EP0765196B1 - Richtmaschine mit ineinandergreifenden rollen und anwendungsverfahren einer solchen richtmaschine - Google Patents

Richtmaschine mit ineinandergreifenden rollen und anwendungsverfahren einer solchen richtmaschine Download PDF

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Publication number
EP0765196B1
EP0765196B1 EP96913592A EP96913592A EP0765196B1 EP 0765196 B1 EP0765196 B1 EP 0765196B1 EP 96913592 A EP96913592 A EP 96913592A EP 96913592 A EP96913592 A EP 96913592A EP 0765196 B1 EP0765196 B1 EP 0765196B1
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EP
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Prior art keywords
rolls
girder
levelling
jacks
roll
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EP96913592A
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English (en)
French (fr)
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EP0765196A1 (de
Inventor
Michel Chevet
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Clecim SAS
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VAI Clecim SA
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21D1/00—Straightening, restoring form or removing local distortions of sheet metal or specific articles made therefrom; Stretching sheet metal combined with rolling
    • B21D1/02—Straightening, restoring form or removing local distortions of sheet metal or specific articles made therefrom; Stretching sheet metal combined with rolling by rollers

Definitions

  • the subject of the invention is a leveler with nested rollers. for a strip product according to the preamble of claim 1, more specificaly of metal strips and a method for adjusting the leveling effect performed on a strip using such a leveler according to the preamble of claim 16.
  • multi-roller leveler For leveling flat products and, in in particular, metal strips such as laminated sheets, we often use a machine called multi-roller leveler comprising two series of rollers with parallel axes, respectively forming two leveling crews between which we do scroll the strip to be leveled in one direction longitudinal perpendicular to the rollers. These are offset longitudinally and vertically by so as to overlap by determining a wavy path of the tape which is thus subjected to the effects of traction-bending in alternating directions on both sides and others of an average plan of scrolling substantially horizontal.
  • the whole is placed in a support cage fixed with two uprights apart and is associated with adjustment means making it possible to modify the nesting of the rollers to adjust the efficiency of the leveling according to needs and characteristics of the strip, in particular its dimensions and the nature of the metal.
  • each leveling crew placed, respectively, on each side of the passage plane of the strip is generally supported on a cross member resistant forming a box spring and extending over all the grip of the leveling crew.
  • the cross member constituting the upper box spring is mounted sliding vertically between the uprights of the support cage, its position being adjustable by mechanical or hydraulic actuators mounted at angles of the cage and allowing to adjust the level of the upper box spring and adjustable crew relative to the fixed lower crew. If needed, the actuators can be adjusted differently, from way to determine a forward or backward tilt or a swaying of one of the crews compared to the other, for example to reduce the overlapping of rollers in the direction of travel of the strip.
  • each active roller is applied, through its rollers support, on an individual crosspiece taking support directly on the amounts of the cage.
  • the bending of each cross member can be compensated for by means of an adjustable thickness shim inserted between each cross member and the support rollers, and consisting of two dishes with inclined faces forming corner, whose thickness can be increased, in the central part, by means of an eccentric, so as to maintain the straightness of the corresponding active roller.
  • each roll of leveling is supported by a system with adjustable thickness corners, on a frame of support which supports itself on the angles of the bed base by fixed wedges placed in the axis of the four leveling cylinders for the level of the bed base.
  • Two rows of flat cylinders distributed between said fixed wedges are interposed between the box spring and the chassis of each leveling crew, respectively on the entry and exit side of this one, the distribution of pressures between said flat cylinders being adjusted to compensate for the bending of the bed base under the effect of the applied forces to maintain the straightness of the support frame and, therefore leveling rollers which take support on it.
  • This adjustment can be carried out under load and is therefore possible to maintain the flatness of the chassis and, therefore, the degree of nesting of the rollers, by adapting to variations in applied forces during operation.
  • the inventor had the idea that would be desirable to have the possibility not only to take account of foreseeable deformations of the machine but also to distribute the load the leveling effect to correct the defects of flatness detected on the tape. Now in the machines used so far, it is simply intended to compensate for cedings to maintain parallelism rollers and the degree of nesting that is set to advance.
  • the invention therefore aims to solve all the problems that have just been exposed thanks to simple and robust devices, likely to resist leveling forces extremely important, for example for leveling cold metal sheets and not allowing only to compensate for all cedings, but also to act precisely on the distribution of leveling stresses applied to the strip at level of each of the active rollers, this distribution can be changed even during tape scrolling.
  • a leveler with nested rollers for a strip product moving next a longitudinal direction of travel including, inside a fixed cage, two roller leveling crews separated parallels, placed on either side of the strip with offset rollers defining a wavy path on either side of a mean plane of tape running, each leveling crew comprising a plurality of rotating rollers planing with parallel axes, each associated with at least a row of support rollers distributed over the whole its length, the assembly being mounted in a chassis of support and applied, on the side opposite the strip, on a resistant box spring resting on the fixed cage, characterized by the fact that the support frame at least one of the leveling crews comprises a frame-shaped part inside which are arranged, one next to the other, a plurality of transverse beams in number equal to that of leveling rollers, slidably mounted in said frame, independently of each other, each along a clamping plane passing through the axis of the corresponding leveling roller, each active roller leveling bearing
  • each leveling roller is rotatably mounted at its ends on two bearings centering connected respectively to the ends correspondents of the associated beam, in a way allowing a limited relative displacement of said roller bearings in relation to the beam under the action of said hydraulic cylinders.
  • the leveler includes means for adjusting the position of each of the cylinders interposed between the box spring and each cross beam for individual adjustment level profile of at least some of the rollers leveling assets relative to the mean plane of tape scrolling.
  • the cylinders can also be set simultaneously, either to determine individually the level of each of the rollers active, or to act globally on nesting rollers.
  • the machine includes means for adjusting the pressure of each of the cylinders interposed between the box spring and each cross beam for individual adjustment of the clamping force supported by at least some leveling rollers.
  • each transverse beam has a width at most equal to the distance between the axes of the leveling rollers and the support cylinders of each beam on the bed base each have a elongated section, each cylinder having a piston whose width across the beam does not not significantly exceed the width thereof and whose length is determined to define a useful section of the cylinder chamber compatible with the support effort to exercise taking into account the number of cylinders acting on each beam.
  • each transverse beam takes support on the box spring via three cylinders, respectively a central cylinder and two cylinders lateral, said jacks being associated with a means of adjusting the position of the central cylinder for the nesting adjustment of the corresponding roller and means for correcting the relative positions of the two other cylinders to control the roll profile and its variation under the effect of the applied forces.
  • the support cylinders are provided in at least one piece of intermediate support interposed between the box spring and the set of transverse beams, and in which are housed the cylinders, the latter being arranged in several rows parallel to the beams transverse.
  • the cylinder bodies placed at the same level on the different cross beams are gathered in a single piece spanning all of the beams and in which recesses are provided constituting the chambers of the jacks and in which sliding pistons are supported on the corresponding beam.
  • the support frame includes a rectangular frame surrounding all of the rollers and associated with a plurality of guide partitions separated one of the other so as to limit flat spaces in which are housed the transverse beams, each being provided, at its two ends, with means of support on the frame with possibility of sliding.
  • the entire support frame is closed, on the side opposite the roller, by a plate covering the set of transverse beams so as to form a housing, said plate being provided, at the right of each beam, of a plurality of passage orifices pistons of the cylinders interposed between each beam and the box spring. The whole thus forms a cassette which can be removed from the leveler by translation in a direction parallel to the axes of the rollers.
  • a method of adjusting the leveling effect carried out on a strip using a roller leveler nested according to the invention is defined in claim 16.
  • the position is adjusted of one of the box springs relative to the other for determine a baseline of the set of the leveling crew relative to each other and, each leveling roller being mounted, with its rollers support, on a transverse beam mounted sliding perpendicular to the passage plane of the band and bearing on the corresponding box spring through at least two cylinders hydraulic levels are precisely determined relative of at least one group of leveling rollers relative to the reference level, by setting individual positions of the support cylinders corresponding to each of the rollers, so that define a specific degree of nesting of each of the rollers of said group, the pressures applied to each of said cylinders being limited to a value of safety corresponding to a maximum leveling effort cashed by each of the leveling rollers.
  • each support beam of a leveling roller is associated with at least three support cylinders, respectively a central cylinder and two side cylinders.
  • the leveler includes an odd number n of nested rollers, respectively (1, 3, 5 .... n) on one of the crews and (2, 4, 6 ... n-1) on the other crew, we adjust position the cylinders corresponding to at least two rolls, respectively (p) and (q) of each of the two crews, placed respectively above and in below the strip and the pressure is adjusted cylinders corresponding to the two pairs of rollers, respectively (p-1, p + 1) and (q-1, q + 1) which frame each of said rollers (p, q) adjusted in position so as to determine at least two curvatures in directions reverse on said rollers (p and q), the locations of these in each of the two crews and their relative levels compared to reference level, as well as the pressures applied to the rollers that frame them, being determined based on the characteristics of the strip to be leveled so as to achieve the leveling effect wish.
  • Figure 1 is a general view of an embodiment of a leveler according to the invention, in partial section along a plane transverse to the direction of travel.
  • FIG. 2 is an enlarged view, of the leveler, in longitudinal section, along a plane median parallel to the direction of travel.
  • Figure 3 is a detailed diagram, in perspective, with partial snatch.
  • Figure 4 is an overall circuit diagram actuator control.
  • Figure 5 shows schematically an arrangement especially leveling rollers.
  • FIGs 1 and 2 there is shown the whole of a leveler comprising a fixed cage 1 consisting of two spaced apart uprights 11, 11 'connected by spacers 12 and fixed to their base 13 on a foundation block 14.
  • the lower cross-member 3 ' is fixed and rests directly on the base 13 of the cage 1.
  • the upper crosspiece 3 is adjustable in height and can slide vertically under the action of four hydraulic cylinders or mechanical 15 provided at the upper part of the uprights 11, 11 '.
  • Each of the crosspieces 3, 3 ' is made so particularly rigid and forms a resistant box spring defining a substantially planar bearing face 32, 32 '.
  • two box springs 3, 3 ' are arranged two planing crews, respectively upper 2 and lower 2 ', placed on either side of a plane P of passage of the strip to be leveled A and bearing on the opposite side, on the bearing faces 32, 32 ' respectively of the upper box spring 3 and the box spring lower 3 '.
  • Each leveling crew 2, 2 ′ comprises a plurality of active rollers 21 spaced from each other others and whose axes are perpendicular to the direction x'-x of movement of the product to be leveled.
  • Each active roller 21 is rotatably mounted at its two ends, on two bearings 23 defining an axis of rotation 20 of the roller and rests on rollers or support rollers 22, the assembly being mounted in a support frame which is applied against the box spring 3.
  • the upper crew 2 includes four active rollers 21 each associated with two rows of support rollers 22 centered respectively on two axes symmetrically spaced on either side of a vertical plane of symmetry P1 passing through the axis of the corresponding active roller 21.
  • the lower 2 'unit includes five rollers active 21 'each associated with two rows of rollers support 22 'and whose axes are placed in vertical planes of symmetry P'1 which are offset by one half step with respect to the P1 planes of symmetry upper rollers 21, so that, so known, a metal strip passing along the longitudinal direction x'-x follows a wavy path, from on either side of a mean plane of travel P between the two rows of rollers 21, 21 ', the amplitude of the undulations depending on the degree of nesting of rollers 21, 21 '.
  • the support chassis 4 of each crew of leveling is constituted by a hollow piece 40 in the form frame in which several beams are housed transverse 5 arranged one beside the other at inside the frame 40 and each supporting one of the active rollers 21 and its support rollers 22.
  • the hollow part 40 therefore forms a section frame rectangular surrounding all the beams transverse 5 which can slide individually inside the frame 40, with the rollers and the pebbles.
  • the chassis 4 constitutes a form box rectangular bounded by two long sides 42 parallel to the planes of symmetry P1 and two small sides 43 perpendicular to said planes, and between which extend from the intermediate partitions 41 which limit, inside the frame 40, several elongated housings 45 in which are threaded, respectively, the transverse beams 5.
  • Each beam 5 is centered on a vertical plane of symmetry P1 passing through the axis of the corresponding active roller 21 and is provided at its two ends with projection 53, 53 'in which are housed, respectively, the two bearings 23, 23 'of the roller active 21.
  • each beam 5 is supported, at each of its two ends, by jacks 52, bearing on corresponding bearing parts on each lateral side 43 of the frame 4.
  • each active roller 21 is supported on two rows of support rollers 22a, 22b which are mounted rotating on intermediate supports 54 fixed on the lower part of the beam 5, around axes alternately discarded on either side of the plane vertical symmetry P1 of the beam.
  • each beam 5 has a rectangular cross section whose width is of the same order as the diameter of the roller 21 corresponding to and at most equal to the center distance of rollers and whose height is at least equal to the width and preferably much greater than this one.
  • each beam 5 forms, with the corresponding active roller 21 and its rollers support 22a, 22b, a relatively rigid assembly, suspended from frame 4 by jacks 52, 52 'and which can slide vertically inside its housing 45, along the plane of symmetry P1 which therefore constitutes a clamping plane of the active roller 21.
  • each beam 5 with its active roller and its support rollers can slide individually in its housing without interference with the movement of sliding neighboring beams.
  • each support beam 5 takes support on the bed base 3 independently of the beams neighbors through a row of several cylinders 6 which are interposed between each beam 5 and the application face 32 of the bed base 3 and distributed over the entire length of the beam 5.
  • the jacks 6 are housed in a room 33 in mechanically welded construction, which covers the entire face application 32 of the bed base 3 and in which the cylinders 6 are arranged in several rows corresponding respectively to each of the beams transverse 5, each cylinder 6 comprising a piston 62 and a body 61 housed in the intermediate part 33.
  • each cylinder 6 preferably uses cylinders with a cross-section elongated, the piston 62 of each cylinder 6 having a width slightly less than that of beam 5, but covering, in the longitudinal direction of the beam 5, a much greater length.
  • the piston and the chamber corresponding 64 have an elongated section having, from preferably circular rounded ends of so as to have an oblong shape, as we have shown schematically in Figure 3.
  • each cylinder we can thus considerably increase the useful section of each cylinder and obtain a force sufficient using only a reduced number of cylinders per beam, the length of each cylinder being determined to define a useful section of the cylinder chamber compatible with the bearing force at exercise given the number of cylinders acting on each beam.
  • each beam 5 can be associated with only three cylinders, respectively a central cylinder 6a centered in the plane median of the leveler and two lateral cylinders 6b and 6c.
  • the bodies 61 of all the jacks placed respectively on the same level on each of the beams parallels 5 can be grouped in one room single 61 ', which spans the entire width of the box spring 3 in the same groove-shaped recess 34.
  • this room 61 ' are arranged several bores centered respectively in the median planes P1 of the different beams 5 and each constituting the chamber 64 of a jack whose piston 62 is supported on the upper face 55 of the beam 5 corresponding.
  • circuits oil supply and outlet are arranged in the room 61 '.
  • each cylinder 6 is associated with a sensor. position 63 housed in room 61 '.
  • the support beams 5 of the active rollers 21 may have a height significantly greater than their width, which gives them relatively high rigidity and allows distribution over the entire length of the active roller, the effects of adjustment cylinders, without hindering the sliding of all.
  • Each beam 5 is indeed, perfectly laterally held in the housing 45 corresponding to frame 4 and resists elastically and without risk of buckling to the actions exerted by the cylinders 6, the effects of which on active rollers 21 can therefore be extremely precise.
  • the lower leveling crew 2 'taking support on the lower base 3 ' is made in a way completely analogous, but is normally fixed in height while the general level of the box spring upper 3 with upper leveling crew 2 can be adjusted in height, by means of jacks 15.
  • the frame 4 is closed, at its part upper, by a plate 43 which covers the assembly beams 5 and in which are provided, at right of each beam 5, rows of orifices 44 of passage of pistons 62.
  • the frame 4 forms a housing containing all the beams 5 with the rollers 21 and their support rollers 22 which can advantageously constitute a removable cassette.
  • This is applied and removably attached against the box spring 3 by clamps 35 actuated by jacks 36 bearing on the base 3, the upper plate 43 bearing on the face application 32 of the bed base 3, through the parts 61 'constituting the bodies of the jacks 6.
  • each beam 5 is supported at its two ends on the sides 43 of the frame 4 by means of jacks 52, 52 '. These the latter are adjusted so as to support the weight of the beam 5 with the support rollers 22 and the active roller 21 corresponding and maintain the beam 5 applied against the corresponding cylinders 6, without opposing the sliding of the beam under the effect of said cylinders.
  • Each cassette constituted by frame 4, and the set of beams 5 and rollers 21 and rollers 22 associates, can be removed from the machine by a displacement parallel to the axes of the rollers and beams.
  • the lower cassette 4 ' is provided rollers 45 which can roll on rails 16 of adjustable height (figure 2).
  • the two leveling crews can be removed at the same time, the upper crew 2 resting on the crew lower 2 'by means of stops not represented.
  • the invention provides two means of adjusting the spacing of the crews of leveling and nesting of rollers.
  • the four jacks 15 allow define a reference level for the upper bed base 3 and the upper leveling crew 2 with respect to a lower level of the leveling crew 2 'defined by the lower base 3'.
  • each cylinder 6 is associated with a position sensor 63 and it is possible, first of all, to adjust in the same way and simultaneously all the cylinders corresponding to a support beam 5 to control the level of the corresponding active roller 21, for example, for vary the nesting rate and the amplitude of ripples, from the entry to the exit of the leveler.
  • Each cylinder 6 being associated with a position 63, it is possible, from the information given by the mathematical model, from adjust the respective cylinder positions so that correct the bending of the corresponding roller 21.
  • the position adjustment of the side cylinders 6b, 6c used to determine the level 21 corresponding active roller means and model mathematics determines, according to the efforts applied and all the parameters of installation, foreseeable transfer of the part corresponding to the box spring 3 and, consequently, the position of the central cylinder 6a enabling the straightness of the corresponding roller 21.
  • FIG. 4 there is shown diagrammatically, the command and control circuits of a machine leveling allowing such adjustments.
  • Each leveling roller being associated with three oblong cylinders 6, the machine therefore comprises in total twenty-seven cylinders that are powered by a circuit hydraulic 7 comprising, conventionally, a pump 70, a tank 71 and twenty-seven servo valves 72 each associated with one of the jacks 6.
  • the four support cylinders 15 of the upper box spring 3 are also supplied with oil, each via a servo valve 73.
  • figure 4 represents only two leveling rollers, respectively upper 21 and lower 21 ', each associated with a support beam 5, 5 'resting on the bed base correspondent 3, 3 'through a series of three cylinders 6, 6 ', only the servo valves 72, 72' corresponding to these six cylinders being represented with the corresponding circuits.
  • the hydraulic circuits which have been represented only very schematically, have all the usual organs for a normal operation, including limiters pressure mounted on the circuits corresponding to each row of cylinders. Therefore, the effort of leveling collected by each of the rollers, which corresponds to the sum of the pressures applied to the matching cylinders can be limited to a value of security, which avoids all risks of deterioration of the machine due, for example, to too uneven distribution of efforts between rollers.
  • Position control and of the pressure of each of the twenty-seven cylinders 6, 6 ' is ensured by an automatic regulation system 8 conventionally connected by a network of communication 9, to various control devices and such as a sequential controller 91 of control of successive planer operations, a auxiliary controller 92, and various interface elements 93, 94, allowing, in particular to the operator to determine or modify possibly the machine setting parameters and monitor the operation of it and the regulation system to intervene in the event of need.
  • Each support cylinder 6 of a beam 5 is associated, as we have seen, with a position sensor 63 and to a pressure sensor 65 which emits signals representative of the position of the piston 62 and of the pressure in the chamber 64 of the jack 6. These signals are applied to the corresponding inputs of the regulation system 8. This also receives signals corresponding, respectively, to the position and pressure of each support cylinder 15 of the box spring which are supplied by sensors of position 18 and pressure sensors 18 'associated with each of the cylinders 15.
  • the system regulator 8 After processing this information, the system regulator 8 issues correction orders which are applied to the control solenoids servo valves 72, 72 'and 73.
  • the regulation system 8 comprises a number of control units and regulation and, in particular, an automatic transfer compensation 81 comprising two parts 81a, 81b assigned, respectively, to the upper box springs 3 and below 3 ', a servo controller of position 82, a profile servo controller straight 83 and a control machine of horizontality 84, which are associated with each of the 5, 5 'beams.
  • an automatic transfer compensation 81 comprising two parts 81a, 81b assigned, respectively, to the upper box springs 3 and below 3 ', a servo controller of position 82, a profile servo controller straight 83 and a control machine of horizontality 84, which are associated with each of the 5, 5 'beams.
  • Figure 4 shows only the cylinder control loops of a beam 5 for supporting an upper cylinder 21 but the same circuits are associated with the cylinders corresponding to all the other rollers.
  • the regulatory system has to maintain the central position of each roller to its set value and control horizontality and straightness of the generator active on contact with the strip to be leveled.
  • horizontality you have to hear the basic level defined by the fixed bottom base 3 ', which may not not be strictly horizontal, due to cedings and possible deformations of the different supports.
  • the basic level therefore corresponds, empty, to the travel plane P defined by the rollers 21 'of the lower leveling crew 2 '.
  • the position of bed base 3 adjusted by means of the jacks 15 makes it possible to define a higher crew reference level 2 strictly parallel to the basic level of the lower crew 2 'and in relation to which will be made the nesting adjustments of the rollers the objective being to make a sheet metal perfectly rectangular section maintaining the straightness and parallelism of active generators rolls of the two crews, respectively upper and lower.
  • the sensors 63 of each of the cylinders 6 make it possible to know, at all times, the position of the piston 62 relative to the body 61 of the cylinder but, due to the elastic deformations of the mechanical elements under the action of the different forces, the measured values do not do not directly represent the position of the active generators of the corresponding leveling roller 21 and must therefore be corrected by the yielding compensation machine 81, taking account of the width L of the product in the elasticity matrix 810.
  • the machine compensation 81 multiplies the leveling force measurement vector F, corresponding to the sum of the pressures of the three jacks measured by the sensors 64, by the elasticity matrix 810 of the mechanical assembly to obtain the correction to be made to the desired position X 0 , corresponding to the leveling force at the level of the roller considered, which is determined by the mathematical model of the regulation system 8.
  • the controller 81a thus forms a signal corresponding to the effective position X of the active generator of the roller in question, which is displayed on the regulator 82.
  • the latter determines the difference between the effective position X to be ensured and the position measured by the corresponding sensor 63 and emits a signal for correcting the position setpoint of the central cylinder 6a which is displayed on the corresponding servo-valve 72a so as to obtain the correct position X of the roller 21 at the center of the latter.
  • the horizontality control machine 84 includes a comparator 86 which receives, on its two inputs 84b, 84c the signals emitted by the sensors of position 63b, 63c, corresponding to the positions of the two cylinders 6b, 6c relative to the reference level defined by the upper base 3.
  • the gap between these two signals is sent in addition or in less on orders for servo valves 72b, 72c associated respectively with the two lateral jacks 6b, 6c so as to permanently reduce this difference to zero.
  • Signals representative of pressures in the three cylinders 6a, 6b, 6c measured by the sensors 65 correspondents are displayed at the entry of the rectilinear profile servo controller 83 which includes a regulator 87 of type P.I.D. associated to 88 comparators to ensure the distribution between the pressures of the three cylinders such that in the event that the force of metal reaction is uniform across the width, the active generator of the roller 21 is rectilinear.
  • the relationship between the force at the center and the forces side is a function of the width L of the sheet glided.
  • the difference between the sum of the lateral forces and the corresponding setpoint is formatted by the P.I.D. 87 which emits a correction signal acting simultaneously on the lateral servo valves 72b, 72c and, in the opposite direction on the servo valve central 72a, so as to cancel this difference.
  • control in position and in pressure of the support cylinders of each of the rollers allows to determine an optimal wavy profile by making the bends necessary for good leveling operation.
  • the cylinders corresponding to all rollers can be adjusted in position so as to define, on the rollers successive, decreasing curvatures from entry to the exit of the leveler, the pressures in the cylinders being adjusted so as to limit the effort supported by each of the rollers.
  • rollers having, for example, a position fixed determined by adjustment in position of their cylinders while other rollers can adapt to the undulations defined by the fixed rollers in exerting on the sheet an effort determined by simple pressure adjustment of the corresponding cylinders.
  • Figure 5 shows schematically a nine roller leveler in which only the cylinders corresponding to the rollers R1, R2, R5, R8 and R9 are set in position, the cylinders of the other rollers R3, R4, R6, R7 being simply adjusted in pressure so as to apply to sheet metal a determined effort but without fixing the position of the corresponding roller.
  • each of the rollers R2, R5, R8 of fixed position is framed by two rollers placed the other side of the band and set only in pressure in order to exert on the band, on the part and on the other side of the fixed roller, forces which determine a certain curvature depending on the characteristics tape and applied pressures.
  • Each group of three rollers determines a curvature, one way or the other, on the roller fixed corresponding and this results in a ripple at three alternating curvatures whose profile depends on the web stiffness, fixed roller positions R2, R5, R8 and pressures applied by others rollers.
  • the transition from a curvature to the next depends on the characteristics of the tape and it note that the curvatures are not necessarily centered on the fixed rollers.
  • the mathematical model can, in function of the different parameters and in particular the nature of the metal and the dimensions of the strip, define an optimal wave profile which is not necessarily related to the number of rollers and their the regulatory system determining the positions and pressures to be assigned to the different rolls according to the rank of each of them for get the desired profile.
  • An essential advantage of the invention therefore lies in the fact that the profile of the undulations can be freely modified by simply adjusting the levels and the pressures applied to all the rollers.
  • each beam could be associated with only two cylinders allowing to adjust the level and possible inclination of the roller corresponding asset. Conversely, we could use more cylinders, especially if gives them a circular section.
  • section cylinders elongated, especially oblong has the advantage essential to obtain the largest active surface and therefore the maximum effort for a number minimum of cylinders distributed over the entire surface of the beam facing the box spring.
  • the invention is, moreover, applicable to all types of multi-roller levelers, crews leveling may include a number more or less large of rollers. Besides, these should not necessarily be associated each with a beam of support and adjustment cylinders, some of rollers can be fixed. Such a solution is not covered by the claims.
  • the installation can be adapted to formats and characteristics of the sheets, and able to perform all necessary corrections.

Claims (20)

  1. Richtmaschine mit ineinandergreifenden Rollen für ein gemäß einer Durchlauflängsrichtung (x', x) sich bewegendes Banderzeugnis, bestehend, innen in einem feststehenden Gerüst (1), aus zwei mit im Abstand beiderseits des Bandes parallel angeordneten Richtrollen-Baugruppen (2, 2') mit versetzt gelagerten Rollen, welche eine gewellte Bahn beiderseits einer mittleren Banddurchlaufebene definieren, wobei jede Baugruppe (2) eine Vielzahl drehbeweglicher Richtrollen (21) mit Parallelachsen umfasst, denen jeweils in mindestens einer Reihe über deren gesamten Länge verteilte Stützrollen zugeordnet sind, und wobei die Einheit in einem Stützrahmen (4) untergebracht ist und auf der dem Band entgegengesetzten Seite auf einem auf dem feststehenden Gerüst (1) abgestützten stabilen Balken (3) angreift, dadurch gekennzeichnet, daß der Stützrahmen (4) mindestens einer Richtrollen-Baugruppe (2) ein rahmenförmig ausgebildetes Teil (40) aufweist, in welchem eine Vielzahl, in diesem Rahmen (40) unabhängig von einander gleitend montierte, in der Anzahl derjenigen der Richtrollen (21) entsprechende, nebeneinander angeordnete Quertraversen (5) untergebracht sind, und zwar jeweils gemäß einer durch die Achse der entsprechenden Richtrolle (21) verlaufenden Anstellungsebene (P1); wobei jede aktive Richtrolle (21) über ihre gesamte Länge sich auf dieser Quertraverse über ihre Stützrollen (22) und jede Quertraverse (5) sich einzeln auf dem Balken (3) über mindestens zwei Hydraulikzylinder (6), die zwischen dem Balken (3) und der Quertraverse (5) dazwischengesetzt und über die gesamte Länge der letzteren verteilt sind, abstützt.
  2. Rollenrichtmaschine nach Anspruch 1, dadurch gekennzeichnet, daß jede Richtrolle (21) an deren Enden drehbar in zwei Zentrierlagern (23) montiert ist, die mit den entsprechenden Enden der zugeordneten Quertraverse (5) derart verbunden sind, daß eine begrenzte Relativbewegung dieser Lager (23) der Rolle (21) zur Quertraverse (5) unter der Wirkung dieser Hydraulikzylinder (6) erfolgen kann.
  3. Rollenrichtmaschine nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, daß sie zur Einzeleinstellung des Profils und der Höhe mindestens einiger Richtrollen (4) zur mittleren Banddurchlaufebene Einstellmittel zur Einzelpositionierung der zwischen dem Balken (3) und jeder Quertraverse (5) dazwischengesetzten Hydraulikzylinder (6) umfaßt.
  4. Rollenrichtmaschine nach einem der Ansprüche 1, 2 und 3, dadurch gekennzeichnet, daß sie zur Einzeleinstellung mindestens einiger mit der Anstellkraft beaufschlagter Richtrollen (4) Mittel zum Einstellen des Drucks jedes der jeweils zwischen dem Balken (3) und jeder Quertraverse dazwischengesetzten Hydraulikzylinder (6) aufweist.
  5. Rollenrichtmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß jede Quertraverse (5) eine höchstens dem Abstand zwischen den Achsen der Richtrollen (21) entsprechende Breite aufweist, und daß die Zylinder (6) zum Abstützen einer jeden Quertraverse (5) auf dem Balken (3) einen langgestreckten Querschnitt aufweisen, wobei jeder Zylinder (6) einen Kolben (62) umfaßt, dessen Breite in der Querrichtung zur Traverse (5) im wesentlichen die Breite derselben nicht überschreitet und dessen Länge zur Bestimmung eines mit der auszuübenden Stützkraft zu vereinbarenden nützlichen Querschnittes der Kammer (64) des Zylinders (6), unter Berücksichtigung der Anzahl der mit der Traverse (5) verbundenen Zylinder festgelegt ist.
  6. Rollenrichtmaschine nach Anspruch 5, dadurch gekennzeichnet, daß die Zylinder (6) einen länglichen Querschnitt mit abgerundeten Enden aufweisen.
  7. Rollenrichtmaschine nach einem der Ansprüche 5 und 6, dadurch gekennzeichnet, daß sich jede Quertraverse (5) auf dem Balken (3) über mindestens drei Zylinder (6) mit länglichem Querschnitt, einen mittigen und zwei seitliche über die Länge der Quertraverse verteilte Zylinder, abstützt.
  8. Rollenrichtmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die Stützzylinder (6) in mindestens einem zwischen dem Balken (3) und den Quertraversen (5) dazwischengesetzten Zwischentragteil (33) montiert sind.
  9. Rollenrichtmaschine nach Anspruch 8, dadurch gekennzeichnet, daß sich das Zwischentragteil (33) der Zylinder (6) über die gesamte Fläche der Richtrollen-Baugruppe (2) erstreckt und mehrere Reihen jeweils einer Quertraverse (5) entsprechender Aussparungen (34) aufweist, die jeweils ein Gehäuse (61) des Zylinders (6) begrenzen, in welchem ein sich auf der Quertraverse (5) abstützender Kolben (62) gleitend montiert ist.
  10. Rollenrichtmaschine nach Anspruch 9, dadurch gekennzeichnet, daß die auf den verschiedenen Quertraversen (5) in gleicher Höhe angeordneten Gehäuse (61) der Zylinder (6) zusammen in einem sich über sämtliche Quertraversen (5) erstreckenden Teil (61') untergebracht sind, in welchem eine Reihe jeweils auf diese Quertraversen (5) zentrierte Aussparungen (34) angeordnet sind, die jeweils das Gehäuse (61) eines Zylinders (6) bilden, dessen Kolben (62) sich auf der entsprechenden Quertraverse (5) abstützt.
  11. Rollenrichtmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß der Tragrahmen (4) ein sämtliche Rollen (21, 22) umgebendes rechteckiges Gestell (40) umfaßt, dem eine Vielzahl parallel zu den Achsen der Rollen (21) querverlaufender Führungstrennungen (41) zugeordnet sind, welche im Abstand voneinander derart angeordnet sind, daß sie die langgestreckten Aussparungen (45) begrenzen, deren Anzahl derjenigen der Rollen entspricht und in denen die Quertraversen (5) aufgenommen sind, wobei jede an ihren beiden Enden gleitende Mittel (52, 52') zur Abstützung auf dem Gestell umfaßt.
  12. Rollenrichtmaschine nach Anspruch 11, dadurch gekennzeichnet, daß jede Quertraverse (5) einen geraden rechteckigen Querschnitt mit einer mindestens seiner Breite entsprechenden Höhe besitzt, um somit eine ausreichende Trägheit aufzuweisen, damit diese Quertraverse (5) mit der aktiven Rolle (21) und den entsprechenden Stützrollen eine halbstarre Einheit bildet, die sich entsprechend der Verteilung der angreifenden Kräfte über die Länge der zugeordneten aktiven Rolle (21) mit einer möglichen Gleitbewegung in der entsprechenden Aussparung (45) verformen kann.
  13. Rollenrichtmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß der Tragrahmen (4) auf der den Rollen entgegengesetzten Seite zur Bildung eines Gehäuses durch eine alle Quertraversen (5) abdeckende, die Seiten des Gestells (40) verbindende Platte (43) verschlossen ist, wobei diese Platte (43) senkrecht zu jeder Quertraverse (5) eine Vielzahl Durchgangsöffnungen (44) für die Kolben (62) der zwischen der Quertraverse (5) und dem Balken (3) angeordneten Zylinder (6) aufweist.
  14. Rollenrichtmaschine nach einem der vorangehenden Ansprüche, dadurch gekennzeichnet, daß die aus dem rahmenförmigen Hohlteil und den Quertraversen (5) mit den aktiven Rollen (21) und den zugeordneten Stützrollen (22) bestehende Einheit eine Kassette bildet, die durch Verschiebung parallel zu den Achsen der Rollen (21) aus der Richtmaschine herausgefahren werden kann.
  15. Rollenrichtmaschine nach Anspruch 14, dadurch gekennzeichnet, daß jede Kassette durch lösbare auf dem Balken (3) abgestützte Spannpratzen (36) in der Arbeitsstellung auf dem entsprechenden Balken (3) beaufschlagt wird.
  16. Einstellverfahren zum Planrichten, das auf ein sich gemäß einer Längsdurchlaufrichtung x'x bewegendes Band in einer Richtmaschine mit ineinandergreifenden Rollen nach einem der vorangehenden Ansprüche angewendet wird, dadurch gekennzeichnet, daß zur Bestimmung einer Bezugshöhe der einen gesamten Richtrollen-Baugruppe (2) zur anderen (2') die Position eines der Balken (3) gegenüber dem anderen (3') eingestellt wird und daß, bei mit ihren Stützrollen (22) auf einer senkrecht zur Banddurchlaufebene gleitbar montierten Quertraverse (5) angeordneter, und auf dem entsprechenden Balken (3) über mindestens zwei Hydraulikzylinder (6a, 6b) abgestützter Richtrolle (21), die relativen Höhen mindestens einer Richtrollen-Baugruppe zur Bezugshöhe durch Einzeleinstellung der Positionen der Stützzylinder (6) der den Rollen (R1, R2 ...) dieser Baugruppe entsprechenden Zylinderreihen genau derart bestimmt werden, daß die Höhe und der Grad der Verschachtelung dieser Rollen (R1, R2 ...) an eine bestimmte Verteilung der Planrichtkraft auf dem Band angepasst wird, wobei die jeweils auf diese Zylinder (6) wirkenden Kräfte durch einen Sicherheitswert begrenzt sind, der einer durch jede der Richtrollen (21) aufgenommenen maximalen Planrichtkraft entspricht.
  17. Verfahren nach Anspruch 16, dadurch gekennzeichnet, daß ein Welligkeitsprofil mit einer Folge abwechselnder Biegungen zur Realisierung eines gewünschten Planrichteffekts unter Berücksichtigung der physikalischen und dimensionsgerechten Bandeigenschaften definiert wird, und daß die Höhen mindestens einiger Richtrollen der beiden Baugruppen (R1, R2, R5 ...) durch Einstellung der Positionen der entsprechenden Stützzylinder derart anpasst wird, daß die aktiven Mantellinien dieser Rollen (R1, R2, R5 ...) die Banddurchlaufbahn unter Bestimmung des vorher definierten Welligkeitsprofils umgrenzen.
  18. Verfahren nach einem der Ansprüche 16 und 17, wobei jedem Balken (5) mindestens drei Stützzylinder (6), jeweils ein mittiger Zylinder (6a) und zwei seitliche Zylinder (6b, 6c) zugeordnet sind, dadurch gekennzeichnet, daß die Höhe jeder Richtrolle (21) entsprechend einem bestimmten Verschachtelungsgrad durch Einstellung der Position des mittigen Zylinders (6a) des entsprechenden Balkens (5) je nach den vorgesehenen Durchbiegungen der verschiedenen Gerüstbestandteile unter Berücksichtigung der angreifenden Kräfte gesteuert wird und der Abstand zwischen den gemessenen Positionen der beiden seitlichen Stützzylinder (6b, 6c) dieses Balkens (5) bestimmt wird und diese Positionen korrigiert werden, um den gemessenen Abstand auf einen der Parallelität der Richtrolle (21) mit der Bezugshöhe entsprechenden Bezugsabstand zurückzufahren.
  19. Verfahren nach Anspruch 18, dadurch gekennzeichnet, daß die Druckkräfte zwischen den drei Zylindern (6a, 6b, 6c) jeder Quertraverse (5) unter Berücksichtigung von deren relativen Positionen verteilt werden, so daß die Geradlinigkeit der mit dem Erzeugnis in Kontakt befindlichen aktiven Mantellinie der in Betracht kommenden Planrichtrolle (21) gewährleistet bleibt.
  20. Verfahren nach einem der Ansprüche 16 bis 19, wobei die Richtmaschine eine ungerade Anzahl (n) ineinandergreifender Rollen (1, 3, 5 ...n) in einer Baugruppe (2') bzw. (2, 4, 6 ... n-1) in der anderen Baugruppe (2) aufweist, dadurch gekennzeichnet, daß die Position der mindestens zwei jeweils oberhalb und unterhalb des Bandes angeordneten Rollen entsprechenden Zylinder (p) bzw. (q) der jeweiligen beiden Baugruppen eingestellt wird, und mindestens der Druck der den beiden Rollenpaaren (p-1, p+1) bzw. (q-1, q+1) entsprechenden Zylinder, welche jeweils diese positionsgeregelten Rollen (p) und (q) umgrenzen, zur Bestimmung mindestens zweier Biegungen in entgegengesetzten Richtungen auf diesen Rollen (p und q) eingestellt wird, wobei der Ort der letzteren in den jeweiligen beiden Baugruppen (2, 2') und deren relative Höhen zu der Bezugshöhe, sowie die mit Druckkräften beaufschlagten Rollen, die sie umgrenzen, entsprechend den technischen Eigenschaften des zu richtenden Bandes zur Erzielung des gewünschten Planeffekts bestimmt werden.
EP96913592A 1995-04-14 1996-04-15 Richtmaschine mit ineinandergreifenden rollen und anwendungsverfahren einer solchen richtmaschine Expired - Lifetime EP0765196B1 (de)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
FR9504557A FR2732912A1 (fr) 1995-04-14 1995-04-14 Planeuse a rouleaux imbriques
FR9504557 1995-04-14
PCT/FR1996/000573 WO1996032212A1 (fr) 1995-04-14 1996-04-15 Planeuse a rouleaux imbriques et procede de mise en ×uvre d'une telle planeuse

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EP0765196A1 EP0765196A1 (de) 1997-04-02
EP0765196B1 true EP0765196B1 (de) 2001-11-07

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JP (1) JPH10501470A (de)
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CA (1) CA2192828C (de)
CZ (1) CZ292110B6 (de)
DE (1) DE69616716T2 (de)
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WO2013135688A1 (de) 2012-03-15 2013-09-19 Sms Siemag Ag Vorrichtung zum richten von metallband

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DE19705457B4 (de) * 1997-02-13 2006-01-12 Sms Demag Ag Blechrichtmaschine
FR2851943B1 (fr) * 2003-03-07 2005-04-08 Dispositif et procede de calibrage d'une planeuse a rouleaux par barre instrumentee
FR2860738B1 (fr) * 2003-10-13 2006-02-03 Vai Clecim Procede d'augmentation de la precision du controle de la trajectoire du produit dans une machine a planer a rouleaux imbriques et installation de planage permettant la mise en oeuvre du procede.
DE102004041732A1 (de) 2004-08-28 2006-03-02 Sms Demag Ag Verfahren zum Richten eines Metallbandes und Richtmaschine
CN100446883C (zh) * 2005-03-28 2008-12-31 宝山钢铁股份有限公司 带钢的平整工艺
CN101804428A (zh) * 2010-04-28 2010-08-18 周锋 矫平机
CN101856680B (zh) * 2010-06-21 2011-09-28 长治钢铁（集团）锻压机械制造有限公司 校平机
CN103084435B (zh) * 2013-01-25 2015-05-13 大连三高集团有限公司 钢板矫平机辊缝调整装置
CN104148303B (zh) * 2014-06-19 2016-01-20 宁波宝新不锈钢有限公司 一种平整机擦拭器的擦拭布和抛光网的安装方法
DE102015216387A1 (de) * 2015-08-27 2017-03-02 Sms Group Gmbh Richtmaschine mit modular aufgebautem Wechselkassettensystem
KR101888892B1 (ko) * 2016-04-04 2018-08-16 주식회사 테크녹스 엠보싱 패턴 제조 장치
CN106238509A (zh) * 2016-08-24 2016-12-21 南通恒鼎重型机床有限公司 矫平机的矫平辊结构
DE102018203734A1 (de) * 2017-03-13 2018-09-13 Sms Group Gmbh Richtstrategien zum Betreiben einer Rollenrichtmaschine und Rollenrichtmaschine
CN110944764B (zh) 2017-07-21 2022-05-03 诺维尔里斯公司 低压轧制控制金属基材表面纹理化的系统和方法
CN107774742A (zh) * 2017-12-07 2018-03-09 中国重型机械研究院股份公司 一种新型变辊距板材矫直机
CN111957763A (zh) * 2019-05-20 2020-11-20 张挺锋 工作辊及支承梁变形量测量装置
CN116713347B (zh) * 2023-08-10 2023-11-03 太原科技大学 用于拉伸弯曲矫直工艺的金属极薄带材可变包角压紧装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2013135688A1 (de) 2012-03-15 2013-09-19 Sms Siemag Ag Vorrichtung zum richten von metallband

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CN1155855A (zh) 1997-07-30
KR970703823A (ko) 1997-08-09
DE69616716T2 (de) 2002-06-13
CA2192828A1 (fr) 1996-10-17
CZ367396A3 (en) 1997-12-17
CN1068534C (zh) 2001-07-18
DE69616716D1 (de) 2001-12-13
WO1996032212A1 (fr) 1996-10-17
CA2192828C (fr) 2006-06-06
EP0765196A1 (de) 1997-04-02
JPH10501470A (ja) 1998-02-10
FR2732912A1 (fr) 1996-10-18

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