EP1226886B1 - Einrichtung zum Fördern und Führen eines Metallbandes - Google Patents

Einrichtung zum Fördern und Führen eines Metallbandes Download PDF

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Publication number
EP1226886B1
EP1226886B1 EP20020290203 EP02290203A EP1226886B1 EP 1226886 B1 EP1226886 B1 EP 1226886B1 EP 20020290203 EP20020290203 EP 20020290203 EP 02290203 A EP02290203 A EP 02290203A EP 1226886 B1 EP1226886 B1 EP 1226886B1
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EP
European Patent Office
Prior art keywords
clamping
jack
band
pressure
piston
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Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
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EP20020290203
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English (en)
French (fr)
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EP1226886A1 (de
Inventor
Jean Perret
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Clecim SAS
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VAI Clecim SA
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Publication of EP1226886A1 publication Critical patent/EP1226886A1/de
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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/34—Feeding or guiding devices not specially adapted to a particular type of apparatus
    • B21C47/3408—Feeding or guiding devices not specially adapted to a particular type of apparatus for monitoring the lateral position of the material
    • B21C47/3425—Feeding or guiding devices not specially adapted to a particular type of apparatus for monitoring the lateral position of the material without lateral edge contact
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21C—MANUFACTURE OF METAL SHEETS, WIRE, RODS, TUBES OR PROFILES, OTHERWISE THAN BY ROLLING; AUXILIARY OPERATIONS USED IN CONNECTION WITH METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL
    • B21C47/00—Winding-up, coiling or winding-off metal wire, metal band or other flexible metal material characterised by features relevant to metal processing only
    • B21C47/34—Feeding or guiding devices not specially adapted to a particular type of apparatus
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B39/00—Arrangements for moving, supporting, or positioning work, or controlling its movement, combined with or arranged in, or specially adapted for use in connection with, metal-rolling mills
    • B21B39/006—Pinch roll sets

Definitions

  • the invention relates to a device for driving and guiding a strip moving along a longitudinal axis, and is particularly applicable to controlling the movement of a metal strip in a rolling installation.
  • This winding must take place under a certain tension which is, however, less than the traction required, usually for rolling.
  • the strip may tend, at the exit of the rolling, to shift laterally and it is necessary to refocus before winding coil.
  • a drive and guide device which comprises, normally two cylindrical rollers mounted on either side of the scroll plane of the strip and between which is applied a clamping pressure of the strip, at least one of the rollers being rotated about its axis to control the tensile movement of the strip thus clamped between the two rollers.
  • the upper roller can be raised so as to deviate from the lower roller to facilitate engagement of the belt on the winder or allow its passage, for example to another downstream winder.
  • the position of the upper roll is determined by adjustable stops depending on the thickness of the band, but to ensure a good band drive, it is necessary to accurately set the clamping pressure applied between the two rollers. It is useful, on the other hand, to be able to modulate the pressures applied, respectively, on each side of the strip, these may be slightly different to exert, if necessary, a re-centering effect of the strip.
  • Document FR-A-2459692 describes a device for this type, in which the upper roller is applied, in the clamping position on fixed stops and the clamping pressure is applied to the bearings of the lower roller by cylinders of a special type allowing a presetting of the applied pressures, respectively, of the right side and left side of the band.
  • the upper roller is carried by a frame which can pivot about a horizontal axis under the action of a pneumatic cylinder, between a raised position allowing the free passage of the band and a lowered clamping position of the band, whose level is adjusted by fixed stops.
  • the upper roller is carried by two sliding-mounted bearings, transversely to the running plane, in guides of the frame, each associated with a pneumatic cylinder with a double effect of adjusting the pressure force applied to the strip on each side of the latter. this.
  • Such devices thus make it possible to adjust the pressures applied on the strip in order to exert the traction force required for rolling and, if necessary, to refocus it before winding.
  • the band has, during the scroll, extra thicknesses due to a folding of the band on itself, especially for small thicknesses.
  • the top roll When the top roll is simply applied by its own weight, it can lift slightly to allow such an allowance to be made without changing the clamping pressure.
  • the clamping pressure is applied by cylinders, they are subject, in case of overthickness, to shocks that may disturb the pressure setting.
  • pneumatic cylinders are used to apply the clamping pressure, which can absorb any thicknesses.
  • the response time of a pneumatic cylinder is not negligible and it is therefore difficult, in this case, to provide a real regulation to refocus the band by modulating the pressures applied to the two levels.
  • the object of the invention is to solve these problems by means of a driving and guiding device which makes it possible to absorb defects of extra thickness that may occur during the running of the strip, without substantially changing the forces applied respectively on the bearings of the clamping roller, on either side of the strip, these forces can thus be modulated so as to correct permanently centering the band to ensure a good winding of the coil.
  • the device according to the invention while providing a reliable result, is relatively simple and inexpensive and can be adapted to existing devices without significant modification thereof.
  • the invention therefore generally relates to a device for driving and guiding a strip product
  • a device for driving and guiding a strip product comprising, inside a frame, two cylindrical rollers rotatably mounted each around an axis perpendicular to the direction of travel, at least one of said rollers rotating on two movable bearings guided transversely to the running plane of the band, means for clamping the band between the two rollers by applying an adjustable clamping pressure on each of the movable bearings and means for controlling the rotation of at least one of said rollers, the clamping means comprising, for each mobile bearing, a hydraulic clamping jack resting on the frame and on the bearing and comprising a chamber of pressure supplied with hydraulic fluid under a clamping pressure.
  • each clamping cylinder is associated with a means for damping the variations in thickness of the strip intended to absorb a limited displacement of the piston in the direction opposite to the clamping direction, without any appreciable variation in the pressure of the clamping applied on each bearing by the corresponding cylinder.
  • this damping means comprises at least one closed chamber containing at least one damping fluid and communicating with the pressure chamber of the clamping jack, so that the damping fluid is subjected to the clamping pressure applied on the piston of said cylinder, said damping chamber having a sufficient volume in view of the compressibility of fluid that it contains to absorb a limited displacement of the piston of the clamping cylinder, without any appreciable variation of the hydraulic clamping pressure applied by the latter; this.
  • the damping chamber comprises a single portion forming a capacity communicating with the pressure chamber of the clamping cylinder by a wide open conduit and filled with the same hydraulic fluid, said capacity having a sufficient volume taking into account the compressibility of said hydraulic fluid to absorb a limited displacement of the clamping cylinder piston.
  • the damping chamber comprises two parts, respectively a first connecting portion forming a closed capacitance placed in communication with the pressure chamber of the jack by a first conduit widely open and filled with the same fluid. hydraulic and at the same clamping pressure, and a second portion which is communicated with the first portion by a second conduit widely open and filled with a gas under pressure so as to form a gas accumulator capable of absorbing the passage in the capacity of a quantity of fluid corresponding to a limited displacement of the piston without appreciable variation of the pressure of said hydraulic fluid.
  • the connecting duct between the pressure chamber and the damping chamber has a passage section sufficient to prevent any significant dynamic variation of the fluid pressure during a limited displacement of the clamping cylinder piston.
  • a shutter without inertia such as a deformable membrane is placed in the second connecting duct between the capacitor and the accumulator to ensure the separation between the hydraulic fluid and the gas.
  • each clamping cylinder is mounted to slide axially in a hollow body integral with the frame and limiting with said clamping cylinder body, a chamber filled with a gas, so as to constitute a pneumatic cylinder damping element capable of absorbing a displacement of the body of the clamping cylinder determined by a limited displacement of the piston of said clamping cylinder.
  • the pressure chamber each clamping cylinder is fed by a hydraulic circuit comprising a means of limiting the preset clamping pressure to a value corresponding to the clamping force between the rollers necessary for the running of the strip, the fluid contained in the chamber of damping being maintained at a pressure at least equal to the pressure limit applied to the piston of the clamping cylinder.
  • a means for measuring the lateral position of the strip is provided upstream of the guide device, and the information on the position of the strip supplied by this means is used to control the tilting of the second roller of the guide device so that to correct, by a slight lateral displacement of the band, a "saber" defect, before the winding of the band on the winder located downstream of the guiding device.
  • the driving torque transmitted to the belt by the rollers is modulated by the power supplied by the motors of these rollers, in order to optimally adjust the traction between the last rolling stand and the device, in particular to facilitate measuring the flatness of the band.
  • the device of the invention makes it possible to dampen the shock of the band at engagement and also allows - without inertia - to pass the extra thicknesses resulting in particular from a fold or a weld.
  • FIGS. 1 and 2 schematically show a device 1 for driving and guiding a metal strip 2 which has just been rolled and which will be wound into a reel.
  • Such a device 1 is therefore located downstream of a last rolling stand (not shown) and upstream of a winder (not shown) which provides the winding.
  • the band 2 is supported and driven by a roller table conveyor T (Fig.1) defining a substantially horizontal scroll plane; the centering along the axis of this conveyor is provided by guides not shown.
  • the device 1 comprises a fixed frame 3 comprising, on each side of the strip, a vertical lateral support.
  • the band 2 passes between two nip rollers 4 and 5 whose axes of rotation are parallel to the plane of travel and located in a transverse plane, said axes being perpendicular to the direction of advance of the band.
  • the lower roller 4 is supported by a shaft 41 rotatably mounted at each end in a fixed bearing 42 locked in one of the lateral supports of the frame 3.
  • the upper roller 5 is supported by a shaft 51 rotatably mounted at each of its ends respectively in a rolling bearing 52 mounted in a housing, which is slidable by being guided by a slideway 53 formed on a support frame 6.
  • rollers 4, 5 are rotated by motor means not shown, by means of cardan extensions.
  • the frame 6 is articulated on the frame 3 about a horizontal axis 9, disposed upstream and above the roller 5.
  • At least one hydraulic cylinder 7 is provided to raise the frame 6 by rotating it in the opposite direction clockwise according to Fig.1, around the axis 9.
  • the cylinder 7 is hinged, in the lower part, on an axis carried by the frame 3 while in the upper part of the cylinder rod 7 is hinged on an axle carried by the frame 6 opposite the axis 9.
  • the frame 6 is sufficiently separated from the roller 4 to facilitate the start of winding or to freely pass the band 2 to another winding equipment located downstream and not shown in the drawing.
  • the frame 6 In the lowered position, the frame 6 is applied by the jack 7 to adjustable stops 8 of the frame 3, the level of which can be adapted to the thickness of the strip S so that it is clamped between the two rollers 4, 5 .
  • these clamping means P are provided to exert a tightening force of the strip 2. As shown in Figures 1 and 2, these clamping means P comprise, on each side of the strip 2, a hydraulic jack 10 whose body 12 is fixed on the frame 6 and whose piston 11 makes it possible to apply an individually adjustable clamping pressure on the associated bearing 52, via a rod 13.
  • the clamping force is exerted solely by the jacks 10 which are preferably single-acting, the weight of the roller 5 being received by balancing jacks 20 which rest on the chassis liftable 6.
  • the rotation shaft of the roll 5 is extended by two journals 51 each slipped into a rolling bearing 54 having a housing which is fixed to the end of the rod of a jack 20 whose body is provided with support parts engaging in a clevis integral with the lift frame 6.
  • jacks 20 allow the weight of the roll 5 to be absorbed and to exert on it an upward pulling force.
  • the cylinders 10 can thus be single-acting, the rod 13 of each cylinder 10 being a simple pusher which bears, in the tightening direction, on the housing of the corresponding bearing 52.
  • Each cylinder 10 comprises a piston 11 slidably mounted in the bore of a cylinder 12 forming the cylinder body and fixed on the rod 13 which bears downward on the housing of the bearing 52 of the roller 5.
  • the axis of the jack 10 is substantially vertical.
  • the cylinder body 12 is closed at its upper end by a cover 12a removably fixed, for example by means of screws.
  • a pressure chamber 12b is thus formed in the cylinder body 12 between the piston 11 and the lid 12a.
  • the jack 10 is a hydraulic cylinder fed by a pipe 10a connected to an orifice provided in the lid 12a and which opens into the volume located above the piston 11.
  • a servo valve which allows, for example connecting the pipe 10a to either a source of pressurized liquid (not shown) or to the tarpaulin (not shown), or to close the pipe 10a.
  • the second chamber of the jack, on the other side of the piston 11, is connected by a channel 10b to a pipe 10c back to the tank.
  • the cylinders 20 for balancing the weight of the roll 5 are continuously fed with a slight overpressure so as to apply the bearings 54 on the ends of the pushers 13 of the cylinders 10 thus exerting a return force upwards.
  • the servo-valves 30 for supplying the jacks 10 make it possible to exactly control the clamping pressures applied respectively on the sides of the strip, by means of a control system shown schematically in FIG. 4.
  • a sensor 21 for measuring the lateral position of the strip is provided, above the strip 2, just upstream of the device 1.
  • This sensor 21 comprises, for example, a CCD camera (digital camera with charge transfer system ), but other means of measurement can be used.
  • the output signal of the camera 21 is sent to the input of a gap shaping circuit 22.
  • the output of the circuit 22 is connected to an input of a comparator 23 of which another input receives, by a line 24, a set value for the control of the tilting of the cylinder 5.
  • the output of the comparator 23 is sent to an input d a microcomputer 25.
  • Other inputs of this microcomputer 25 are respectively connected to a line 26 supplying a pressure limit value, a line 27 providing a setpoint value of the position of the rod 13, a line 28 receiving the information of the sensor 15 on the position measurement and a line 29 receiving the information of the pressure sensor 16.
  • the response time is extremely low and one can thus achieve a pressure regulation to correct any decentering of the band.
  • a damping means A which makes it possible to absorb a limited displacement of the piston 11, in the direction opposite to the clamping, without any appreciable variation of the clamping pressure applied to the bearing 52 and consists of a chamber B subjected to the clamping pressure and containing a fluid having a degree of compressibility which allows it to dampen the upward movements of the piston.
  • the damping chamber B comprises two parts, respectively a connecting portion consisting of a capacitor 14 which communicates with the pressure chamber 12b of the jack and a damping portion constituted of a gas accumulator 17.
  • the capacity 14 consists of a recess in the cover 12, above the pressure chamber 12b, and contains the same hydraulic fluid. As can be seen in FIG. 2, the capacitor 14 has a cylindrical shape, of diameter greater than that of the bore of the jack body 12 and communicates with the pressure chamber 12b via a conduit 14a of sufficient section to avoid any dynamic variation. sensitive pressure of the fluid in the capacity 14 during the displacement of the piston 11.
  • a position sensor 15 may be disposed inside the capacitor 14, along the axis of the jack 10, and is thus protected against external shocks.
  • the position sensor 15 comprises a first part connected to the upper end of the rod 13 and a second part linked to the cover 12a and can move axially relative to the first part.
  • a pressure sensor is connected to an orifice 16 formed on the lid to enable the force exerted on the bearing 52 to be determined by the jack 10.
  • the second part of the damping chamber B comprises a volume filled with gas, advantageously constituted by a gas accumulator 17 whose outer shape is substantially cylindrical and centered, preferably, on an axis orthogonal to that of the cylinder 10.
  • accumulator 17 is attached laterally to the cover 12a which has a transverse passage duct 18 which opens into the capacitor 14 to put the latter in communication with the accumulator 17.
  • the diameter of the passage duct 18 is large enough to prevent variation dynamic pressure during the passage of the liquid in the capacity 14.
  • the separation between the liquid of the capacity 14 and the gas of the accumulator 17 is provided by a shutter without inertia, for example formed by a partition 19 applied on the bottom a countersink formed around the perimeter of the duct 18.
  • the inflation pressure of the accumulator 17 is set to a value a little higher than a set point of the pressure provided in the capacity 14 to exert the necessary force on the strip 2 during its introduction and during its travel.
  • This overpressure which can vary according to the products, is therefore collected, during normal operation, by the closing partition 19 of the duct 18.
  • the operation of the device is as follows.
  • the device Waiting for the arrival of the tape head 2, the device is closed by the jacks 7, the chassis 6 coming to rest on the stops 8.
  • the position control of the jacks 10 makes it possible to adjust, as a function of the thickness of the strip, the spacing between the rollers 4 and 5.
  • the rollers 4 and 5 are then rotated with a slight overspeed relative to that of the strip 2.
  • the clamping pressure is regulated by the cylinders 10 controlled in position, by means of a control system which can be of the type shown in FIG.
  • At least one of the rollers is rotated so as to control the running of the strip under the desired traction for rolling.
  • the sensor 21 detects this deviation and controls a tilting of the roll 5 in the direction that corrects the deviation detected.
  • the tilting of the roller 5 is obtained by displacement of one of the lateral bearings 52 relative to the other bearing, so that the geometric axis of the roller 5 tilts slightly about an orthogonal longitudinal axis, the clamping force the band becoming stronger on one side than the other.
  • the strip 2 and subjected to an asymmetric clamping force is pushed laterally, that is to say orthogonally to its longitudinal direction of advance, the side of the lowest effort by a so-called effect of "cherry core” .
  • the strip 2 is thus maintained in the axis of the winder and its defects, in particular that of "saber” (transverse deflection), are compensated for so as to allow a winding without telescoping turns.
  • the torque of the drive motors of the rollers 4 and 5 can be modulated so as to adjust an optimum level of traction between the last stand and the rollers 4 and 5, especially not to to mask, by excessive traction, flatness defects and to allow their measurement which takes place in the immediate exit zone of the last rolling stand.
  • the device 1 of the invention makes it possible to absorb strong defects of extra thickness that can occur in case of folding of the strip 2.
  • the damping effect can occur without delay, thanks to the dimensions of the duct 18, the gas contained in the accumulator 17 and the shutter without inertia 19.
  • the gas pressure in the accumulator 17 returns to its initial value, which is slightly greater than the limited pressure in the capacitor 14, and the cylinder 10 then returns to its normal operating conditions in regulation.
  • damping chamber B is in one part filled with oil giving the capacity 14 a sufficient volume to absorb a limited displacement of the piston 11, without excessive variation of the pressure of the hydraulic fluid given the compressibility of it.
  • the gas accumulator G could then be deleted.
  • gas accumulator could also be realized in another way.
  • FIG. 5 shows an alternative embodiment in which the elements that are identical or playing roles similar to elements already described above are designated by the same references or by the sum of the number 100 and the preceding references, without their description being described. either recovery.
  • each damping means A comprises a pneumatic cylinder 31 having a cylindrical body 32 fixed on the frame 6 centered on the axis of the hydraulic cylinder 110 for adjusting the clamping pressure.
  • the bottom 112a of the clamping cylinder 110 is widened so as to constitute a piston slidably mounted in the body 32 of the pneumatic cylinder 31, whose rod is formed by the body 112 of the clamping cylinder 110.
  • the body 112 can be guided by a vertical axial extension 112d, of smaller diameter, which passes through a bore of the upper bottom of the body 32.
  • the piston 111 bears against a lower stop 32a of the body 32, and the clamping force of the band 2 is provided by the hydraulic cylinders 110 and the oil pressure in these cylinders.
  • the entire cylinder 110 tends to lift and the piston 111 deviates from the stop 32a by compressing the gas contained in the chamber 117 of the pneumatic cylinder 31 which dampens the passage of the overthickness without significant modification of the clamping pressure applied by the cylinder 110 on the bearing 52 on the roller 5.
  • the body 112 of the jack 110 is mounted with a lateral play in a housing 61 of the frame 6 and bears on it by a hinge 18, so as to follow the slight offset of the bearings 152 due to the rotation of the connecting rods 153.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Registering, Tensioning, Guiding Webs, And Rollers Therefor (AREA)
  • Winding Of Webs (AREA)

Claims (18)

  1. Vorrichtung für den Antrieb und die Führung eines Bandproduktes (2), das in eine Längsrichtung abläuft, umfassend ein Stützgestell (3), zwei zylindrische Walzen (4, 5), die beiderseits einer mittleren Bandablaufebene (2) angeordnet und jeweils um eine im Wesentlichen zur Mittelebene parallele und zur Ablaufrichtung senkrechte Achse drehbar befestigt sind, eine erste Walze (4), die auf zwei festen Lagern (42) läuft, bzw. eine zweite Walze (5), die auf zwei beweglichen Lagern (52, 152) läuft, die quer zur Bandablaufebene geführt werden, Mittel (P) zum Einklemmen des Bandes (2) zwischen den beiden Walzen (4, 5) durch Anlegen eines einstellbaren Klemmdrucks auf jedes der beweglichen Lager (52, 152) der zweiten Walze (5) und Mittel zur Steuerung der Drehung mindestens einer der Walzen (4, 5), wobei die Klemmmittel (P) für jedes bewegliche Lager (52, 152) einen hydraulischen Druckzylinder (10, 110) mit einem Körper (12, 112), der auf dem Gestell (3) aufliegt, und einen Kolben (11, 111) umfassen, der gleitend in dem Körper (12, 112) befestigt und mit einer Stange (13, 113) verbunden ist, die auf dem entsprechenden beweglichen Lager (52) der zweiten Walze (5) aufliegt, wobei der Kolben (11, 111) in dem Körper (12, 112) des Zylinders (10, 110) eine Druckkammer (12b, 112b) begrenzt, die mit Hydraulikfluid unter einem Festklemmdruck gespeist wird, dadurch gekennzeichnet, dass jeder Druckzylinder (10, 110) mit einem Mittel (A) zur Dämpfung der Breitenänderungen des Bandes verbunden ist, das dazu vorgesehen ist, eine begrenzte Verschiebung des Kolbens (11, 111) in die zur Klemmrichtung entgegen gesetzte Richtung ohne wesentliche Änderung des auf jedes Lager (52, 152) vom entsprechenden Zylinder (10, 110) angelegten hydraulischen Klemmdrucks aufzunehmen.
  2. Vorrichtung nach Anspruch 1, dadurch gekennzeichnet, dass das Dämpfungsmittel (A) mindestens eine geschlossene Kammer (B) umfasst, die mindestens ein Dämpfungsfluid enthält und mit der Druckkammer (12b) in Verbindung steht, damit das Dämpfungsfluid dem an den Kolben (11, 111) des Zylinders (10, 110) angelegten Klemmdruck unterzogen wird, wobei die Dämpfungskammer (B) im Hinblick auf die Komprimierbarkeit des Fluids, das sie enthält, ein ausreichendes Volumen aufweist, um eine begrenzte Verschiebung des Kolbens (11, 111) des Druckzylinders (10) ohne Wesentliche Änderung des an diesen angelegten hydraulischen Klemmdrucks aufzunehmen.
  3. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die geschlossene Dämpfungskammer (B) einen Behälter (14) bildet, der mit der Druckkammer (12b) des Zylinders (10, 110) durch eine weit offene Leitung (14a) in Verbindung steht und mit demselben Hydraulikfluid gefüllt ist, wobei der Behälter (14) ein ausreichendes Volumen im Hinblick auf die Komprimierbarkeit des Hydraulikfluids aufweist, um eine begrenzte Verschiebung des Kolbens (11, 111) ohne wesentliche Änderung des Drucks des Fluids in der Druckkammer (12b) und dem Behälter (14) aufzunehmen.
  4. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass die Dämpfungskammer (B) zwei Teile umfasst, einen ersten Verbindungsteil, der einen geschlossenen Behälter (14) bildet, der mit der Druckkammer (12b) des Zylinders durch eine erste weit offene Leitung (14a) in Verbindung gebracht wird, die mit demselben Hydraulikfluid gefüllt ist und denselben Klemmdruck aufweist, bzw. einen zweiten Teil (17), der mit dem ersten Teil (14) durch eine zweite weit offene Leitung (14b) in Verbindung gebracht wird, der mit einem Druckgas gefüllt ist, um einen Gasspeicher (G) zu bilden, der den Durchgang einer Fluidmenge in den Behälter (14) entsprechend einer begrenzten Verschiebung des Kolbens (11, 111) ohne wesentliche Änderung des Drucks des Hydraulikfluids aufnehmen kann.
  5. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass ein nicht träges Verschlussmittel, wie beispielsweise eine verformbare Membran (19) zur Trennung zwischen dem Hydraulikfluid und dem Gas in der zweiten Verbindungsleitung (14b) zwischen dem Behälter (14) und dem Speicher (G) angeordnet ist.
  6. Vorrichtung nach einem der Ansprüche 3, 4 oder 5, dadurch gekennzeichnet, dass die Verbindungsleitung (14a, 14b) zwischen der Druckkammer (12b) und der Dämpfungskammer (B, 14) einen ausreichenden Durchgangsquerschnitt aufweist, um jede wesentliche dynamische Veränderung des Drucks des Fluids bei einer begrenzten Verschiebung des Kolbens (11, 111) des Druckzylinders (10, 110) zu verhindern.
  7. Vorrichtung nach Anspruch 4, dadurch gekennzeichnet, dass der Gasspeicher (17) auf einer Seite des Zylinders angeordnet ist und eine zylindrische Gesamtform mit einer zu jener des Zylinders (10) orthogonalen Achse aufweist.
  8. Vorrichtung nach einem der Ansprüche 3 und 4, dadurch gekennzeichnet, dass der in dem Körper (12) des Hydraulikzylinders (10) vorgesehene Behälter (14) ausreichende Abmessungen hat, um in ihm ein Mittel zum Messen der Position des Kolbens, wie beispielsweise einen Positionsfühler (15), anzuordnen.
  9. Vorrichtung nach Anspruch 2, dadurch gekennzeichnet, dass der Körper (112) jedes Druckzylinders (110) axial gleitend in einem Hohlkörper (32), der auf dem Gestell (3) befestigt ist, angeordnet ist, um einen Kolben (112) zu bilden, der im Inneren des Körpers (32) eine Druckkammer (117) begrenzt, die mit einem Gas gefüllt ist, wobei die Gesamtheit einen Druckluftdämpfungszylinder (B) bildet, der eine Verschiebung des Körpers (112) des Druckzylinders (110), die durch eine begrenzte Verschiebung des Kolbens (111) des Druckzylinders (110) bestimmt wird, aufnehmen kann.
  10. Vorrichtung nach einem der Ansprüche 2 bis 9, dadurch gekennzeichnet; dass die Druckkammer (12b) jedes Druckzylinders (10, 110) von einer Hydraulikschaltung gespeist wird, umfassend ein Mittel zur Begrenzung des Klemmdrucks, das auf einen Wert voreingestellt ist, der der Klemmkraft zwischen den Walzen (4, 5), die für das Ablaufen des Bandes (2) erforderlich ist, entspricht.
  11. Vorrichtung nach Anspruch 10, dadurch gekennzeichnet, dass das in der Dämpfungskammer (B) enthaltene Fluid (G) auf einem Druck mindestens gleich der Grenze des an den Kolben (11, 111) des Druckzylinders (10, 110) angelegten Drucks gehalten wird.
  12. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sie ein Mittel (21) zum Messen der Seitenposition des Bandes (2) umfasst, das stromaufwärts in Richtung des Ablaufens der Führungsvorrichtung (1) angeordnet ist, und dass die Information über die Position des Bandes, die von diesem Messmittel (21) geliefert wird, verwendet wird, um das Kippen der zweiten Walze (5) der Führungsvorrichtung zu steuem, um einen Mittenfehler des Bandes zu korrigieren.
  13. Vorrichtung nach Anspruch 12, dadurch gekennzeichnet, dass das Mittel zum Messen der Seitenposition des Bandes (2) eine Digitalkamera (21) umfasst.
  14. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass das Antriebsmoment, das auf das Band (2) von den Walzen (4, 5) übertragen wird, durch die von den Motoren dieser Walzen gelieferte Leistung moduliert wird, um den Zug zwischen dem letzten Walzkäfig und der Antriebsvorrichtung (1) optimal zu regeln.
  15. Vorrichtung nach einem der vorhergehenden Ansprüche, bei der die Achsen der Walzen in einer im Wesentlichen vertikalen Ebene angeordnet sind, dadurch gekennzeichnet, dass sie eine untere Walze (4), die unter dem Band angeordnet und drehbar auf zwei festen Lagern befestigt ist, und eine Walze (5) umfasst, die über dem Band angeordnet und drehbar auf zwei beweglichen Lagern befestigt ist.
  16. Vorrichtung nach Anspruch 15, dadurch gekennzeichnet, dass die bewegliche Walze (5) von zwei Lagern (52) getragen wird, die gleitend zwischen festen Führungsflächen (53) in eine Querrichtung zur Bandablaufebene (2) befestigt sind.
  17. Vorrichtung nach Anspruch 15, dadurch gekennzeichnet, dass die bewegliche Walze (5) von zwei Lagern (152) getragen wird, die an den Enden von zwei Führungsstangen (153) befestigt sind, die um eine feste Achse (62) angelenkt sind, wobei jeder Druckzylinder (110) derart befestigt ist, dass er einem Versatz der Lager (152) auf Grund der Drehung der Stangen (153) beim Anlegen des Klemmdrucks folgt.
  18. Vorrichtung nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die bewegliche Walze (5) und die Gesamtheit der Klemmmittel (P) auf einem Rahmen (6) befestigt sind, der um eine feste Achse (9) drehbar auf dem Gestell (3) befestigt ist und in Klemmposition an einen festen Anschlag (8) durch einen Zylinder (7) angelegt wird, der den Rahmen (6) um die Achse (9) bis zu einer von der Bandablaufebene (2) entfernten Position drehen kann.
EP20020290203 2001-01-30 2002-01-29 Einrichtung zum Fördern und Führen eines Metallbandes Expired - Lifetime EP1226886B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR0101249A FR2820061B1 (fr) 2001-01-30 2001-01-30 Dispositif d'entrainement et de guidage d'une bande
FR0101249 2001-01-30

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EP1226886B1 true EP1226886B1 (de) 2006-06-07

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
AT510149B1 (de) 2010-10-08 2012-02-15 Siemens Vai Metals Tech Gmbh Treiber für eine stahlbandhaspelanlage
CN107777466B (zh) * 2017-10-26 2023-08-01 天津市力干科技有限公司 铜带机气动送料系统

Family Cites Families (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE2305785A1 (de) * 1973-02-07 1974-08-08 Krupp Gmbh Treibeinrichtung fuer walzgut
DE2614254A1 (de) * 1976-04-02 1977-10-27 Schloemann Siemag Ag Verfahren zur regelung der bandzug-anpresskraft an treibapparaten fuer walzband, insbesondere vor bandhaspeln in breitbandwalzenstrassen sowie treibapparat zur durchfuehrung des verfahrens
FR2459692A1 (fr) * 1979-06-26 1981-01-16 Secim Dispositif d'entrainement de bande
DE3026524A1 (de) * 1980-07-12 1982-02-11 Schloemann-Siemag AG, 4000 Düsseldorf Stellvorrichtung fuer die andrueckrollen und/oder umlenkschalen von bandhaspeln, insbesondere unterflurhaspeln
DE3507251A1 (de) * 1985-03-01 1986-09-04 SMS Schloemann-Siemag AG, 4000 Düsseldorf Treibapparat fuer walzband

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DE60211967T2 (de) 2007-06-14
FR2820061A1 (fr) 2002-08-02
FR2820061B1 (fr) 2003-05-02
DE60211967D1 (de) 2006-07-20
EP1226886A1 (de) 2002-07-31

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