr nahe Formateinstellung der Bogenstütze behindern würden. Ein weiterer Vorteil der Schuppenformation ist darin zu sehen, dass sie es ermöglicht, die windschiefen Schwenkachsen sämtlicher Stützsegmente im gleichen Radialabstand relativ zur Bogenstützen-Rotationsachse anzuordnen. Die windschiefen Schwenkachsen liegen demgemäß auf ein und demselben Kreisbogen, dessen Krümungsmittelpunkt die Bogenstützen-Rotationsachse ist. Demzufolge können die Stützsegmente als sich bezüglich ihrer zwischen dem Segmentkopf und der Schwenkachse zu messenden Segmentlänge nicht voneinander unterscheidende Gleichteile gefertigt werden.In a development that is advantageous in terms of sheet format variability and identical-part production, the segment heads of the support segments in the passive position form an imbricated formation. The imbricated formation allows pivoting all in the passive position to be adjusted support segments of the sheet support on one and the same side of the sheet support, namely after the one of the sheet support nearest sprocket side facing away from the sheet support. Thus, since no support segment has to be pivoted to said sprocket and there is no support segment located in the passive position between the sheet support and the nearest sprocket, the sheet support along the sheet support rotational axis can be adjusted very close to the sprocket zoom, if a large sheet width of sheet to be processed requires such format adjustment of the sheet support. If the scale formation were not present, the support segments would have to be pivoted alternately to one and the other side of the sheet support in the passive position, so that then some of the support segments between the sheet support and the sprocket and hinder the sprocket very close format setting of the sheet support would. Another advantage of the imbricated formation is to be seen in the fact that it makes it possible to arrange the skewed pivot axes of all the support segments at the same radial distance relative to the arch support rotation axis. The skewed pivot axes are accordingly on one and the same circular arc whose center of curvature is the arch support rotation axis. As a result, the support segments can be manufactured as identical parts that are not different from each other with respect to their segment length to be measured between the segment head and the pivot axis.
Bei einer hinsichtlich einer Automatisierung der Verstellung der Stützsegmente in die Aktivposition und in die Passivposition vorteilhaften Weiterbildung weisen die Stützsegmente jeweils einen ersten Anschlag und einen zweiten Anschlag auf und sind die vorzugsweise als Kurven ausgebildeten Anschläge derart zueinander versetzt angeordnet, dass ein relativ zu den Stützsegmenten schwenkbarer Schalthebel für ein Einklappen des jeweiligen Stützsegments an den ersten Anschlag anschlägt und für ein Ausklappen dieses Stützsegments an den zweiten Anschlag anschlägt. Die Verstellung des jeweiligen Stützsegments in die Aktivposition wird also durch dasselbe Betätigungselement wie die Verstellung des Stützsegments in die Passivposition bewirkt, nämlich durch den Schalthebel. Auch ist für die beiden Klappbewegungen des Stützsegments nur ein einziger Antrieb erforderlich.In an advantageous in terms of automation of the adjustment of the support segments in the active position and in the passive position development, the support segments each have a first stop and a second stop and the preferably designed as curves attacks are arranged offset from one another such that a relative to the support segments pivotable Shift lever for folding the respective support segment abuts the first stop and for unfolding this Support segment abuts the second stop. The adjustment of the respective support segment in the active position is thus effected by the same actuator as the adjustment of the support segment in the passive position, namely by the shift lever. Also, only a single drive is required for the two folding movements of the support segment.
Gemäß hinsichtlich einer kompakten Gestaltung der Anschläge vorteilhaften Weiterbildungen gehören die Stützsegmente zu bistabilen Kippsprungwerken, von denen jedes eine indifferente Totposition aufweist, und umfassen die Kippsprungwerke jeweils eine Feder mit einer Federkraft-Wirkungslinie, die in der indifferenten Totposition durch die jeweilige der windschiefen Schwenkachsen verläuft. Die Längen der Anschläge bzw. die Längen von an den Anschlägen ausgebildeten Kurvenbahnen können kurz gehalten werden, da die Anschläge nur für die der Totposition vorangehenden Verstellung der Stützsegmente benötigt werden und die Federn der Kippsprungwerke die der Totposition nachfolgende Verstellung der Stützsegmente bewirken.According to embodiments which are advantageous with regard to compact design of the stops, the supporting segments belong to bistable tilting jumpers, each of which has an indifferent dead position, and the tilting jumpers each comprise a spring with a spring force action line which runs in the indifferent dead position through the respective skewed pivot axes. The lengths of the stops or the lengths of formed on the stops cam tracks can be kept short, since the attacks are needed only for the dead position preceding adjustment of the support segments and the springs of Kippsprungwerke the dead position subsequent adjustment of the support segments.
Bei einer hinsichtlich eines ohne Flattern der Bogen und demzufolge abschmierfrei erfolgenden Auslegens der Bogen auf einen Auslagestapel vorteilhaften Weiterbildung weist die Maschine einen Ausleger auf, der vorlaufende Greiferbrücken zum Festhalten vorlaufender Bogenenden der Bogen und nachlaufende Greiferbrücken zum gleichzeitigen Festhalten nachlaufender Bogenenden der Bogen umfasst.In terms of a without flapping the sheet and thus ausschmierfrei performing the sheet on a delivery stack advantageous development, the machine has a boom, the leading gripper bridges for holding leading end of the sheet and trailing gripper arms for simultaneous retention of trailing bow ends of the sheet comprises.
Bei einer Weiterbildung, die hinsichtlich eines funktionssicheren Ergreifens der nachlaufenden Bogenenden durch die nachlaufenden Greiferbrücken vorteilhaft ist, sind die Bogenstützen Bestandteile einer Auslagetrommel des zum Auslegen der Bogen dienenden Auslegers. Die Auslagetrommel drückt mit den Bogenstützen bzw. deren aktivierten Stützsegmenten den jeweiligen Bogen gegen die Umfangsoberfläche des Zylinders, so dass die nachlaufende Greiferbrücke bei Unterstützung durch eine an der Auslagetrommel angeordnete Saugerbrücke das nachlaufende Bogenende ungestört von dem Zylinder übernehmen kann.In a development that is advantageous in terms of a functionally reliable gripping the trailing arc ends by the trailing gripper bars, the arch supports are components of a delivery drum of the serving for laying the sheet boom. The delivery drum presses with the sheet supports or their activated support segments the respective arc against the peripheral surface of the cylinder, so that the trailing gripper bridge can support the trailing end of the arm undisturbed by the cylinder support by a arranged on the delivery drum suction bridge.
Bei hinsichtlich einer hohen Bedienungssicherheit vorteilhaften Weiterbildungen sind den Stützsegmenten Sperrklinken zum Arretieren der Stützsegmente in der Passivposition beigeordnet und sind die Sperrklinken derart aufgereiht, dass ein relativ zu den Sperrklinken schwenkbarer Hebelarm im Laufe seiner Schwenkbewegung an den Sperrklinken nacheinander zu deren Betätigung anschlägt. Die Sperrklinken verhindern eine durch ein unabsichtliches Anstoßen eines Bedieners an die in der Passivposition befindlichen Stützsegmente erfolgende Verstellung dieser Stützsegmente in die Aktivposition. Eine solche unbeabsichtigte Aufrichtung der Stützsegmente könnte ansonsten eine zwischen einer der vorlaufenden Greiferbrücken und den unabsichtlich aufgerichteten Stützsegmenten erfolgende Kollision und daraus resultierende Maschinenschäden zur Folge haben.In terms of a high operating safety advantageous developments of the support segments pawls are assigned to lock the support segments in the passive position and the pawls are lined up so that a pivotable relative to the pawls lever arm strikes in the course of its pivotal movement of the pawls successively to their operation. The pawls prevent an unintentional abutment of an operator to the present in the passive position support segments adjustment of these support segments in the active position. Such inadvertent erection of the support segments could otherwise result in a collision occurring between one of the leading gripper bars and the unintentionally erected support segments and resulting machine damage.
Gemäß hinsichtlich einer weiteren Erhöhung der Standzeit der Andrückpolster, mit denen die Stützsegmente bestückt sind, vorteilhaften Weiterbildungen ist den Stützsegmenten eine An- und Abstelleinrichtung zum jeweils in eine Schwenkrichtung und dabei in eine Abstellposition erfolgenden Schwenken der Stützsegmente beigeordnet, wobei in die Schwenkrichtung gesehen der Aktivposition die Passivposition vorgeordnet und die Abstellposition nachgeordnet ist, und umfasst die An- und Abstelleinrichtung einen relativ zu den Stützsegmenten drehbar und mit der Bogenstützen-Rotationsachse koaxial gelagerten Schaltring. Die Andrückpolster bestehen vorzugsweise aus einem gummielastischen und vergleichsweise weichen Kunststoff, dessen Resistenz gegen durch Abrieb bedingten Verschleiß (Radiergummieffekt) unvermeidlich vergleichsweise gering ist. Der Zylinder, an welchen die Bogenstützen den Bogen andrücken, ist vorzugsweise ein Gegendruckzylinder, dessen Umfangsoberfläche mit einer rauen Anti-Abschmier-Oberflächenstruktur versehen ist. Im Druckbetrieb befindet sich der anzudrückende Bogen zwischen den Andrückpolstern und der Anti-Abschmier-Oberflächenstruktur, so dass letztere im Druckbetrieb an den Andrückpolstern keinerlei Abrieb verursachen kann. Im ohne Bogentransport erfolgenden Leerlauf der Maschine befindet sich kein Bogen zwischen der Anti-Abschmier-Oberflächenstruktur und den Andrückpolstern, so dass diese dabei direkt auf der Anti-Abschmier-Oberflächenstruktur abwälzen würden und durch letztere einem starken Abrieb ausgesetzt wären, wenn die Andrückpolster für den Leerlauf nicht mittels der An- und Abstelleinrichtung von dem Gegendruckzylinder und seiner Anti-Abschmier-Oberflächenstruktur abgestellt werden würden. Mittels des Schaltringes lässt sich vorteilhafterweise eine bei einer plötzlich auftretenden Druckunterbrechung rasch auszuführende Synchronverstellung sämtlicher aktivierter Stützsegmente in die Abstellposition durchführen.According to a further increase in the service life of Andrückpolster, which are equipped with the support segments, advantageous developments, the support segments an arrival and Abstelltinrichtung assigned to each in a pivoting and thereby taking place in a parking position pivoting the support segments, wherein seen in the pivoting direction of the active position upstream of the passive position and the parking position is arranged downstream, and comprises the supply and Abstellinrichtung a rotatable relative to the support segments and coaxially mounted with the Bogenstützen rotation axis switching ring. The Andrückpolster preferably consist of a rubber-elastic and relatively soft plastic whose resistance to wear caused by abrasion (eraser effect) is inevitably relatively low. The cylinder to which the sheet supports press the sheet is preferably an impression cylinder whose peripheral surface is provided with a rough anti-smearing surface structure. In the printing operation, the sheet to be pressed is located between the pressing pads and the anti-smearing surface structure, so that the latter can cause no abrasion on the pressure pads during printing operation. There is no arc between the anti-smearing surface structure and the Andrückpolstern so that they would roll it directly on the anti-Abschmier surface structure and would be exposed by the latter a strong abrasion, when the Andrückpolster for the Neutral would not be turned off by means of the arrival and Abstelleinrichtung of the impression cylinder and its anti-Abschmier surface structure. By means of the switching ring can be advantageously carried out at a suddenly occurring pressure interruption quickly synchronized adjustment of all activated support segments in the parking position.
Weitere funktionell und konstruktiv vorteilhafte Weiterbildungen ergeben sich aus der nachfolgenden Beschreibung eines bevorzugten Ausführungsbeispieles und der dazugehörigen Zeichnung.Other functionally and structurally advantageous developments will become apparent from the following description of a preferred embodiment and the accompanying drawings.
In dieser zeigt:
- Figur 1a
- eine Druckmaschine mit einem Bogenausleger in einer Draufsicht,
- Figur 1b
- die Druckmaschine in einer Seitenansicht,
- Figuren 2a und 2b
- verschiedene Formateinstellungen einer Bogenstütze einer Auslagetrommel des Bogenauslegers,
Figur 3- die Bogenstütze und eine vorlaufende Greiferbrücke des Bogenauslegers in einer dreidimensionalen Ausschnittsdarstellung,
Figur 4- die Bogenstütze und eine nachlaufende Greiferbrücke des Bogenauslegers in einer dreidimensionalen Ausschnittsdarstellung,
Figuren 5bis 7- die Funktionsweise eines ein Stützsegment der Bogenstütze umfassenden Kippsprungwerkes anhand einer Positionsabfolge,
Figuren 8 und 9- die Funktionsweise einer dem Stützsegment beigeordneten Sperrklinke anhand einer Positionsabfolge und
- Figuren 10a bis 11c
- die Funktionsweise einer An- und Abstelleinrichtung der Bogenstütze anhand einer Positionsabfolge.
- FIG. 1a
- a printing machine with a sheet delivery in a plan view,
- FIG. 1b
- the printing press in a side view,
- FIGS. 2a and 2b
- different format settings of a sheet support of a delivery drum of the sheet delivery,
- FIG. 3
- the arch support and a leading gripper bridge of the sheet delivery in a three-dimensional cutaway view,
- FIG. 4
- the arch support and a trailing gripper bridge of the sheet delivery in a three-dimensional cutaway view,
- FIGS. 5 to 7
- the operation of a tipping platform comprising a support segment of the arch support on the basis of a position sequence,
- FIGS. 8 and 9
- the operation of a subordinate to the support segment pawl based on a position sequence and
- FIGS. 10a to 11c
- the operation of a contact and Abstelleinrichtung the sheet support on the basis of a position sequence.
In
Der erste Kettenförderer 6 umfasst auf der Antriebsseite und Bedienungsseite je ein Kettenrad 8 und eine um letzteres umlaufende Endloskette 9. Die Endlosketten 9 des ersten Kettenförderers 6 tragen zwischen sich in eine Transportrichtung 11 vorlaufende Greiferbrücken 10 zum Halten vorlaufender Bogenenden 12 der Bogen 2. Der zweite Kettenförderer 7 umfasst ebenfalls auf jeder der beiden Maschinenseiten ein Kettenrad 13 und eine um letzteres umlaufende Endloskette 14. Die Endlosketten 14 des zweiten Kettenförderers 7 tragen zwischen sich nachlaufende Greiferbrücken 15 zum Halten in die Transportrichtung 11 nachlaufender Bogenenden 16. Jede der nachlaufenden Greiferbrücken 15 bildet zusammen mit jeweils einer der vorlaufenden Greiferbrücken 10 ein Greiferbrücken-Paar, das den jeweiligen Bogen 2 während seines zu einem Auslagestapel 17 hin erfolgenden Transports beidendig festhält.The endless chain 9 of the
Eine der Antriebsseite zu gelegene Bogenstütze 18 und eine der Bedienungsseite zu gelegene Bogenstütze 19 sind miteinander in spiegelsymmetrischer Weise baugleich und dienen zum Andrücken des jeweiligen Bogens 2 gegen die Umfangsoberfläche des Gegendruckzylinders 4. Die Bogenstützen 18, 19 sind Bestandteile einer in Skelettbauweise ausgebildeten Trommel 20, nämlich einer Auslagetrommel 20, des Auslegers 5 und sind entlang ihrer geometrischen Bogenstützen-Rotationsachse 21 stufenlos aus einer in
Die Auslagetrommel 20 ist eine greiferlose Stütztrommel, d. h. sie umfasst kein Greifersystem zum Einklemmen der Bogen 2.The
In
Aufgrund der Baugleichheit gelten die in der nachfolgenden Beschreibung mit Bezug auf die antriebsseitige Bogenstütze 18 gegebenen Erläuterungen im übertragenen Sinne für die bedienungsseitige Bogenstütze 19 mit. Außerdem gilt die nachfolgende Beschreibung der einen Hälfte der antriebsseitigen Bogenstütze 18 für deren diametrale, andere Hälfte mit.Due to the design uniformity given in the following description with respect to the drive-
In
Die Auslagetrommel 20 hat eine Saugerbrücke 29 zum per Vakuum erfolgenden Festhalten der nachlaufenden Bogenenden 16. Die Saugerbrücke 29 übernimmt das nachlaufende Bogenende 16 des jeweiligen Bogens 2 vom Gegendruckzylinder 4, damit danach die nachlaufende Greiferbrücke 15 des zweiten Kettenförderers 7 das nachlaufende Bogenende 16 sicher erfassen kann.The
Die Bogenstütze 18 umfasst eine Tragscheibe 30, in welcher die Stützsegmente 22 um Drehgelenke 31 (vgl.
Das Ein- und Ausklappen der Stützsegmente 22 erfolgt mittels eines Kurvengetriebes, das nachfolgend im Detail beschrieben wird. Jedes Stützsegment 22 weist als Anschläge eine erste Kurve 34 und eine zweite Kurve 35 auf. Das Stützsegment 22 und die Kurven 34, 35 sind aus ein und demselben Stück, z. B. als Gussteil, gefertigt. Ein Schalthebel 36 mit einer Kurvenrolle 37 ist um die Bogenstützen-Rotationsachse 21 schwenkbar in der Bogenstütze 18 gelagert. Die erste Kurve 34 ist im Wesentlichen hakenförmig und beginnt am dem Segmentkopf 24 entgegengesetzten Ende des Stützsegments 22 und verläuft im Wesentlichen zum Segmentkopf 24 hin gekrümmt. Die zweite Kurve 35 ist im Wesentlichen fingerförmig und zwischen dem Segmentkopf 24 und der ersten Kurve 34 angeordnet. Durch das im Uhrzeigersinn entlang der Stützsegmente 22 erfolgende Schwenken des Schalthebels 36 tritt der Schalthebel 36 bzw. dessen Kurvenrolle 37 mit einer nach der anderen der ersten Kurven 34 in Schaltkontakt, so dass die Stützsegmente 22 nacheinander eingeklappt werden. Durch das Schwenken des Schalthebels 36 entgegen dem Uhrzeigersinn tritt der Schalthebel 36 bzw. dessen Kurvenrolle 37 mit den zweiten Kurven 35 nacheinander in Schaltkontakt, so dass eines der Stützsegmente 22 nach dem anderen wieder ausgeklappt wird. Die ersten Kurven 34 sind also Einklappkurven bzw. - anschläge und dienen der Verstellung der Stützsegmente 22 aus der Aktivposition 22.2 in die Passivposition 22.1. Dem im Wesentlichen radialen Aufrichten der Stützsegmente 22 dienen dagegen die zweiten Kurven 35, welche Ausklappkurven bzw. -anschläge sind. Durch eine in Schwenkrichtung des Schalthebels zueinander versetzte Anordnung der beiden Kurven 34, 35 des jeweiligen Stützsegments 22 kann vorteilhafterweise ein und dasselbe Betätigungselement, nämlich der Schalthebel 36, sowohl zum Einklappen als auch zum Ausklappen der Stützsegmente 22 Verwendung finden.The folding and unfolding of the
Jedes Stützsegment 22 bildet zusammen mit seinem Drehgelenk 31 und einer Feder 38 ein bistabiles Kippsprungwerk (over-center device) K. Die Feder 38 ist eine Zugfeder und mit ihrem einen Federende an der Tragscheibe 30 in einem ersten Befestigungspunkt 39 und mit ihrem anderen Federende an dem Stützsegment 22 in einem zweiten Befestigungspunkt 40 befestigt. Die Befestigungspunkte 39, 40 sind Haltestifte zum Einhängen von Federösen der Feder 38. Die Feder 38 ist permanent unter Vorspannung gehalten und hat, wie dies in
Jedes Stützsegment 22 ist mit einer Sicherungseinrichtung ausgerüstet, die ein unabsichtliches Ein- und Ausklappen des jeweiligen Stützsegments 22 verhindert. Die Sicherungseinrichtungen sind als Gesperre ausgebildet und halten die Stützsegmente 22 sowohl in der Aktivposition 22.2 als auch in der Passivposition 22.1 fest. Jedes Gesperre umfasst eine zweiarmige Sperrklinke 42, die mittels eines Sperrhakens 48 das jeweilige Stützsegment 22 in der Aktivposition 22.2 an einer ersten Rastfläche 43 des Stützsegments 22 arretiert, wie dies in
Die
- 11
- Maschinemachine
- 22
- Bogenbow
- 33
- Druckwerkprinting unit
- 44
- GegendruckzylinderImpression cylinder
- 55
- Auslegerboom
- 66
- erster Kettenfördererfirst chain conveyor
- 77
- zweiter Kettenförderersecond chain conveyor
- 88th
- Kettenrad (von 6)Sprocket (from 6)
- 99
- Endloskette (von 6)Endless chain (from 6)
- 1010
- vorlaufende Greiferbrücke (von 6)leading grabber bridge (from 6)
- 1111
- Transportrichtungtransport direction
- 1212
- vorlaufendes Bogenendeleading bow end
- 1313
- Kettenrad (von 7)Sprocket (from 7)
- 1414
- Endloskette (von 7)Endless chain (from 7)
- 1515
- nachlaufende Greiferbrücke (von 7)trailing gripper bridge (from 7)
- 1616
- nachlaufendes BogenendeTrailing bow end
- 1717
- Auslagestapeldelivery pile
- 1818
- antriebsseitige Bogenstützedrive-side arch support
- 1919
- bedienungsseitige Bogenstützeoperator-side arch support
- 2020
- Auslagetrommeldelivery drum
- 2121
- Bogenstützen-RotationsachseSheet support rotation axis
- 2222
- Stützsegmentsupporting segment
- 22.122.1
- Passivpositionpassive position
- 22.222.2
- Aktivpositionactive position
- 22.322.3
- Totpositiondead position
- 22.422.4
- Abstellpositionparking position
- 2323
- Tangentialpunkttangency
- 2424
- Segmentkopfsegment header
- 2525
- Trommelrahmendrum frame
- 2626
- Führungsschieneguide rail
- 2727
- Pfeilarrow
- 2828
- Rollerole
- 2929
- Saugerbrückesuction bridge
- 3030
- Tragscheibecarrying disc
- 3131
- Drehgelenkswivel
- 3232
- Schwenkachseswivel axis
- 3333
- Andrückpolsterpressing pad
- 3434
- erste Kurvefirst turn
- 3535
- zweite Kurvesecond bend
- 3636
- Schalthebelgear lever
- 3737
- Kurvenrollefollower
- 3838
- Federfeather
- 3939
- erster Befestigungspunktfirst attachment point
- 4040
- zweiter Befestigungspunktsecond attachment point
- 4141
- Federkraft-WirkungslinieSpring-action line
- 4242
- Sperrklinkepawl
- 4343
- erste Rastflächefirst catch surface
- 4444
- zweite Rastflächesecond locking surface
- 4545
- Federfeather
- 4646
- Gelenkzapfenpivot pin
- 4747
- Hebelarmlever arm
- 4848
- Sperrhakenratchet
- 4949
- Keilflächewedge surface
- 5050
- Schaltringswitching ring
- 5151
- Schaltrolleswitching role
- 5252
- Pfeilarrow
- 5353
- Rollenachseroller axis
- 5454
- erste Kontaktflächefirst contact surface
- 5555
- zweite Kontaktflächesecond contact surface
- AA
- An- und AbstelleinrichtungOn and off device
- aa
- Radialabstandradial distance
- KK
- Kippsprungwerktilt mechanism
- SS
- Schuppenformationimbricated formation
Claims (13)
- Machine (1) for processing sheets (2) of printing material, including a cylinder (4) for transporting the sheets (2) and sheet supports (2) supported for rotation about a sheet support axis of rotation (21), each sheet support (2) comprising support segments (22) for pressing the sheets (2) against the cylinder (4),
characterized in
that the support segments (22) are supported to be selectively swivellable into an active position (22. 2) and into a passive position (22.1) about skew swivel axes (32) skewed relative to the sheet support axis of rotation (21). - Machine according to Claim 1,
characterized in
that in the passive position (22.1), segment heads (24) of the support segments (22) form a shingled formation (S). - Machine according to Claim 1 or 2,
characterized in
that the support segments belong to bistable over-centre devices (K), each of which has an indifferent dead position (22.3). - Machine according to Claim 3,
characterized in
that each over-centre device (K) comprises a spring (38) with a spring-force line of effect (41) that in the indifferent dead position, passes through the respective one of the skew swivel axes (32). - Machine according to any one of Claims 1 to 4,
characterized in
that pawls (42) for locking the support segments (22) in the passive position (22.1) are assigned to the support segments (22). - Machine according to Claim 4,
characterized in
that the pawls (42) are aligned in such a way that a lever arm (47) swivellable relative to the pawls (42) successively hits the pals (42) in the course of its swivelling movement to actuate the pawls (42). - Machine according to any one of Claims 1 to 6,
characterized in
that each support segment (22) includes a first stop and a second stop and the stops are offset relative to each other in such a way that a switching lever (36) swivellable relative to the support segments (22) hits the first stop to fold in the respective support segment (22) and the second stop to fold out the said support segment (22). - Machine according to Claim 7,
characterized in
that the stops are embodied as cams (34, 35). - Machine according to any one of Claims 1 to 8,
characterized in
that an engagement/disengagement device (A) for respectively swivelling the support segments (22) in one direction into a disengaged position (22.4) is assigned to the support segments (22), the passive position (22.1) arranged before the active position (22.2) and the disengaged position (22.4) arranged behind the active position (22.2) as viewed in the swivelling direction. - Machine according to Claim 9,
characterized in
that the engagement and disengagement device (A) comprises a switching ring (50) supported to be rotatable relative to the support segments (22) and to be essentially coaxial with the axis of rotation (21) of the sheet support. - Machine according to any one of Claims 1 to 10,
characterized in
that the sheet supports (18, 19) are parts of a delivery drum (20) of a delivery (5) for delivering the sheets (2). - Machine according to Claim 11,
characterized in
that the delivery (5) comprises leading gripper bars (10) for holding leading sheets ends (12) of the sheets (2) and trailing gripper bars (15) for simultaneously holding trailing sheet ends (16) of the sheets (2). - Method for supporting sheets (2) of printing material as they are transported in a printing press wherein support segments (22) are adjusted as a function of the format of the sheets (2) in that some of the support segments (2) are swivelled from a passive position (22.1) into an active position (22.2) about skew swivel axes (32) skewed relative to a sheet support axis of rotation (21), and wherein the sheets (29) are pressed against a cylinder (4) during printing by means of the support segments (22) that have been swivelled into the active position (22.2).
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004009703A DE102004009703A1 (en) | 2004-02-27 | 2004-02-27 | Machine for processing sheets of substrate |
DE102004009703 | 2004-02-27 |
Publications (2)
Publication Number | Publication Date |
---|---|
EP1568495A1 EP1568495A1 (en) | 2005-08-31 |
EP1568495B1 true EP1568495B1 (en) | 2014-04-23 |
Family
ID=34745307
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05100276.4A Not-in-force EP1568495B1 (en) | 2004-02-27 | 2005-01-18 | Machine for treating sheets to be printed |
Country Status (6)
Country | Link |
---|---|
US (1) | US7156021B2 (en) |
EP (1) | EP1568495B1 (en) |
JP (1) | JP4679928B2 (en) |
CN (1) | CN100467270C (en) |
DE (1) | DE102004009703A1 (en) |
HK (1) | HK1080800A1 (en) |
Families Citing this family (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN100526073C (en) * | 2004-08-30 | 2009-08-12 | 海德堡印刷机械股份公司 | Apparatus for conveying a sheet through a printing machine |
DE102012010886A1 (en) * | 2012-06-01 | 2013-12-05 | Heidelberger Druckmaschinen Aktiengesellschaft | Transmission drum for conveying sheet, has driven element movable perpendicular to rotational axis and mounted at inclined surface of pushrod and coupled with holder, where pushrod is coupled with latch assembly |
DE102017218411B4 (en) | 2017-10-13 | 2021-06-10 | Koenig & Bauer Ag | Sheet transport device and method for transporting sheets from a sheet guide cylinder to a sheet conveyor system |
EP3694718B1 (en) * | 2017-10-13 | 2021-12-01 | Koenig & Bauer AG | Sheet-processing machine comprising a sheet transport device, and method for transporting sheets from a sheet-guiding cylinder to a sheet conveyor system |
DE102017218407B4 (en) | 2017-10-13 | 2021-06-17 | Koenig & Bauer Ag | Sheet transport device and method for transporting sheets from a sheet guide cylinder to a sheet conveyor system |
DE102017012198B9 (en) | 2017-10-13 | 2022-10-06 | Koenig & Bauer Ag | Sheet transport device and method for transporting sheets from a sheet guiding cylinder to a sheet conveying system |
EP3694717B1 (en) | 2017-10-13 | 2021-12-01 | Koenig & Bauer AG | Sheet-processing machine comprising a sheet transport device, and method for transporting sheets from a sheet-guiding cylinder to a sheet conveyor system |
DE102017218413A1 (en) | 2017-10-13 | 2019-04-18 | Koenig & Bauer Ag | A sheet transporting apparatus and method for transporting sheets from a sheet guiding cylinder to a sheet conveying system |
DE102017218409A1 (en) | 2017-10-13 | 2019-04-18 | Koenig & Bauer Ag | A sheet transporting apparatus and method for transporting sheets from a sheet guiding cylinder to a sheet conveying system |
DE102017218410B4 (en) | 2017-10-13 | 2021-06-17 | Koenig & Bauer Ag | Sheet transport device and method for transporting sheets from a sheet guide cylinder to a sheet conveyor system |
WO2019072651A1 (en) | 2017-10-13 | 2019-04-18 | Koenig & Bauer Ag | Sheet-processing machine comprising a sheet transport device, and method for transporting sheets from a sheet-guiding cylinder to a sheet conveyor system |
DE102017218412A1 (en) | 2017-10-13 | 2019-04-18 | Koenig & Bauer Ag | A sheet transporting apparatus and method for transporting sheets from a sheet guiding cylinder to a sheet conveying system |
CN113319601B (en) * | 2021-06-01 | 2022-12-23 | 广东艾普升智能装备有限公司 | Digit control machine tool convenient to change cutter |
Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4315513A1 (en) * | 1993-05-10 | 1994-11-17 | Heidelberger Druckmasch Ag | Device for adapting the format of a sheet transfer drum |
Family Cites Families (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US3442506A (en) * | 1967-06-30 | 1969-05-06 | Miehle Goss Dexter Inc | Antismudge sheet transfer device |
DE2518334C2 (en) * | 1975-04-25 | 1976-11-11 | Heidelberger Druckmasch Ag | ARCH SUPPORT DISC FOR ARCH TRANSFER DRUMS |
DE2813136C3 (en) * | 1978-03-25 | 1986-04-17 | Heidelberger Druckmaschinen Ag, 6900 Heidelberg | Sheet carrying device which is arranged axially and adjustable in the circumferential direction on a transfer drum |
DE3364404D1 (en) * | 1982-03-16 | 1986-08-14 | Agfa Gevaert Nv | Sheet-holding apparatus |
US5839030A (en) * | 1995-11-13 | 1998-11-17 | Agfa-Gevaert N.V. | Drum-type imagesetter with variable diameter |
US6684774B2 (en) | 1997-05-09 | 2004-02-03 | Heidelberger Druckmaschinen Ag | Sheet-fed rotary printing press |
DE19826891A1 (en) | 1998-06-17 | 1999-12-23 | Heidelberger Druckmasch Ag | Sheet-fed rotary printing machine |
DE19719624C1 (en) | 1997-05-09 | 1998-06-10 | Heidelberger Druckmasch Ag | Sheet-fed rotary press with printing-varnish units |
JP2000177104A (en) * | 1998-12-18 | 2000-06-27 | Mitsubishi Heavy Ind Ltd | Intermediate cylinder of sheet-fed press |
DE19912709C2 (en) * | 1999-03-20 | 2000-12-28 | Koenig & Bauer Ag | Transfer drum with swiveling drum caps |
DE10014417A1 (en) * | 2000-03-24 | 2001-09-27 | Heidelberger Druckmasch Ag | Device for transporting a sheet for a rotary printing machine |
DE10355045B4 (en) * | 2002-12-20 | 2018-09-06 | Heidelberger Druckmaschinen Ag | Method for varying a drum profile of a vario drum and a vario drum for carrying out the method |
JP2005007858A (en) * | 2003-06-18 | 2005-01-13 | Heidelberger Druckmas Ag | Method for operating machine for processing printing-paper sheet |
-
2004
- 2004-02-27 DE DE102004009703A patent/DE102004009703A1/en not_active Withdrawn
-
2005
- 2005-01-18 EP EP05100276.4A patent/EP1568495B1/en not_active Not-in-force
- 2005-02-24 JP JP2005048405A patent/JP4679928B2/en not_active Expired - Fee Related
- 2005-02-28 CN CNB2005100524718A patent/CN100467270C/en not_active Expired - Fee Related
- 2005-02-28 US US11/068,297 patent/US7156021B2/en not_active Expired - Fee Related
-
2006
- 2006-01-17 HK HK06100721.0A patent/HK1080800A1/en not_active IP Right Cessation
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE4315513A1 (en) * | 1993-05-10 | 1994-11-17 | Heidelberger Druckmasch Ag | Device for adapting the format of a sheet transfer drum |
Also Published As
Publication number | Publication date |
---|---|
HK1080800A1 (en) | 2006-05-04 |
EP1568495A1 (en) | 2005-08-31 |
US20050188869A1 (en) | 2005-09-01 |
JP2005238844A (en) | 2005-09-08 |
CN1660574A (en) | 2005-08-31 |
DE102004009703A1 (en) | 2005-09-15 |
CN100467270C (en) | 2009-03-11 |
US7156021B2 (en) | 2007-01-02 |
JP4679928B2 (en) | 2011-05-11 |
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