EP0742170B1 - Vorrichtung zum Zuführen einer kontinuierlich ankommenden Bahn in einer Station, die sie in angehaltenem Zustand bearbeitet - Google Patents

Vorrichtung zum Zuführen einer kontinuierlich ankommenden Bahn in einer Station, die sie in angehaltenem Zustand bearbeitet Download PDF

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Publication number
EP0742170B1
EP0742170B1 EP96106944A EP96106944A EP0742170B1 EP 0742170 B1 EP0742170 B1 EP 0742170B1 EP 96106944 A EP96106944 A EP 96106944A EP 96106944 A EP96106944 A EP 96106944A EP 0742170 B1 EP0742170 B1 EP 0742170B1
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EP
European Patent Office
Prior art keywords
roller
shaft
axis
fact
rotation
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Expired - Lifetime
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EP96106944A
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English (en)
French (fr)
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EP0742170A3 (de
EP0742170A2 (de
Inventor
Edouard Borel
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Bobst Mex SA
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Bobst SA
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Publication of EP0742170A3 publication Critical patent/EP0742170A3/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H20/00—Advancing webs
    • B65H20/02—Advancing webs by friction roller
    • B65H20/04—Advancing webs by friction roller to effect step-by-step advancement of web
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H23/00—Registering, tensioning, smoothing or guiding webs
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H20/00—Advancing webs
    • B65H20/24—Advancing webs by looping or like devices
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B65—CONVEYING; PACKING; STORING; HANDLING THIN OR FILAMENTARY MATERIAL
    • B65H—HANDLING THIN OR FILAMENTARY MATERIAL, e.g. SHEETS, WEBS, CABLES
    • B65H2404/00—Parts for transporting or guiding the handled material
    • B65H2404/10—Rollers
    • B65H2404/14—Roller pairs
    • B65H2404/142—Roller pairs arranged on movable frame
    • B65H2404/1421—Roller pairs arranged on movable frame rotating, pivoting or oscillating around an axis, e.g. parallel to the roller axis
    • B65H2404/14211—Roller pairs arranged on movable frame rotating, pivoting or oscillating around an axis, e.g. parallel to the roller axis the axis being one the roller axis, i.e. orbiting roller

Definitions

  • the present invention relates, within a machine comprising several successive workstations, with one device feeding a strip of material into a station working on it stopping, this strip running in the machine continuously.
  • a stationary workstation can be a platen printing press or cutting.
  • the platen press is a machine station which requires a temporary stop of the tape running during the operation printing or cutting it occurs, due to the power continuous, an accumulation of tape in the form of an upstream mouth.
  • the function of the feeding device is to create cyclically and permanently check this mouth which lengthens during the stop due to work of the platen press, and which shortens as soon as the supply to the press resumes for the subsequent operation, these operations are scrolling cyclically.
  • Such a feeding device is necessary because that a floating mouth causes from a certain speed of scrolling of the strip of positioning faults of this strip in the hurry. To this end, several feeding devices have already been designed.
  • Document US 4,060,187 describes a supply device comprising two lateral circular plates mounted facing each other side walls of the frame, and this in rotation along a first axis.
  • Counterweights diametrically opposite the cylinder are also mounted on the discs. Since the time to stop at the maximum of the mouth is relatively short, it is expected, at this level, an early and then late correction of the position angular bearings holding the cylinder in the turntables, which extend this deadline.
  • a screw device makes it possible to modify the eccentricity of the cylinder and counterweights, so the length of the loop, depending on the cutting or printing format.
  • Another type of feeding device comprises a first drive roller, also called “roll call” or “drive sensitive ", around which a second satellite roll mounted around two lateral levers pivoting on the axis of this drive roller: first towards upstream to temporarily increase the path of the strip, which stops the portion of tape under the downstream stage, then downstream to introduce very quickly the next portion in the deck.
  • a first drive roller also called “roll call” or “drive sensitive”
  • second satellite roll mounted around two lateral levers pivoting on the axis of this drive roller: first towards upstream to temporarily increase the path of the strip, which stops the portion of tape under the downstream stage, then downstream to introduce very quickly the next portion in the deck.
  • the pinion for driving the roller satellite is meshed with a gear of equal size secured to the axis of the drive roller. This absence of sliding avoids altering printing in the case of a printed strip which is in contact with the satellite roll by its printed side, and it keeps the relative positioning of the strip in the platen press relative to the other stations upstream.
  • EP-A 0 305 230 which corresponds to the preamble of claim 1, describes another device of this type in which the satellite roller located downstream and above the band oscillates in an oblique plane oriented downwards under the drive cylinder to form a loop developing downward.
  • the tension in the tape is held at the entrance to the platen press by means of a "sliding" cylinder, that is to say a cylinder rotating at high speed and against which the strip is maintained by suction due to radial conduits bringing communication the external surface and an internal box placed under vacuum more or less strong, and whose extent corresponds to the contact surface.
  • this rotary vacuum cylinder is not very reliable at high speed and its maintenance is delicate.
  • the strip is delivered to itself over a long distance between the oscillating roller and the sliding cylinder, distance over which can appear significant fluctuations as we increase the cadence.
  • the object of the present invention is a supply device of a band in a station working it at a standstill, this band arriving from upstream stations continuously, which is able to support a high rate, for example greater than 350 cycles per minute, while ensuring high precision of the belt stop position in the platinum, of the order of 1 / 10th of a millimeter.
  • the structure and the arrangement of the constituent parts of this device must be relatively simple to reduce production costs accordingly and allow the vibrations in the vertical plane and the band flutter.
  • a device as described in claim 1 including especially a first drive roller around which oscillates upstream then downstream a second satellite roller mounted on two lateral levers pivoting on the axis of this drive roller, the drive pinion of the satellite roller being meshed with a gear of equal diameter secured to the axis of the roller drive (wheel along which the pinion rolls during oscillations satellite roller), because it further comprises a counterweight driven in rotation from the gear of the axis, this counterweight being mounted on a arm pivoting around the axis and connected by a mechanism to the levers for oscillate in the opposite direction of the satellite roller.
  • the counterweight pinion has a diameter identical to that of the gear wheel of the axle with which it is also meshed; the counterweight presenting moments of inertia with respect to its axis of central rotation and relative to the axis of the arm identical to those of satellite roll.
  • one of the levers holding the satellite roller has a toothed segment in the form of a circular sector centered on the axis of the drive roller, and meshed with a first integral toothed wheel an axis of return parallel to this axis of the drive roller, a second toothed wheel secured to the return axle being meshed with a wheel inverter itself geared to a circular toothed sector of the arm swivel carrying the counterweight.
  • This relatively simple mechanism allows to give the arm and the counterweight an oscillation exactly in the right direction reverse levers and satellite roller.
  • the satellite roll is located above the roll and oscillates in a substantially horizontal plane to optimize the potential length of the stopped tape.
  • the band then goes below of the drive roller and exits above the satellite roller.
  • the counterweight oscillates in the same horizontal plane as the satellite roll, which moreover achieves a compensation of the upstream / downstream constraints of the device on the frame.
  • this assembly simulating a second roller satellite moving in opposite direction, allows to reuse the combination a drive roller and a satellite roller to form a loop, but at much higher rates.
  • An advantage retained by this device according to the invention is that the law of advancement of the strip includes an acceleration phase in which the value and the variation acceleration are controlled, in particular so that at start of the tape, which is a critical phase since it is necessary to ensure the detachment of the belt from the platen press tool, this acceleration and its variation have a low value, and that the acceleration then increases gradually.
  • a pressure roller or a plurality of pressure rollers, is installed from the axis of the roller satellite through elastic means to press the strip of material against the satellite roller with a predetermined pressure, and this close to the start line of the strip out of this satellite roll.
  • the device also includes a telescopic shelf guiding the strip between the exit of the oscillating satellite roll and the entry of the station working the stationary band, this tablet comprising a pair of quasi-stationary horizontal downstream combs located one above the other and fixed, in rotation, to the entrance to the workstation, and a pair of combs upstream and downward oscillating horizontal located at the exit of the roller satellite (ie at the level of the upper generator) and fixed in rotation around the axis of this satellite roll; the upper oscillating combs and lower being respectively held in sliding, for example by rails or slides, in line with stationary downstream combs with their teeth offset laterally.
  • the downstream combs are held respectively by an upper cross member and a lower cross member integral with a pair of side rails whose downstream ends are mounted rotating near the entrance to the workstation, and whose ends upstream are engaged in external rollers mounted on two plates side pivoting on the axis of the satellite roller.
  • the upstream combs are then held by a vertical pair of solid or tubular sleepers secured to the side plates.
  • the pressure roller is mounted on two horizontal side levers articulated respectively on each plate lateral oscillating, one or a pair of vertical lateral cylinders mounted also against the plates exerting a pressure force on the levers predetermined.
  • the combs are confined in two half-caissons: one quasi-stationary attached to the entrance to the work station and the other oscillating connected in rotation to the axis of the satellite roller that it encompasses, the teeth of the lower combs being supported individually by vertical plates emerging orthogonally from caisson bottoms, the teeth of the upper combs being supported by vertical plates or tubes descending from the ceilings, the interpenetration of these plates or tubes forming longitudinal flow chambers of the air emerging, at the bottom of each respective box, in rooms transverse with side windows.
  • the air flows generated by the displacements intermittent band and combs are channeled in a plane horizontal to prevent the strip from being pressed against friction upper or lower combs.
  • a vertical pair of towing rollers is mounted near the entrance to the next stationary work station, such as a platen press, (or at the outlet of the telescopic shelf) to supply the belt with the correct tension in this station.
  • a device for driving one of the towing rollers particularly well associated with the supply device described previously includes a belt passing through a pulley secured to the tractor rollers as well as by two discs located respectively on each of the two branches of a vertical lever mounted free to rotate on the axis of the drive roller; the upper disc being integral with the axis of transmission from the satellite roller, which transmission axis crosses the upper arm of the lever and prints the roller oscillation on it satellite; the lower disc, of diameter identical to that of the upper disc, being held by the lower arm of the lever so as to have a position symmetrical to the upper disc with respect to a line connecting the axis of the tractor roller and the axis of rotation of the lever when it is in middle position of oscillation.
  • the diameter of the disc upper is also identical to that of the satellite roller, then, this device to lift and oscillating discs gives the belt a movement of advance intermittent whose speed is strictly identical to that of the belt of paper. If the diameters of the pulley and the tractor roller are extra identical, then this roller pulls the tape at exactly the same speed, therefore with an always constant tension pre-established.
  • the diameter of the disc may be different from that of the satellite roller provided that the diameters of the pulleys and tractor roller have proportionally the same difference.
  • the device drive is then completed, at this pulley of the roller tractor, by a rear return pulley and a return pulley, the symmetry between the discs and between the roller pulley and the deflection pulley being made in relation to the line connecting the axis of the rear pulley and the axis of lever rotation.
  • the feeder sequential of a band 3 in a station 1 working it at standstill, such than a platen press, this strip arriving upstream continuously mainly comprises a drive roller 10, arranged transversely to the direction of travel of the strip, and above which a satellite roller 20 oscillates, parallel to the roller drive 10, this satellite roller oscillating from upstream to downstream between the positions 20 and 20 'substantially in a horizontal plane.
  • the moving strip 3, guided by feed rollers 5 and 5 'pass in below the drive roller 10 performs there between a half and three-quarters of a turn up before going over the roller satellite 20 whose output is located at the tools of the platen press 1.
  • the upstream movement of the satellite roll of the position 20 'to 20 momentarily extends the last loop of the strip, which then stops the portion located in the platen press 1.
  • the central axis 12 of the roller drive 10 is held by bearings in the right side walls 7, central 8 and left 9 of the frame, the walls 7 and 8 close together forming a bathtub.
  • This drive roller 10 is driven by a motor-reducer 18 illustrated schematically on the wall 7 directly in the extension of the axis 12.
  • a main toothed wheel 14 is integral with this drive axis 12.
  • the central axis of rotation 27 of the satellite roller 20 is, for its part, held by bearings 28 in the upper end of two levers 55, 52/53 both mounted in rotation through bearings on the roller axis 12 training.
  • the lower branches 53 of these levers are united rigidly by a low inertia cylinder-cross 56.
  • the end of the axis 27 satellite roller 20 is integral with a pinion 29 meshed with the wheel main gear 14. More particularly, this pinion 29 and gear 14 have an identical diameter, so that the average speeds of rotation of the drive rollers 10 and satellite roller 20 are strictly identical.
  • a beautiful 50 hung by means of a bearing on the axis 27 of the satellite roller 20 makes it possible to pull the latter cyclically from upstream to downstream, the parallelism of the roller 20 relative to the roller 10 being maintained by to the cylinder crosses 56.
  • the device according to the invention further comprises a counterweight 80 in the form of a cylindrical mass mounted in rotation around an axis 74 mounted through a bearing at the upper end of a swing arm 70 rotating itself, through a bearing 71, around the axis 12 of the drive roller 10.
  • the axis 74 is also integral with a counterweight pinion 76 meshed with the wheel main gear 14.
  • the diameter of the pinion 76 is equal to that of this wheel main gear 14 so that the average speed of rotation of the counterweight 80 is identical to that of the satellite roller 20.
  • the axis of rotation of the lever 52/53 consists of a cylinder 51 on the one hand held in the central wall 8 by an external bearing and on the other hand holding, also at means of bearings, the through axis 12 for driving the roller 10.
  • This cylinder 51 is completed at its outer end, that is to say between the walls 7 and 8 of the frame constituting a bathtub, by a toothed segment 54 in shape of circular sector centered on the axis of rotation 12 of the roller 10.
  • This toothed segment 54 is meshed with a first return wheel 61 secured to a return axle 60 held at each end by bearings in the walls of the bath 7, 8.
  • a second wheel of return 62 secured to the return axis 60 meshes with an inverting wheel 65 whose axis of rotation, not illustrated, is also held at each end by bearings in the walls 7 and 8 of the bath.
  • This reversing wheel 65 is also meshed with a toothed sector 67 of the arm 70, this sector 67 being centered on the bearing 71 of the arm.
  • This mechanical transmission prints on the arm 70 an oscillation in rotation in the opposite direction levers 55, 52/53.
  • this counterweight 80 is dimensioned so that its moment of inertia with respect to its center of rotation and with respect to axis 12 of the drive roller 10 is identical to the moment of inertia corresponding to the satellite roller 20, compensation is obtained for momentary variations in torque causing the load on the gear motor 18 on axis 12, admittedly important, is rigorously constant, which allows the use of particularly efficient electric motors of the type "brushless".
  • the counterweight is going to be dimensioned in mass so as to counterbalance the effect of the mass of the satellite system, and this in a horizontal plane and for the part close to the frame 8.
  • two side plates 21 are mounted in rotation about the axis 27 of the satellite roller 20. These plates are engaged by rollers 23 in guide rails 24 mobile in rotation 25 at their downstream end, i.e. close to the press with plate 1.
  • a lever horizontal 32 On the internal face of each plate is mounted a lever horizontal 32 whose upstream end is held by an axis of rotation then that the downstream end is held by a remote-controlled cylinder, the pressure roller being rotatably mounted on these two levers. So we can adjust by means cylinders 34 the pressure force of the roller 30 against the satellite roller 20.
  • the side plates 21 guided by the rails 24 keep the combs by means of two cross tubes 22 upper and lower oscillating downstream 45 in the extension of the combs stationary 44 held in turn by cross tubes 42 fixed to these same rails 24.
  • the side plates 21 always remain correctly aligned along the rails 24, and the same is true for the combs constituting a double guide shelf for the paper strip running at very high speed when introduced into the platen press 1.
  • the strip 3 remains flat and keeps its register.
  • Figures 4 and 5 illustrate an alternative of the first embodiment in which the combs constituting the double telescopic shelf are confined in two half-boxes: a quasi-stationary 78 downstream connected by a fastener 97 in rotation at a fixed point close to the entrance to the station, or directly to the lower plate if its stroke is short; and an oscillating 79 with the satellite roller 20 which it encompasses and to the axis of which it is connected in rotation, these two half-boxes being connected to each other by longitudinal sliding rails not shown.
  • the downstream half-box 78 has a significant primary ceiling 84 connected at its downstream end to two small side walls 93 of length between a quarter and a fifth of the length of the ceiling, walls themselves connected to a secondary bottom 83 of length between a third and a quarter of the length of the ceiling.
  • Teeth 47 start from the bottom edge of a vertical transverse upper end half-wall, the edge of which upper is connected to the ceiling 84, and terminate substantially in the middle of the ceiling.
  • the vertical plates 87 only start from a certain distance from the transverse half-wall, for example equivalent to a tenth of the length of the ceiling, to create a transverse chamber upper 96 'opening on both sides on side windows upper 94 formed in the side walls.
  • the upstream half-box 78 has a substantial bottom primary 82, if desired partially glazed, connected, at the level of the satellite roller 20, with two side walls 90 oblique upstream except for an advanced triangular downstream, walls themselves connected to a secondary ceiling 85 having a series of longitudinal grooves corresponding to the vertical upper plates 87 of the downstream half-box 78.
  • the faces upper of the primary bottom 82 and secondary ceiling 85 of the half-box upstream 79 are at height with the lower faces respectively of the bottom secondary 83 and primary ceiling 84 of the downstream half-box 78, faces of contact where sliding support rails can be installed.
  • the primary bottom 82 ends upstream, at the roller satellite 20, in an oblique plate held by the side walls 90, plate oblique from which triangular ribs 88 support the teeth lower upstream comb 48.
  • These teeth are here in the form of sheets longitudinal horizontal laterally between two structures upper tubulars 86.
  • each of the tubular structures 86 and at level of this intermediate horizontal plate 77 is installed one of a series of pressure rollers 31, corresponding to pressure roller 30 of the figure 1, permanently keeping the strip pressed against the roller satellite 20.
  • the lower plates 88 and 89 create chambers 99 horizontal longitudinal lower telescopic, while the plates 87 associated with tubular structures 86 create chambers horizontal longitudinal upper 98 also telescopic. These chambers impose on the ambient air stirred by the oscillating movement of the semi-box 79 of the horizontal flows reaching the transverse chambers upstream 91 and downstream 96 where these flows enter and exit laterally always at the horizontal. Vertical air flows likely to flatten so harmful band against upper or lower shelf are so practically annihilated in this alternative of the first embodiment.
  • Intermittent lower roller drive could be carried out by means of an electric motor modulated in speed. However, at the envisaged rates, the piloting of such an engine would be delicate, would pass necessarily by a slightly higher speed setpoint involving a variable slip likely to damage the surface of the bandaged. Intermittent mechanical drive based on cams could also be considered. However, such a mechanism would also prove to be difficult, bulky and expensive. In addition, it would induce strong modulation in the general drive torque of the machine, which is precisely the reverse of the aims sought.
  • uses the drive of the satellite roller to carry out a drive secondary differential of the tractor roller 40 as illustrated in FIG. 6, and partially on the left side of Figure 2.
  • This drive first comprises a bent vertical lever 33 located on the external face of the wall 9 on the driver side and mounted free in rotation on an extension of the axis 12 of the roller drive 10.
  • the end of the upper branch substantially vertical of the lever is crossed by an extension of the axis 27 drive of the satellite roller giving this lever its movement oscillation.
  • a first upper disc 35 is mounted at the end of this axis 27, either at the end of this upper branch of the lever 33, and is therefore rotated at the same angular speed as the roller satellite.
  • the end of the lower branch oblique downstream of the lever 33 carries a second lower disc 36 whose diameter is identical to the disc superior.
  • This training then includes a training hen 37 integral with the end of the axis of the tractor roller 40 and located on the face external of the wall 9 in the same vertical plane containing the disks 35 and 36 thus allowing the installation of an endless belt 59 passing around these discs and pulley.
  • a pulley is also provided rear 38 and a return pulley 39 from the belt to the lower disc 36.
  • the angle of the lever 33 and the layout of the chicken 39 are such that the path of the belt 59 has symmetry with respect to the line (x) connecting the axis of rotation 12 of the lever and axis of rotation of the rear pulley 38 when the upper branch of the lever 33 is vertical, ie in the middle position of oscillation. So, when the satellite roller and the upper disc 35 are pulled back towards position a1, the increase in the upper horizontal path of the belt 59 is compensated by a decrease of equal value of the path path between the return pulley 39 and the lower disc 36 having advanced in its position a1. A reverse effect appears when advancing the disc 35 towards position a2 causing the lower disc 36 to recede. Thanks to this layout, the length of the path remains practically constant, the minimal variations being absorbed without further by the elasticity of the belt.
  • the diameter of the disc 35 is equal to that of the satellite roller 20 to which it is directly connected, and that the diameter of the hen 37 is equal to that of the tractor roller 40 at which it is also directly linked, we can see that the speed and intermittent acceleration of movement of the belt 59 between the disc 35 and the pulley 37 is strictly identical to that of the band 3, and it the same is true for the peripheral speed of the tractor roller 40.
  • This roller 40 therefore effectively pulls the tape at the right time, and this under a constant voltage preset.
  • the diameter of the disc 35 can be different from that of roller 20 as long as it is the same between the pulley 37 and roller 40.
  • the counterweight 80 will then be resized to also balance the additional inertias of the rollers 40, 41, etc. (see figure 6).
  • the tube 10 can be replaced by the extension of axis 60 to frame 9 and addition of an arrangement pinion / toothed segment analogous to the figures 61/54 on the lever 55, the tube 10 and the extended axis 60 each having specific advantages in the convenient.

Landscapes

  • Advancing Webs (AREA)
  • Replacement Of Web Rolls (AREA)
  • Controlling Rewinding, Feeding, Winding, Or Abnormalities Of Webs (AREA)
  • Folding Of Thin Sheet-Like Materials, Special Discharging Devices, And Others (AREA)
  • Sewing Machines And Sewing (AREA)
  • Manufacturing Of Electric Cables (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Electric Propulsion And Braking For Vehicles (AREA)

Claims (12)

  1. Vorrichtung zum Zuführen einer Bahn (3) in eine Station, welche sie im Stillstand bearbeitet, wobei diese Vorrichtung eine erste Antriebswalze (10) umfasst, um welche eine zweite Schwenkwalze (20) stromaufwärts dann stromabwärts schwingt, welch letztere auf zwei Seitenhebeln (52-53, 55) angebracht ist, die auf der Achse (12) dieser Antriebswalze drehen, wobei das Antriebsritzel (29) der Schwenkwalze (20) mit einem Zahnrad (14) von gleichem Durchmesser in Eingriff ist, welch letzteres mit der Achse (12) der Antriebswalze fest verbunden ist, dadurch gekennzeichnet, dass die Vorrichtung ausserdem ein Gegengewicht (80) umfasst, das vom Zahnrad (14) der Achse (12) drehend angetrieben wird, wobei dieses Gegengewicht auf einem Arm (70) angebracht ist, welcher um die Achse (12) dreht und durch einen Mechanismus (54, 60, 61, 62, 65) mit den Hebeln (52, 53) verbunden ist, um in entgegengesetzter Richtung der Schwenkwalze (20) zu drehen.
  2. Vorrichtung gemäss Patentanspruch 1, dadurch gekennzeichnet, dass das Gegengewicht (80) von einem Ritzel (76) angetrieben wird, welches den gleichen Durchmesser aufweist wie das Zahnrad (14) der Achse (12) der Antriebswalze (10), mit welchem Zahnrad (14) dieses Ritzel (76) ebenfalls in Eingriff ist, wobei das Gegengewicht (80) Trägheitsmomente in bezug auf seine zentrale Drehachse und in bezug auf die Achse des Armes (70) aufweist, welche mit denjenigen der Schwenkwalze (20) identisch sind, und eine Masse die so ausgewählt ist, dass sie die horizontalen Kräfte am besten ausgleicht.
  3. Vorrichtung gemäss Patentansprüchen 1 und 2, dadurch gekennzeichnet, dass einer der Hebel (52-53), welche die Schwenkwalze halten, ein Zahnsegment (54) in der Form eines Kreisauschnittes enthält, das auf der Achse (12) der Antriebswalze (10) zentriert und mit einem ersten Zahnrad (61) in Eingriff ist, welch letzteres mit einer zu dieser Achse (12) der Antriebswalze (10) parallelen Umlenkachse (60) fest verbunden ist, wobei ein zweites Zahnrad (62) mit der Umlenkachse (60) fest verbunden und mit einem Umlenkrad (65) in Eingriff ist, das seinerseits mit einem Zahnkreisausschnitt (67) des drehenden und das Gegengewicht (80) tragenden Armes (70) in Eingriff ist.
  4. Vorrichtung gemäss einem der vorerwähnten Patentansprüche 1 bis 3, in welcher die Schwenkwalze (20) oberhalb der Antriebswalze (10) angeordnet ist und in einer sozusagen horizontalen Ebene schwingt, dadurch gekennzeichnet, dass das Gegengewicht (80) in der gleichen horizontalen Ebene schwingt wie die Schwenkwalze (20).
  5. Vorrichtung gemäss Patentanspruch 4, dadurch gekennzeichnet, dass eine Pressrolle (30) oder eine Mehrzahl von Pressrollen (31) von der Achse (27) der Schwenkwalze an über elastische Mittel (32, 34) eingerichtet sind, um die Materialbahn (3) mit einem vorbestimmten Druck gegen die Schenkwalze (20) zu drücken, und dies in der Nähe der Startlinie der Bahn ausserhalb dieser Schwenkwalze.
  6. Vorrichtung gemäss Patentanspruch 4, dadurch gekennzeichnet, dass sie ausserdem ein teleskopisches Tablett umfasst, welches die Bahn (3) zwischen dem Ausgang der schwingenden Schwenkwalze (20) und dem Eingang der Station (1), welche die Bahn im Stillstand bearbeitet, führt, wobei dieses Tablett ein Paar praktisch feststehende, horizontale, stromabwärtige Kämme (44), die einer über dem anderen angeordnet und drehend (25) am Eingang der Bearbeitungsstation (1) befestigt sind, und ein Paar schwingende, obere und untere, horizontale, stromaufwärtige Kämme (45) umfasst, die am Ausgang der Schwenkwalze (20) angeordnet und um die Achse (27) dieser Schwenkwalze drehend befestigt sind ; die oberen und unteren stromabwärtigen Kämme werden jeweils gleitend (23, 24) in der Verlängerung der entsprechenden schwingenden stromaufwärtigen Kämme (45) gehalten, und dies mit ihren seitlich versetzten Zähnen.
  7. Vorrichtung gemäss Patentanspruch 6, dadurch gekennzeichnet, dass die stromabwärtigen Kämme (44) jeweils von einer oberen Querstange und einer unteren Querstange (42) gehalten werden, welch letztere mit einem Paar seitlichen Schienen (24) fest verbunden sind, deren stromabwärtigen Enden drehend (25) in der Nähe der Bearbeitungsstation angebracht sind, und deren stromaufwärtige Enden mit Aussenrollen (23) in Eingriff sind, die auf zwei Seitenplatten (21) angebracht sind, welche auf der Achse (27) der Schwenkwalze (20) drehen, während die stromaufwärtigen Kämme (45) von einem vertikalen Paar Querstangen (22), welche mit den Seitenplatten (21) fest verbunden sind, gehalten werden.
  8. Vorrichtung gemäss Patentanspruch 7, dadurch gekennzeichnet, dass eine Pressrolle (30) auf zwei horizontalen Seitenhebeln (32) angebracht ist, welche jeweils beweglich an jeder schwingenden Seitenplatte (21) befestigt sind, wobei ein oder ein Paar vertikaler seitlicher Zylinder (34), welche ebenfalls an den Platten befestigt sind, eine vorbestimmte Druckkraft auf die Hebel (32) ausüben.
  9. Vorrichtung gemäss Patentanspruch 6, dadurch gekennzeichnet, dass die Kämme in zwei Halbkasten eingeschlossen sind : der eine (78) praktisch feststehend und am Eingang der Bearbeitungsstation (1) befestigt, und der andere (79) schwingend und mit der Achse (27) der Schwenkwalze (20), welche er einschliesst, drehend verbunden, wobei die Zähne (48, 49) der unteren Kämme einzeln von vertikalen Platten (88, 89), welche rechtwinklig aus den Boden (82, 83) der Kasten austreten, getragen werden, und die Zähne (46, 47) der oberen Kämme von vertikalen Platten (87) oder Röhren (86), welche von den Decken (84, 85) herunterkommen, gestützt werden, und die Verflechtung dieser Platten oder Röhren Längskammern (98, 99) für den Luftstrom bilden, der am Boden von jedem jeweiligen Kasten in Querkammern (91, 96) mündet, welche Seitenfenster (92, 94, 95) enthalten.
  10. Vorrichtung gemäss Patentanspruch 4, dadurch gekennzeichnet, dass ein vertikales Paar Zugrollen (40, 41) in der Nähe des Eingangs der nächsten Station angebracht ist.
  11. Vorrichtung gemäss Patentanspruch 10, dadurch gekennzeichnet, dass die Antriebsvorrichtung von einer der Zugrollen (40) einen Riemen (59) umfasst, der um eine mit der Zugrolle (40) fest verbundene Riemenscheibe (37) sowie über zwei Scheiben (35, 36) verläuft, welche jeweils auf jedem der zwei Arme eines vertikalen Hebels (33) angeordnet sind, welch letzterer frei drehend auf der Achse (12) der Antriebswalze (10) angebracht ist, wobei die obere Scheibe (35) mit der Achse (27) der Schwenkwalze (20) fest verbunden ist, welche Achse den oberen Arm des Hebels (33) durchquert und diesem die Schwingung der Schwenkwalze (20) überträgt, und die untere Scheibe, von gleichem Durchmesser wie die obere Scheibe, vom unteren Arm des Hebels so gehalten wird, dass ihre Stellung zu derjenigen der oberen Scheibe in bezug auf eine Linie, welche die Achse der Zugrolle und die Drehachse des Hebels verbindet, wenn sich letzterer in mittlerer Schwingstellung befindet, symmetrisch ist.
  12. Vorrichtung gemäss Patentanspruch 10, dadurch gekennzeichnet, dass die Antriebsvorrichtung von einer der Zugrollen (40) auf der Höhe der Riemenscheibe (37) der Zugrolle (40) mit einer hinteren Umkehrscheibe (38) und einer Umlenkscheibe (39) ergänzt ist, wobei die Symmetrie zwischen den Scheiben (35, 36) und zwischen der Zugrollenriemenscheibe (37) und der Umlenkscheibe (39) in bezug auf eine Linie, welche die Achse der hinteren Umkehrscheibe (38) und die Drehachse (12) des Hebels (33) verbindet, realisiert ist.
EP96106944A 1995-05-08 1996-05-03 Vorrichtung zum Zuführen einer kontinuierlich ankommenden Bahn in einer Station, die sie in angehaltenem Zustand bearbeitet Expired - Lifetime EP0742170B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
CH1305/95 1995-05-08
CH01305/95A CH690547A5 (fr) 1995-05-08 1995-05-08 Dispositif d'alimentation d'une bande dans une station la travaillant à l'arrêt, cette bande arrivant de manière continue.

Publications (3)

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EP0742170A2 EP0742170A2 (de) 1996-11-13
EP0742170A3 EP0742170A3 (de) 1997-10-22
EP0742170B1 true EP0742170B1 (de) 1999-02-10

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US (1) US5685472A (de)
EP (1) EP0742170B1 (de)
JP (1) JP2634041B2 (de)
KR (1) KR100199354B1 (de)
CN (1) CN1071279C (de)
AT (1) ATE176655T1 (de)
BR (1) BR9602194A (de)
CA (1) CA2175981C (de)
CH (1) CH690547A5 (de)
DE (1) DE69601511T2 (de)
DK (1) DK0742170T3 (de)
ES (1) ES2128806T3 (de)

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US6997712B2 (en) * 2003-10-06 2006-02-14 Yong Woon Kim Tooth containing image thereon
KR101242777B1 (ko) 2008-12-04 2013-03-12 봅스트 맥스 에스에이 패키징 제조 기계의 이송 스테이션을 위해 연속적인 스트립 기재를 전환 유닛에 이송하기 위한 장치
TWI494261B (zh) * 2010-07-14 2015-08-01 Bobst Sa 用於轉換網狀基材，進料站及包裝生產機之保護轉換單元的方法
CN102280208A (zh) * 2011-07-08 2011-12-14 江苏亨通高压电缆有限公司 一种多面皮带牵引装置
US20160121572A1 (en) 2013-05-29 2016-05-05 Bobst Mex Sa Unit for converting a continuous web substrate, and packaging production machine thus equipped
CN107934628A (zh) * 2017-12-14 2018-04-20 杭州春来科技有限公司 滤纸阻滞扭矩保持装置
CN108906919B (zh) * 2018-07-17 2024-03-22 宣化钢铁集团有限责任公司 一种带有滑板导向垂直压下的连续矫直机
CN112654571B (zh) * 2018-09-10 2022-03-08 鲍勃斯脱梅克斯股份有限公司 用于展开带材的装置及印压元件成片材形式的机器
CN113878629B (zh) * 2021-09-24 2023-03-10 温州市众邦拉链有限公司 一种拉链带裁切设备
CN118003270B (zh) * 2024-04-10 2024-06-04 珠海博杰电子股份有限公司 一种固带机构

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US3667354A (en) * 1969-01-30 1972-06-06 Rotographic Machinery Co Web fed rotary variable repeat cutter-creaser system
DE2149483A1 (de) * 1971-10-04 1973-04-19 Hans Stang Einlaufvorrichtung fuer mehrere, nebeneinander angeordnete textile baender
FR2214295A5 (de) * 1973-01-11 1974-08-09 Etudes De Machines Speciales
CH602462A5 (de) * 1975-11-26 1978-07-31 Bobst Fils Sa J
FR2618770B1 (fr) * 1987-07-30 1990-01-05 Chambon Machines Dispositif d'alimentation pour une machine travaillant sur une nappe de materiau a l'arret, notamment pour une presse a decouper a plat
CH679134A5 (de) * 1989-05-03 1991-12-31 Bruderer Ag
US5197645A (en) * 1989-09-07 1993-03-30 Nordlof Richard D Roll type stock feed apparatus with pneumatically actuated roll release

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CN1071279C (zh) 2001-09-19
CA2175981A1 (en) 1996-11-09
ES2128806T3 (es) 1999-05-16
US5685472A (en) 1997-11-11
DK0742170T3 (da) 1999-09-20
JPH08310700A (ja) 1996-11-26
EP0742170A3 (de) 1997-10-22
CN1136005A (zh) 1996-11-20
EP0742170A2 (de) 1996-11-13
KR100199354B1 (ko) 1999-06-15
DE69601511T2 (de) 1999-07-08
ATE176655T1 (de) 1999-02-15
JP2634041B2 (ja) 1997-07-23
DE69601511D1 (de) 1999-03-25
KR960041021A (ko) 1996-12-17
BR9602194A (pt) 1998-04-07
CH690547A5 (fr) 2000-10-13
CA2175981C (en) 2000-05-16

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