EP1601474B1 - Verfahren zum ändern der konfiguration eines walzgerüstes sowie ein zur durchführung des verfahrens geeignetes walzgerüst - Google Patents

Verfahren zum ändern der konfiguration eines walzgerüstes sowie ein zur durchführung des verfahrens geeignetes walzgerüst Download PDF

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Publication number
EP1601474B1
EP1601474B1 EP04717667A EP04717667A EP1601474B1 EP 1601474 B1 EP1601474 B1 EP 1601474B1 EP 04717667 A EP04717667 A EP 04717667A EP 04717667 A EP04717667 A EP 04717667A EP 1601474 B1 EP1601474 B1 EP 1601474B1
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EP
European Patent Office
Prior art keywords
rolls
cylinders
plane
configuration
rolling
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Expired - Lifetime
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EP04717667A
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English (en)
French (fr)
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EP1601474A2 (de
Inventor
Germain Le Viavant
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Clecim SAS
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Siemens VAI Metals Technologies SAS
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/08—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/001—Convertible or tiltable stands, e.g. from duo to universal stands, from horizontal to vertical stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/025—Quarto, four-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
    • B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
    • B21B2013/028—Sixto, six-high stands
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B29/00—Counter-pressure devices acting on rolls to inhibit deflection of same under load, e.g. backing rolls ; Roll bending devices, e.g. hydraulic actuators acting on roll shaft ends
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
    • B21B31/08—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts
    • B21B31/10—Interchanging rolls, roll mountings, or stand frames, e.g. using C-hooks; Replacing roll chocks on roll shafts by horizontally displacing, i.e. horizontal roll changing

Definitions

  • the invention relates to a method of changing the configuration of a rolling mill and an improved rolling mill for carrying out the method.
  • a rolling mill comprises, in a general manner, a holding cage having two spaced apart columns between which are arranged a set of superimposed cylinders with substantially parallel axes and comprising, at least, two working cylinders, respectively upper and lower which define a gap for passage of the product to be rolled and are supported, on the side opposite the product, respectively on two support cylinders.
  • Each cylinder is rotatably mounted, at its ends, on bearings carried by support pieces called chocks, which are slidably mounted in windows formed in the two columns of the cage, parallel to a substantially vertical clamping plane in which are placed substantially the axes of the cylinders.
  • each chock is provided, on either side of the clamping plane, sliding faces cooperating with corresponding guide faces formed on both sides of the corresponding window of the cage.
  • Hydraulic cylinders known as balancing, allow to adjust the relative positions of the cylinders for the engagement of the product or for the disassembly of the cylinders.
  • the working rolls tend to move away from each other and the air gap between the generatrices opposite must be maintained by applying a clamping force between the chocks of the support rolls.
  • the rolling force to be exerted on the product to obtain a certain thickness reduction ratio depends, in particular, on the diameter of the working rolls which determines the length of the reduction zone in which the metal flows and characteristics mechanical and metallurgical thereof such as its yield strength and composition, eg low carbon low carbon steel, stainless steel, alloy steel, etc.
  • Rolling cages used in the metallurgical industry may have several types of configuration depending on the nature of the product to be treated.
  • the most common rolling mills are of the "quarto" type having two work rolls associated, each with a larger diameter support roll, or of "sexto” type in which intermediate rolls are interposed between each working roll and the corresponding support roll.
  • This arrangement makes it possible, in particular, to offset axially, with respect to one another, the two intermediate rolls in order to apply the rolling force, not on the entire roll table, but only over the width of the roll. product. This reduces the deformations of the cylinders and gives a product of better flatness.
  • each roll can flex under the action of applied efforts. This results in a variation in thickness of the passage space of the strip between the working rolls which generates defects in profile and flatness.
  • balancing cylinders can be used to adjust the spacing of the working rolls.
  • the cylinders cooperate with bearing members often called "ears" formed on each lateral side of the chock, on either side of the clamping plane.
  • the bending forces can also be applied to the intermediate rolls which are interposed between each working roll and the associated support roll and can, in addition, be moved axially in opposite directions so as to to apply the rolling force, only over the width of the product, which makes it possible to obtain a product of better flatness.
  • the thickness of the rolling mill product may have to vary over a large range, in particular for the rolling of non-ferrous metals.
  • the chocks of the quarto working rolls and the intermediate sexting rolls are adapted so that their bearing lugs are substantially at the same level in each of the configurations.
  • Such an arrangement therefore makes it easy to adapt to a considerable variation in the thickness of the product to be rolled, for example for the rolling of a copper or aluminum slab in a reversible cage.
  • CQ, DQ, DDQ, EDDQ whose elastic limit extends from 180Mpa to 250 MPa and very hard steels having a high elastic limit (HSLA) of up to 600 MPa.
  • HSLA high elastic limit
  • IF very low carbon soft steels
  • the rolling process must be able to adapt to the quality of the treated steels, for example to take account of the fact that, in a tandem rolling mill, the rolling determines, by hardening, a progressive increase in the hardness of the produced and, consequently, the rolling force to be applied for the same reduction in thickness, from one cage to the next.
  • the application means of the clamping force may be saturated in effort if the hardness of the starting material is too high.
  • the cage itself must be adapted to the configuration, because the height of the window in which the superimposed chocks must be threaded depends on the number of cylinders and their diameters.
  • the height of the hydraulic blocks also depends on the configuration since it is necessary to provide, in a sexto cage, support and guide parts for the intermediate cylinders.
  • the invention will make it possible to extend the production range of a rolling plant, by giving the possibility of adapting the configuration of the rolling mill to the structural and dimensional characteristics of the product to be treated in order to pass through example, a quarto configuration sexto configuration or even a configuration called "Z.High".
  • the rods of the cylinders must be removably attached to the chocks and these disassembly and reassembly of the cylinders lengthen the time required for the change of configuration.
  • Such a disadvantage can be accepted when one simply has to adapt to a change in thickness of the product.
  • the configuration of the rolling mill is modified, according to the invention, so as to adapt to a change of the product to be rolled, it is necessary to minimize the time of replacement of the rolls.
  • the rolls and in particular the working rolls wear out in service and must be periodically removed for cleaning and grinding of their surface. Their diameter therefore varies over a certain range.
  • each cylinder is carried by two chocks which are also complex and expensive organs. Their disassembly is quite long and it is therefore preferable, for a replacement, to remove the block with its chocks to replace it with a new cylinder provided in advance with its chocks. This requires, however, to have a large number of chocks.
  • the invention aims to solve all of these problems through a method and an installation for changing easily and quickly the configuration of a rolling mill to better adapt to the nature of the product to be rolled.
  • the invention also makes it possible to use the same cylinders with their chocks in several configurations and thus to limit the number of cylinders and chocks the installation must be equipped with.
  • three types of working rollers having three diameters, one large, one medium and one smallest diameter are produced with a range of wear, the rolls of each type being equipped with one another. advance of their chocks, and keeping the same cage, the same means of applying the tightening and cambering forces and the same type of support rolls, and by changing the arrangement of the rollers interposed between the support rolls, one gives the mill one or other of at least three configurations, respectively, at least one quarto configuration in which the cylinders of large or medium diameter are used as work rolls, a sexto configuration in which the cylinders of medium diameter are used as working rolls and large diameter rolls are used as intermediate rolls, between each working roll of medium diameter and a cylinder and a Z.High type sexto configuration, in which the small diameter rolls are used as work rolls and the larger diameter or medium diameter rolls are used as intermediate rolls between each small work roll. diameter and a support cylinder.
  • it is used, as positive or negative bending cylinders, single-acting cylinders that bear in one direction on the chocks.
  • each cylinder remains equipped with its chocks, they can simply be returned depending on the position of the cylinder in the cage.
  • the invention makes it possible to superimpose the wear areas of the working and intermediate rolls and, thus, to have a greater total wear range of the cylinders even if a reprocessing on the surface is to be redone.
  • the invention makes it possible to associate the wear ranges in order to increase the total range.
  • the invention also covers an improved rolling mill for the implementation of the method, comprising, in a general manner, a holding cage, a set of superposed cylinders rotatably mounted, each on two chocks, means for applying a clamping force and means for applying vertical bending forces, at least on the chocks of the work rolls, respectively in a positive direction of separation of said chocks with respect to the rolling plane and in a negative direction of approximation and comprising, on each side of the clamping plane, two sets of upper and lower cambering cylinders, which cooperate with bearing members provided on the sides of each chock, on either side of the clamping plane. .
  • the rolling mill is equipped with at least three pairs of cylinders respectively having a large, a mean and a small diameter and usable as working rolls within the same stand in at least three configurations of the rolling mill, respectively at least one quarto configuration in which the rolls of large or of medium diameter are used as working rolls, a sexto configuration in which the rolls of medium diameter are used as working rolls and the rolls of large diameter as intermediate rolls and a sexto configuration of Z.High type in which the rolls of small diameter are used as working cylinders associated with lateral support means and the cylinders of medium diameter as intermediate cylinders.
  • the rolls remain equipped with their chocks and the chocks support members, at least larger diameter cylinders, are offset in height relative to the the axis of rotation of the cylinder, so that, after displacement in height of the larger diameter cylinder and 180 ° turning of its chocks around the axis, the support members of said cylinder are substantially at the same level with respect to at the rolling plane, respectively in the quarto configuration and in the sexto configuration, and that the same bending jacks act in the positive direction on the same chocks, respectively in the working position in the quarto configuration and, after flipping, in an intermediate position in the sexto configuration.
  • the support members of the chocks of the two working rolls which, in a conventional manner, extend in projection relative to the corresponding sliding faces, are placed in each configuration substantially at the level of the plane.
  • each support member of a first working chock placed on a first side of the rolling plane is provided with a passage recess of the rod of a bending jack placed on said first side and crossing the plane rolling member for bearing, in the positive direction, on a corresponding bearing member of the second working chock placed on the second side of the rolling plane and provided with a recess for the passage of the stem of a bending cylinder placed on said second side and passing through the rolling plane to bear, in the positive direction, on the support member of the first work chock.
  • the sets of camber cylinders are centered substantially in two planes parallel to the clamping plane and spaced symmetrically on either side thereof.
  • each column of the cage is provided with two hydraulic blocks fixed, on either side of the clamping plane, on the sides of the corresponding window and comprising guide pieces in which are housed bending cylinders, respectively upper and lower, and extending projecting towards the inside of the cage, to a guiding face parallel to the clamping plane and cooperating, in the quarto and sexto configurations, with a corresponding sliding face of a working chock.
  • the sliding faces of the larger diameter chocks acting as intermediate chocks co-operate with guide faces formed on support pieces removably mounted inside.
  • these support pieces may be legs removably attached to the chocks of the two support cylinders.
  • each protruding part of a hydraulic block carries two groups of jacks respectively acting towards the rolling plane and the side opposite to it, by bearing on said projecting piece, and the support members of the chocks are placed substantially on three levels which remain the same in all configurations, respectively a central level of support of the working chocks, substantially corresponding to the rolling plane, and two levels, respectively upper and lower, support of the intermediate cylinders, placed respectively above and below the projecting parts of the hydraulic blocks.
  • each protruding part of a hydraulic block carries, in a central zone, at least one pair of opposed cylinders acting respectively in the direction of approaching and away from the rolling plane and, on either side of the this central zone, two lateral cylinders acting in the direction of removal from the rolling plane.
  • each chock of a cylinder of large or medium diameter consists of three contiguous parts, respectively a central support portion of a centering bearing of the corresponding cylinder and two end portions of support, each, two support members extending on either side of the clamping plane, fixed on two lateral sides, perpendicular to the axis, of the central part, in a removable manner allowing, d ' one hand, to secure the central portion with the two end parts for the transmission of clamping forces and, secondly, to rotate the end portions relative to the central portion, after separating the three parts.
  • each chock is provided on each side of the clamping plane with a support member for at least one central cambering cylinder placed on a first side of the rolling plane, said support member comprising at least one recess for the passage of the rod of at least one central bending cylinder placed on the other side of the rolling plane.
  • each hydraulic block of bending placed on one side of the clamping plane advantageously comprises a central group of cylinders comprising at least two pairs of opposed cylinders acting respectively on the support members of the central portions of the two working chocks placed on either side of the rolling plane, each pair comprising two cylinders respectively acting in the positive direction and in the negative direction on a bearing member of one of the chocks, and each positive cambering cylinder of a first chock placed on a first side of the rolling plane bears on the other side on the hydraulic block and passes through said rolling plane through a recess in the corresponding support member of a second chock placed on the other side of said rolling plane.
  • the central portion of a first working chock placed on a first side of the rolling plane comprises, on a first side of the clamping plane, a support member having a cooperating single support portion. with a pair of opposing camber cylinders and framed by two recesses, and on the second side of the rolling plane, a support member having two support portions spaced apart on either side of a single and cooperating recess respectively with two pairs of opposite cylinders controlled in synchronism, the arrangement of the support members and cylinders being reversed for the second working chock placed on the other side of the rolling plane.
  • the arrangements according to the invention are applicable to a rolling mill comprising means for axial displacement, with respect to each other, of the intermediate rolls in order to adapt to the width of the product the length of the rolls on which 'exerts the rolling effort.
  • each protruding piece, respectively upper or lower of a hydraulic block comprises a central portion fixed relative to the cage and two movable lateral parts placed on either side of the part.
  • central and sliding axially on the hydraulic block, and each set of bending cylinders, respectively upper or lower comprises at least one central cylinder bearing on the fixed central portion of the projecting piece and acting towards the rolling plane, and at least two lateral cylinders bearing respectively on the two movable lateral parts of the projecting piece and acting on the opposite side to the rolling plane
  • each chock comprising a central portion provided, on each side, a support member for at least one central cylinder, and two end portions contiguous on either side of the central portion and each provided, on each side of the clamping plane, a body of support for a lateral cylinder mounted on a corresponding movable part of the projecting piece.
  • This rolling mill comprises, as usual, a support cage A having two columns connected by a cross member and resting on a foundation. Each column has two amounts A1, A2 limiting a window A3 in which are threaded the chocks of the cylinders.
  • the rolling mill comprises two working rolls C1, C'1 placed on either side of a rolling plane P1 that is substantially horizontal and bearing, on the opposite side, two rolls.
  • chocks S1, S'1 slidably mounted in the windows A3 of each column A, parallel to a generally vertical clamping plane P2, in which the axes of the cylinders are placed substantially.
  • the working cylinders C1, C'1 which are also carried by chocks E1, E'1 sliding vertically.
  • each chock S1, S'1 of a support roll S, S ' is provided with lateral sliding faces S2, S'2 which slide along parallel conjugate guide faces A4. at the clamping plane P2, formed on the internal faces of the two uprights A1, A2 of the column A.
  • each window A3 of the cage is provided at the level of the rolling plane P1, bearing and guiding parts B1, B2 generally called “hydraulic blocks" for the reasons indicated above.
  • Each chock E is therefore slidably mounted along guide faces formed on the ends of parts F, F 'of the two hydraulic blocks which project from both sides of the window A3, towards the inside of the -this.
  • each type of cylinder may vary over a certain range because, as indicated above, High, it is necessary to rectify periodically, by machining, the outer face of cylinders whose surface quality may deteriorate in the long run. This is the case, in particular, of the working rolls which are in contact with the rolled product. But the other cylinders, intermediate or support, must also be replaced after some time of use, by new cylinders ground.
  • a rolling plant must therefore be equipped with several examples of cylinders of each type having, in the new state, a determined diameter which can then decrease over a certain wear range, as and as successive rectifications.
  • Each cage must therefore be equipped with means for clamping and guiding the cylinders extending over a range of adjustment which depends not only on the variation in thickness of the product but also on the number of cylinders and their diameters.
  • the invention makes it possible to give the same rolling mill one or the other of three configurations respectively quarto (a), sexto (b) or Z .High (c), keeping the same cage A, the same support rolls S, S ', the same means D of application of the clamping force, the same hydraulic blocks B1, B2 and the same bending means V, V '.
  • Figures 2, 3 and 4 show respectively in cross section and for each configuration (a), (b), (c), the central portion of the cage, between the support cylinders.
  • the rolls are supported on each other along a common generatrix, the two working rolls C1, C'1 being spaced apart, simply, from an air gap corresponding to the thickness to give the product to be rolled.
  • the overall height of the set of cylinders depends on the configuration of the rolling mill.
  • the height H of the window A3 must therefore be sufficient to allow the threading of all the chocks in the most bulky configuration, that is to say the sexto configuration shown in FIG. 3, and for the maximum diameter of the cylinders. of each type.
  • the height of the hydraulic blocks B1, B2 which carry the parts F, F 'for guiding the working chocks and the sets V, V' of bending cylinders depends on the number of cylinders placed between the support cylinders and their diameters.
  • these hydraulic blocks B1, B2 are fixed on the uprights A1, A2, on each side of the window B, their height is limited to the space between the chocks S1, S'1 of the support rolls S , S 'and must therefore be reduced in the quarto configuration for which only two working rolls C1, C'1 are interposed between the support rolls S, S'.
  • the invention allows, on the other hand, to give the same rolling mill one of the three configurations (a), (b), (c) shown in Figure 1 while maintaining the same cage A and the same hydraulic blocks B1, B2 .
  • the invention makes it possible to give the hydraulic blocks B1, B2 a minimum height (h), valid for all configurations and which, in practice, can be of the same order as the sum of the diameters of the working cylinders C1, C'1 in the quarto configuration, as shown in FIG.
  • each of said hydraulic blocks comprises only two projecting parts F, F 'which carry bending cylinders V, V' acting in the positive direction and in the direction negative, these cylinders being further centered in two vertical planes Q1, Q2 parallel to the clamping plane and spaced symmetrically on either side thereof.
  • chocks adapted to the three configurations and of the type shown in perspective are used in FIGS. 4, 5 and 6, the mounting of said chocks between the hydraulic blocks being shown in FIGS. 7 to 12.
  • the diameters of the rolls can vary over a certain wear range and the various rolling mill members, in particular the cage, the hydraulic blocks and the bending jacks, are normally adapted to a certain type of roll. .
  • the cylinders must be dismantled for maintenance and rectification after use and it is necessary to reduce the downtime of the rolling mill, it is normally equipped with several sets of cylinders for the rapid replacement of cylinders in service by new rectified cylinders.
  • a roll stand is therefore associated with means for rapid replacement of the rolls which will be used for the configuration change according to the invention.
  • each cylinder is disassembled with its chocks and new cylinders must be equipped in advance, in the workshop, their two chocks with bearings.
  • the roll stand shown in FIG. 1 will be equipped on the one hand with a certain type of support rolls S, S 'which remains the same in all configurations and, secondly, of at least two and, preferably, three types of working rolls having different diameters, respectively cylinders of large diameter C1, cylinders means C2 diameter and C3 small diameter cylinders.
  • the configuration change can be made very quickly, for example using a known type of replacement system in which the cylinders are disassembled and replaced by displacement parallel to their axis, each chunk being provided with rollers rolling on rails formed on the cage, at a disassembly level for which the rollers are spaced from each other so that their surface is not deteriorated .
  • the support cylinders S, S'4 which can, moreover, remain in the cage, are all first, upwards and downwards, substantially to the levels it must occupy in sexto configuration, and the working cylinders C1, C'1 are placed at their disassembly level.
  • a replacement device comprising two boxes, respectively an empty box in which are transferred the two working rolls C1, C'1 previously in service, and a box in which were placed on the one hand two cylinders of medium diameter C2, C'2 at the working rolls and, secondly, at the levels of the intermediate rolls, two cylinders of large diameter C1, C'1, of the same type as those which have just been removed . All these cylinders were equipped in advance with their chocks. After placing the new cylinders in alignment with the rails, they are introduced into the cage in the service position and the support cylinders can be tightened. In known manner, to facilitate disassembly and replacement, the cylinders and their chocks can be placed in cassettes comprising either two working rolls C1, C'1, or a set of two working rolls and two intermediate rolls, for the sexto configuration.
  • the diameters can vary over a certain range.
  • the support rolls remain in place in the cage.
  • the two cylinders of the same type can be equipped with the same chocks which are arranged in such a way that, by simple turning, they can equip either an upper cylinder or a lower cylinder. It thus benefits from a modular arrangement making it possible to have in stock, simply, three types of chocks, respectively for large diameters, for average diameters and for small diameters and to equip on demand the new cylinders by orienting the chocks according to the arrangement they must occupy, either above or below the rolling plane.
  • Figures 6, 7 and 8 show respectively the three types of chocks usable for a large diameter cylinder ( Figure 6) of medium diameter ( Figure 7) or small diameter ( Figure 8).
  • each chock consists of three contiguous portions, respectively a central portion and two end portions.
  • Figure 6 shows a chock E1 for a large diameter cylinder, having a central portion 1 on the sides of which are fixed two end portions, respectively 2a, 2b.
  • Figure 6 shows a chock for a lower cylinder but an upper chock would be constituted in the same way, turning it 180 ° in block to mount it on an upper cylinder.
  • each cylinder is provided at each end with a journal which rotates in a centering bearing housed in a casing constituting the chock on which are formed the support members of the camber cylinders and the sliding faces. side.
  • the bearing (not shown) is housed in the central portion 1 of the chock and each end portion 2a, 2b consists of a flange provided with a circular hole 25 for the passage of the trunnion.
  • the central portion 1 of the chock is provided, as usually support members 11, 12 for the bending cylinders. In the example shown, these support members form ears extending projecting from the sides 15 of the chock on which are provided the sliding faces thereof, which are parallel to the clamping plane P2 ( Figure 2).
  • the arrangement of the support members is particular. Indeed, on one side of the chock, for example the right side in Figure 6, the support member 12 has a central recess 14 between two spaced bearing portions 12a, 12b. On the other hand, on the other side of the clamping plane, the support member 11 comprises a single support portion between two recesses 13a, 13b. In addition, the two support members 11, 12 are offset in height relative to the x'x axis of the pin threaded into the chock so that, in the working position shown in Figure 2, these organs of support are located substantially at the rolling plane P1.
  • each flange 2a, 2b is provided with a protruding portion forming a stud 23 extending horizontally and capable of engaging in a conjugate groove of the same section, formed on the side of the central portion 1 of the chock and forming a mortise.
  • a chock of the type shown in Figure 6 can be arranged in various ways, by turning, or all of the chock, or only the end parts.
  • the entire chock by turning 180 ° about the x'x axis of the entire chock, it can be mounted either on an upper working cylinder C1 or a working cylinder lower C'1, in a quarto configuration.
  • the same chock can be adapted to the configuration sexto maintaining substantially the same spacing of the support members relative to the rolling plane P1.
  • Figures 9 and 10 show the arrangement and use of two chocks of the type of Figure 6, respectively for the positive bending and for the negative bending of the working rolls, in the quarto configuration.
  • the respective positive and negative cambering of the rolls is performed by two sets of cylinders, respectively upper V and lower V ', which are centered in two planes Q1, Q2 parallel to the clamping plane P2.
  • these bending cylinders are supported on projecting parts F, F 'of the two hydraulic blocks B1, B2 fixed on both sides of the window A3.
  • each hydraulic block has only two projecting parts. spaced apart on both sides of the rolling plane, and, secondly, the support members of the chocks can be placed, by simply turning them, or between the two projecting parts, substantially at the level of rolling plane, above and below it.
  • Such an arrangement makes it possible, in fact, to reduce the height requirement of the hydraulic blocks, by defining only three support levels of the chocks which remain the same in all the configurations, respectively a central level of support of the corresponding work chocks. substantially to the rolling plane and two levels, respectively upper and lower, support of the intermediate cylinders placed respectively above and below the projecting parts of the hydraulic blocks.
  • FIGS. 9 and 10 are partial views, in perspective, showing, in a quarto configuration, the arrangement of the working chocks as well as the bending cylinders, respectively in the positive direction in FIG. 9 and in the negative direction in FIG. 10.
  • chocks In this quarto configuration, large diameter cylinders associated with chocks of the type shown in FIG. 6 are used and it is seen that, in a particularly advantageous manner, the same chocks can, by simple reversal, serve as upper chock E1, or lower chock E'1, each chock being symmetrical with respect to a median plane perpendicular to the x'x axis of the trunnion.
  • Each hydraulic block B1, B2 comprises a solid piece 5 fixed on the inner face of the corresponding amount A1, A2 of the column A and carrying two parts 6, 6 'placed symmetrically with respect to the rolling plane P1 and which project. inwardly of the window to an end 61, 61 'carrying a vertical guiding face of the corresponding chock E1, E'1.
  • the jacks are arranged in two groups, respectively a central group of jacks acting towards the rolling plane P1 and a group of lateral jacks placed on either side of the central group and acting from opposite side to the rolling plane P1.
  • These two groups of cylinders are placed, respectively, in a central portion 62 and two lateral parts 63, 64 of the projecting parts 6 and are centered on the same plane Q1, Q2 parallel to the clamping plane P2, on both sides. other of it.
  • the central portion 62 is integral with the solid part 5 fixed on the corresponding amount of the cage while the two lateral parts 63, 64 can slide axially in grooves 51, 51 'formed on this part 5.
  • each projecting piece 6, 6 ' carries three jacks all acting towards the rolling plane but controlled separately, one for positive bending and the other for bending negative.
  • the cylinders placed in the lateral parts 63, 64 act on the opposite side to the rolling plane, only for positive cambering.
  • FIG 9 is a partial view, in perspective, showing only positive bending cylinders.
  • the upper chock E1 placed above the rolling plane comprises a central portion 1 provided with two support members 11, 12 projecting from either side of the sides 15 of the chock, respectively to the right (11) and to the left (12) in the figure, these support members being placed at a level substantially corresponding to that of the rolling plan.
  • the two support members extending on either side of the central portion 1 of the chock have inverted slots profiles, one having a recess central framed by two support parts while the other has a central support portion framed by two recesses.
  • the central portion 1 of the upper chock E1 placed above the rolling plane comprises, on the right, a central support portion 11 flanked by two recesses 13a, 13b while the 12 support ear placed on the left side and not visible in the figure, has a central recess flanked by two support parts.
  • the lower chock E'1 comprises, on the right side, two bearing portions 11'a, 11'b flanking a central recess 13 ', the disposition being reversed on the left side.
  • the support members vis-à-vis have overlapping tooth profiles.
  • the positive bending of the upper chock E1 can be controlled by a central jack V'1 mounted in the central part of the corresponding projecting piece 6 'and passing through the rolling plane P1 to exert a positive bending force on the central support part 11 of the upper chock 1.
  • a positive bending force can also be exerted by lateral cylinders, respectively V3a, V3b on the right side and V4a, V4b on the left side, mounted in the lateral parts 63, 64 of the projecting piece 6 and acting in the positive direction, that is to say on the opposite side to the rolling plane, on the bearing members of the two end portions 2a, 2b of the chock, respectively 21a, 21b on the right side and 22a, 22b on the left side.
  • the positive bending forces can be applied by all cylinders and two levels on each working chock in the quarto configuration, which allows to have a higher bending effort.
  • the central group of jacks cooperating with the central parts 1, 1 'of the two chocks E1, E'1, consists of at least two pairs of opposed jacks acting respectively in the positive direction and in the negative direction on both sides of the corresponding support member of the chock.
  • the central portion 1 of the upper chock E1 is provided with a central support member 11 on which bears, in the direction negative, a central cylinder V1 mounted in the central portion 62 of the upper projecting piece 6 of the hydraulic block and, therefore, opposite to the positive camber cylinder V'1 of the same chock, which is placed on the other side of the rolling plane and passes through it.
  • the negative curve of the bottom chord E'1 is made, on the right side of the figure, by two cylinders V'1 a and V'1b mounted in the lower projecting piece 6 ', which exert bending forces directed towards the rolling plane on the bearing parts 11'a, 11'b passing on both sides of the jack V'1 positive bending of the upper chuck E1, and are opposed to the cylinders V1 a, V1 b positive bending of the same lower chock E'1, mounted in the upper projecting piece 6.
  • the arrangement is reversed on the hydraulic block B2 placed to the left of the clamping plane and the upper projecting part 6 carries in its central part two negative bending cylinders of the upper chock E1 and a central cylinder bending positive of the lower chock E'1, the arrangement being reversed on the central portion 62 'of the lower projecting piece 6' of the hydraulic block B2.
  • intermediate cylinders of the same type as the working cylinders C1, C are used according to the invention. 1 of the quarto configuration, which are therefore spaced apart from each other in order to set up medium-diameter work rolls C2, C'2.
  • the ends 61 of the two protruding parts 6, 6 'then serve to guide the working chocks E2, E'2. Since, according to one of the features of the invention, the height of the hydraulic blocks B1, B2 must be limited to that which is necessary for the quarto configuration, the guidance of the intermediate chocks E1, E'1, in the configuration sexto, is provided by two support pieces B3 bearing laterally on the uprights A1, A2 which limit the sides of the window A3 and on which are formed vertical guide faces (f) parallel to the clamping plane P2.
  • the hydraulic blocks B1, B2 still define three support levels of the bending cylinders, respectively a central level H1 corresponding substantially to that of the rolling plane P1 and two levels, respectively upper H2 and lower H'2 placed at above and below the protruding parts 6, 6 '.
  • the two sets of cylinders V, V 'placed in these protruding parts 6, 6' remain the same but their functions are different.
  • the central cylinders V1, V2, V'1, V'2 which act at the central level H1, in the direction of the rolling plane P1 will be used for the positive and negative bending of the working cylinders C2 , C'2 whereas the lateral cylinders V3, V4, V'3, V'4 which act at the H2 and H'2 levels, towards the opposite side of the rolling plane, serve for positive cambering of the intermediate cylinders C1, C ' 1.
  • the support members 21, 22 change from one side to another and are substantially aligned with the support members 11, 12 of the central part 1.
  • the support members 21, 22 of the end portions substantially return to the same level H2 as in the quarto configuration.
  • the cylinders V3a, V3b placed on the right side therefore exert positive bending forces on the bearing members 22a, 22b of the two end portions 2a, 2b of the upper intermediate chock E1.
  • the two support members 21 placed to the left after reversal cooperate with the lateral cylinders V4 for the positive camber of the intermediate cylinder C1.
  • the arrangement is the same, in the opposite direction, for the chock E'1 of the lower intermediate cylinder C'1.
  • the chocks of the cylinders of medium diameter which, in the sexto configuration, constitute the working rolls C2, C'2, are similar to the chocks E1, E'1 of the large-diameter rolls and therefore comprise a central portion 10 on which are joined two end portions 20a, 20b.
  • the bearings not shown in the figures, are adapted to the diameter of the trunnions of cylinders C2, C'2 of medium diameter, but the spacing between the lateral faces 150 of the work chocks E2, E'2 is the same that the spacing between the side faces 15 of the chocks E1 large diameter.
  • the sliding faces 150 of the chocks E2, E'2 can therefore slide along the same guide faces 61 formed at the ends of the protruding parts 6, 6 'of the two hydraulic blocks B1, B2.
  • the sliding faces 150 of a chock E2 medium diameter extend only over a portion of the height of the chock, this being provided, on the remaining part, with two sliding lateral faces 16 whose spacing is reduced.
  • the end portions 20a, 20b are fixed on the central portion 10 so that their support members 210, 220 are at the same level as the support members 110, 120 of the central portion 10.
  • Figures 11 and 12 show, in perspective, the arrangement of the bending cylinders to the right of the clamping plane, respectively in the positive direction in Figure 11 and in the negative direction in Figure 12.
  • the upper working chock E2 is turned upside down relative to FIG. 7, so that its support members 210, 220 are substantially at the level of the rolling plane P2.
  • the sliding faces 150 extending upwardly to slide between the ends 61 of the upper projecting pieces 6.
  • the positive cambering of the working roll C2 is effected, to the right of the figure, by the central cylinder V'1 which is mounted on the other side of the rolling plane and passes therethrough to be applied to the support member 110 of the central portion 10.
  • the support members 210a, 210b of the end portions 20a, 20b of the working chock E2 are thus not used for cambering but simply carry rollers G which, in a conventional manner, roll on rails R put in place for disassembly, these rollers G being, thus, sufficiently spaced to ensure, in good conditions, the sliding retention of the chock.
  • cylinders of medium diameter C2, C'2 provided with their chocks E2, E'2 can be used as intermediate cylinders in a Z.High type sexto configuration, as shown in the view (c) of Figure 1, as well as in Figures 4, 13 and 14.
  • Such a chock preferably comprises, preferably, three contiguous portions, respectively a central portion 3 and two end portions 4a, 4b.
  • the central portion 3 carries the centering bearings of the cylinder and can have a fairly reduced height, the journals of a working cylinder having a small diameter in the case of a Z.High mounting.
  • this central portion 3 is provided, on either side of the x'x axis of the bearing, with two sliding faces 35 whose spacing corresponds to that of the facing ends 61 of the protruding parts 6 two hydraulic blocks B1, B2 and two support members 31, 32 which protrude from the plane of the sliding faces 35.
  • the chock is shown in its position E3 corresponding to an upper work roll and therefore comprises a central bearing portion 31 which extends only over part of the length of the chock and is surrounded by two recesses 33a, 33b.
  • the support member 32 comprises two parts spaced apart on either side of a central recess 34.
  • the chock E3 of the upper work roll C3 is provided on the right of the figure with a bearing portion 31 which extends substantially at the level of the rolling plane P2. and passes between the rods of the two cylinders V1, V'1 respectively housed in the projecting parts 6, 6 ', the lower cylinder V'1 acting in the positive direction (FIG. 13) and the upper cylinder V1 in the negative direction (FIG. Figure 14).
  • the chock E'3 of the lower cylinder C'3 is provided on the right of the figure with two bearing parts 31'a, 31'b on which two pairs of opposed cylinders act, respectively, the upper cylinders. V1 a, V1 b in the positive direction ( Figure 13) and the lower cylinders V'1a, V'1b in the negative direction ( Figure 14).
  • the invention allows to exert positive bending forces on the intermediate cylinders.
  • the sliding faces 150 of a medium-diameter chock E2 extend only over part of the height thereof and are extended by narrower sliding faces 16 which, in the assembly Z.High slide along the inner faces 37 of the legs 36 of the central portion 3 of the chock E3 of the small diameter cylinder C3.
  • the guide faces 61 formed at the ends of the protruding parts 6, 6 ' serve, over part of their height, to guide the work chocks E3, E'3 and, on the part remaining, guiding intermediary chocks E2, E'2 which are also guided, by their sliding faces 16, on the legs 36 of the working chocks E3, E'3.
  • the two side portions 63, 64 of a projecting piece 6 are mounted to slide axially in a groove 51 of the solid portion 5 of the hydraulic block B, the central portion 62 remaining fixed.
  • the central cylinders V2, V'2 which act towards the rolling plane B2 remain fixed axially but the lateral cylinders, respectively upper V3, V4 and lower V'34, V'4 mounted on both sides of the clamping plane, on the moving parts 63, 64 of the parts projection 6, 6 'can move axially with the chocks of the corresponding cylinder.
  • FIG. 11 corresponds to view (c) of Fig. 15 with a backward shift for the upper intermediate roll C1 and forwards for the lower intermediate roll C'1.
  • FIG. 12 corresponds to the view (a) of FIG. 15 with a shift towards the front of the upper intermediate cylinder C1 and towards the rear of the lower intermediate cylinder C'1.
  • view (b) of FIG. 15 which corresponds to the quarto configuration shown in FIGS. 9 and 10, there is no axial shift of the rolls, the moving parts 63, 64 being spaced symmetrically with respect to the central piece 62, as shown in view (b) of FIG.
  • the intermediate cylinders C1, C'1 or C2, C'2 can be moved axially with their chocks and the positive bending cylinders V3, V4, V'3, V'4.
  • the chocks of the work rolls remain centered in the median plane of the hydraulic blocks B1, B2, as well as the central cylinders V1, V2, V'1, V'2.
  • the cylinders can be disassembled and replaced by moving parallel to their axis, rolling on removable or retractable rails.
  • These rails may consist, for example, of sections 7 slidably mounted on grooves 52 parallel to the axes of the cylinders and formed on each side of the clamping plane, on the solid portions 5 of the two hydraulic blocks B1, B2.
  • these grooves may be provided on four levels, on either side of each projecting piece 6, 6 ', to allow the assembly of four pairs of rails, respectively upper 71, 72 and lower 71 ', 72'.
  • the support members of the end portions 2, 20, 30, of each type of chock E1, E2, E3 carry rollers G spaced axially.
  • FIG. 5 shows the cylinders in disassembly position, for the sexto configuration.
  • the two upper cylinders, C2 and C1 working respectively can be raised by their positive bending cylinders, a little above the rail levels to allow the introduction of the latter inside the cage, by axial sliding on the grooves 52.
  • the rolls can then be lowered so that their rollers G rest on the rails 71, 72.
  • the rollers mounted at the ends of the support members of the chocks E'2, E'1 of the two lower cylinders, respectively C'2 working and C'1 intermediate, are located in any case, above the level of the lower rails 72 '71' which can therefore be set up, by axial sliding, for disassembling the rolls. If the lower support cylinder S 'is lowered by means of not shown timing means, the two cylinders C'1, C'2 descend with it and their rollers come to rest on the respective rails 72', 71 'to allow the disassembly and reassembly of the cylinders by axial displacement.
  • the profiles 7 constituting the rails could also be provided with retractable support parts to allow adjustments of the levels of the chocks, during rolling.
  • the height H of the window A3 must, however, correspond to the total height of the chocks in the sexto configuration and that is why it is advantageous in the quarto and Z.High configurations represented. respectively on the views (a) and (c) of Figure 1, to have, at the ends of each window A3, two massive pieces M, M 'forming interposed shims, on the one hand between the clamping means D and the chocks S1 of the upper support cylinder and secondly between the lower part of each window A3 and unrepresented wedging means on which support the lower support chocks S'1. This avoids increasing the stroke of the clamping cylinders D.
  • the positive and negative cambering of the rolls is ensured by pairs of opposing single-acting cylinders acting, respectively, towards the rolling plane and on the side opposite to it. .
  • such cylinders are simply applied to the support members of the chocks and release them when they are retracted. It would, however, be possible to use double-acting cylinders having a rod removably attached to the support member of the chock and thus, to ensure the negative and positive bending of the corresponding cylinder.
  • the support members of the chocks sometimes called “ears" project protruding from the sliding faces on each side of the chock.
  • the invention could, however, adapt to other known arrangements.
  • the cambering forces could be applied, on each side of the chock, on an intermediate piece engaging in a groove formed in the corresponding sliding face, this groove being offset with respect to the axis of the empoise so as to allow two positions thereof, by simple reversal.
  • the invention does not necessarily apply to a new installation but has, on the contrary, great advantages for the modernization of an existing installation.
  • the invention also makes it possible, in the context of modernization, to extend the range of products that can be processed in an existing mill while keeping the same cage, which is simply adapted, for example to place it there. hydraulic blocks of bending.
  • an existing quarto cage having a window height too low for a conventional sexto configuration could be modernized, thanks to the invention, allowing to go from a quarto configuration to a Z.High configuration or vice versa, the range of laminatable products being thus extended.
  • cages that are symmetrical with respect to the rolling plane, but in certain cases the arrangements just described would make it possible to produce asymmetrical assemblies.
  • the invention therefore provides many possibilities to respond very flexibly to a change in the characteristics of the products to be rolled.
  • the modular construction that has been described has the advantage of using only three types of chocks for all configurations, because each chock is provided, on either side of the clamping plane, support members having inverted profiles and can be used on either side of the rolling plane.
  • chocks having the same support members on either side of the clamping plane, but with inverted slot profiles above and below the rolling plane.
  • a superior chock could have, on each side, a single support part placed between two recesses, the chock lower part having, conversely, support members comprising, on each side, two bearing parts flanking a single recess.
  • Such an arrangement would still make it possible to produce hydraulic blocks of reduced height having a C-shaped profile with two parts projecting from support of bending cylinders acting on support members placed substantially at the level of the rolling plane while traversing it in the direction of positive bending.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
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  • Jigs For Machine Tools (AREA)
  • Chemical Treatment Of Metals (AREA)

Claims (32)

  1. Verfahren zum Konfigurationswechsel eines Walzwerks, umfassend:
    - ein Haltegerüst (A), das zwei beabstandete Walzenständer hat, die jeweils mit einem Fenster (A3) versehen sind, das zwei entgegengesetzte Seiten (A1, A2) hat,
    - eine Einheit übereinanderliegender Walzen mit im Wesentlichen parallelen Achsen, die mindestens zwei Arbeitswalzen aufweisen, jeweils eine obere (C1) und eine untere (C'1), die zu beiden Seiten einer Walzebene (P1) im Wesentlichen horizontal zu einem zu walzenden Produkt angeordnet sind, und zwei Stützwalzen (S), jeweils eine obere und eine untere,
    - wobei jeder Zylinder (C1, C'1) zwei Enden aufweist, die jeweils drehend auf einem Lager installiert sind, das von einem Einbaustück (E) getragen wird, das gleitend parallel zu einer Spannebene (P2) entlang von Gleitseiten installiert ist, die mit den entsprechenden Führungsseiten zusammenwirken, die auf den zwei Seiten des entsprechenden Fensters (A3) des Gerüsts eingerichtet sind,
    - Mittel (D) zum Anlegen einer Spannkraft zwischen den Einbaustücken (S1, S'1) der Stützwalzen (S, S'),
    - Mittel zum Anlegen senkrechter Durchbiegekräfte, die jeweils zu jeder Seite der Spannebene (P2) zwei Einheiten (B, V) hydraulischer Durchbiegezylinder zumindest der zwei Arbeitswalzen, nämlich der oberen (C1) und der unteren (C'1) aufweisen,
    - wobei die Durchbiegezylinder (V, V') mit Stützorganen zusammenwirken, die auf den Seiten der Einbaustücke (E) der Walzen zu beiden Seiten der Spannebene (P2) eingerichtet sind,
    Verfahren, bei dem man das Walzwerk von einer Quarto-Konfiguration zu einer Sexto-Konfiguration und umgekehrt übergehen lässt, indem man jede Arbeitswalze (C1, C'1) der Quarto-Konfiguration durch eine Arbeitswalze mit kleinerem Durchmesser (C2, C'2) und eine Zwischenwalze ersetzt und dabei das gleiche Gerüst (A), die gleichen Mittel (D, B, V) zum Anlegen von Spann- und Durchbiegekräften und den gleichen Stüizwalzentyp (S, S') beibehält.
    dadurch gekennzeichnet, dass man drei Arbeitswalzentypen (C1, C'1) (C2, C'2) (C3, C'3) herstellt, die bis auf einen Abnutzungsbereich drei unterschiedliche Durchmesser, jeweils einen großen, einen mittleren und einen kleineren Durchmesser haben, wobei die Walzen jedes Typs im Voraus mit ihren Einbaustücken ausgestattet sind, und dass durch Beibehalten des gleichen Gerüsts (A), der gleichen Mittel (D, B, V) zum Anlegen von Spann- und Durchbiegekräften und des gleichen Stützwalzentyps (S, S') und durch Wechseln der Anordnung der zwischen den Stützwalzen eingefügten Walzen man dem Walzwerk die eine oder andere von mindestens drei Konfigurationen verleiht, jeweils mindestens eine Quarto-Konfiguration, in der die Walzen mit großem (C1) oder mittlerem (C2) Durchmesser als Arbeitswalzen verwendet werden, eine Sexto-Konfiguration, in der die Walzen mit mittlerem Durchmesser (C2) als Arbeitswalzen und die Walzen mit großem Durchmesser (C1) als Zwischenwalzen zwischen jeder Arbeitswalze mit mittlerem Durchmesser (C2) und einer Stützwalze (S) verwendet werden, und eine Sexto-Konfiguration des Typs Z.High, bei der die Walzen mit kleinem Durchmesser (C3) als Arbeitswalzen verwendet werden und die Walzen mit größerem Durchmesser (C1) oder mit mittlerem Durchmesser (C2) als Zwischenwalzen zwischen jeder Arbeitswalze mit kleinem Durchmesser (C3) und einer Stützwalze (S) verwendet werden.
  2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass das Durchbiegen der Arbeitswalzen in die positive Spreizrichtung der Einbaustücke und in die negative Annäherungsrichtung erfolgt, indem zu beiden Seiten der Walzebene (P1) und zu beiden Seiten der Spannebene (P2) mindestens zwei Paare einfach wirkender Zylinder (V1, V'1) (V'1a, V'1b) verwendet werden, die auf die Arbeitswalzen mit großem Durchmesser (C C'1) in der Quarta-Konfiguration, auf die Arbeitswalzen mit mittlerem Durchmesser (C2, C'2) in der Sexto-Konfiguration und auf die Arbeitswalzen mit kleinem Durchmesser (C3, C3') in der Z.High-Konfiguration einwirken.
  3. Verfahren nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass man zu beiden Seiten der Walzebene (P1) und zu beiden Seiten der Spannebene (P2) mindestens ein Paar einfach wirkender Zylinder (V3, V'3) verwendet, die in die positive Richtung auf die Arbeitswalzen mit großem Durchmesser (C1, C'1) in der Quarto-Konfiguration einwirken, auf die gleichen Walzen mit großem Durchmesser (C1, C'1), die als Zwischenwalzen dienen, in der Sexto-Konfiguration und auf die Walzen mit mittlerem Durchmesser (C2, C'2) in der Z.High-Konfiguration einwirken.
  4. Verfahren nach einem der Ansprüche 1 bis 3, bei dem man für jeden Walzentyp über mehrere Walzenpaare verfügt, jeweils Stütz- oder Arbeitswalzen, die leicht unterschiedliche Durchmesser haben, dadurch gekennzeichnet, dass man bei einer Quarto-Konfiguration in dem Gerüst ein Paar Stützwalzen (S, S') anbringt, die einen etwas größeren Durchmesser haben als der der Stützwalzen, die für eine Sexto- oder Z.High-Konfiguration verwendet werden.
  5. Walzwerk aufweisend:
    - ein Stützgerüst (A) mit zwei beabstandeten Walzenständern, die jeder mit einem Fenster (A3) mit zwei entgegengesetzten Seiten (A1, A2) versehen sind,
    - eine Einheit übereinanderliegender Walzen mit im Wesentlichen parallelen Achsen, die mindestens zwei Arbeitswalzen, jeweils eine obere und eine untere aufweisen, die zu beiden Seiten einer Walzebene (P1) im Wesentlichen horizontal zu einem zu walzenden Produkt angeordnet sind, und zwei Stützwalzen, jeweils eine obere (S) und eine untere (S'),
    - wobei jede Walze zwei Enden hat, die jeweils drehend auf einem Lager installiert sind, das von einem Einbaustück (E) getragen wird, das parallel zu einer Spannebene (P2) entlang von Gleitseiten, die mit entsprechenden Führungsseiten, die auf den zwei Seiten des entsprechenden Fensters (A3) des Gerüsts angeordnet sind, zusammenwirken, gleitend installiert ist,
    - Mittel (D) zum Anlegen einer Spannkraft zwischen den Einbaustücken (S1, S'1) der Stützwalzen (S, S').
    - Mittel (B, V) zum Anlegen senkrechter Durchbiegekräfte, die zu beiden Seiten der Spannebene (P2) zwei Einheiten (V, V') hydraulischer Durchbiegezylinder mindestens der zwei Arbeitswalzen, jeweils einen oberen und einen unteren, aufweisen,
    - wobei die Durchbiegezylinder (V, V') mit Auflageorganen zusammenwirken, die auf den Seiten jedes Einbaustücks zu beiden Seiten der Spannebene (P2) eingerichtet sind,
    dadurch gekennzeichnet, dass es mit mindestens drei untereinander austauschbaren Walzenpaare ausgestattet ist, die mindestens drei unterschiedliche Durchmesser haben, jeweils einen großen, einen mittleren und einen kleinen Durchmesser, und die als Arbeitswalzen im Inneren eines gleichen Gerüsts in mindestens drei Konfigurationen des Walzwerks verwendet werden können, respektive mindestens eine Quarto-Konfiguration, in der die Walzen mit großem (C1, C'1) oder mittlerem Durchmesser (C2, C'2) als Arbeitswalze verwendet werden, eine Sexto-Konfiguration, in der die Walzen mit mittlerem Durchmesser als Arbeitswalzen und die Walzen mit großem Durchmesser (C1, C'1) als Zwischenwalzen zwischen jeder Arbeitswalze mit mittlerem Durchmesser (C2, C'2) und einer Stützwalze (S, S') verwendet werden, und eine Sexto-Konfiguration des Typs Z.High, bei der die Walzen mit kleinem Durchmesser (C3, C'3) als Arbeitswalzen verbunden mit seitlichen Auflagemitteln verwendet werden, und die Walzen mit größerem Durchmesser (C1, C'1) oder mit mittlerem Durchmesser (C2, C'2) als Zwischenwalzen zwischen jeder Arbeitswalze mit kleinem Durchmesser (C3, C'3) und einer Stützwalze (S, S' verwendet werden.
  6. Walzwerk nach Anspruch 5, dadurch gekennzeichnet, dass für jeden Konfigurationswechsel die Walzen mit ihren Einbaustücken (E) ausgestattet bleiben, und dass die Auflageorgane (11, 12) der Einbaustücke (E1, E'1) zumindest der Walzen mit größerem Durchmesser (C1, C'1) in der Höhe in Bezug auf die Rotationsachse (x'x) der Walze verschoben werden, so dass nach dem Höhenverschieben einer Walze mit größerem Durchmesser (C1) und Umkehren um 180° ihrer Einbaustücke (E1) um die Achse die Auflageorgane (11, 12) dieser sich im Wesentlichen auf der gleichen Ebene im Vergleich zu der Walzebene (P1) respektive in der Quarto-Konfiguration und in der Sexto-Konfiguration befinden, und dass die gleichen Durchbiegezylinder (V1, V2) zumindest in die positive Richtung auf die Einbaustücke (E1), die jeweils in Arbeitsposition in der Quarto-Konfiguration und nach Umdrehen in Zwischenposition in der Sexto-Konfiguration angeordnet sind, einwirken.
  7. Walzwerk nach einem der Ansprüche 5 und 6, dadurch gekennzeichnet, dass auf jeder Seite der Spannebene (P2) die Durchbiegezylinder, jeweils der obere (V) und der untere (V') zu beiden Seiten der Walzebene (P1) in zwei vorstehenden Teilen, jeweils einem oberen (6) und einem unteren (6') aufgenommen sind, die auf einem Hydraulikblock (B1, B2), der auf jeder Seite des entsprechenden Fensters (A3) des Gerüsts befestigt ist, eingerichtet sind.
  8. Walzwerk nach Anspruch 7, dadurch gekennzeichnet, dass sich jeder vorstehende Teil (6, 6') eines Hydraulikblocks (B1, B2) zum Inneren des Fensters (A3) bis zu einer Führungsseite (61) parallel zu der Spannebene erstreckt und in der Quarte- und Sexto-Konfiguration mit einer Gleitseite (15) des entsprechenden Einbaustücks (E1. E2) einer Arbeitswalze (C1, C2) zusammenwirkt.
  9. Walzwerk nach Anspruch 8, dadurch gekennzeichnet, dass in der Sexto-Konfiguration die Gleitseiten (15) der Einbaustücke mit größerem Durchmesser (E1, E'1), die als Zwischeneinbaustücke dienen, mit Führungsseiten (f) zusammenwirken, die auf den Stützteilen (B3) eingerichtet sind, die abnehmbar im Inneren des entsprechenden Fensters (A3) des Gerüsts (A) jeweils oberhalb und unterhalb der zwei vorspringenden Teile (6, 6') des Hydraulikblocks (B1, B2) installiert sind.
  10. Walzwerk nach Anspruch 9, dadurch gekennzeichnet, dass die Stützteile (B3, B'3) der Führungsseiten (f) der Zwischeneinbaustücke (E1, E'1) in der Sexto-Konfiguration Ständer sind, die abnehmbar auf den Einbaustücken (S1, S' 1) der zwei Stützwalzen (S, S') befestigt sind.
  11. Walzwerk nach Anspruch 7, dadurch gekennzeichnet, dass auf jeder Seite der Spannebene (P2) die zwei vorstehenden Teile, jeweils der obere (6) und der untere (6'), die zu beiden Seiten der Walzebene (P1) auf dem entsprechenden Hydraulikblock (B1, B2) eingerichtet sind, sich jeweils zum Inneren des Fensters (A3) bis zu einer Führungsseite (61, 61') parallel zur Spannebene erstrecken und in der Z.High-Konfiguratlon mit zwei übereinanderliegenden Gleitseiten, jeweils (35) eines Arbeitseinbaustücks (E3, E'3) und (150) eines Zwischeneinbatistücks (E2, E'2) zusammenwirken.
  12. Walzwerk nach einem der Ansprüche 7 bis 11, dadurch gekennzeichnet, dass die Auflageorgane (11, 12), (110, 120) der Einbaustücke der Arbeitswalzen, jeweils der oberen (C1), (G2) und unteren (C'1). (C'2) im Wesentlichen auf der Ebene der Walzebene (P1) zwischen den vorstehenden Teilen, jeweils dem oberen (6) und dem unteren (6') der zwei Hydraulikblöcke (B1, B2) angeordnet sind.
  13. Walzwerk nach einem der Ansprüche 7 bis 11, bei dem jedes Einbaustück (E1) auf jeder Seite der Spannebene (P2) mit mindestens einem Auflageorgan (11. 12) versehen ist, das sich in Bezug auf die entsprechende Gleitseite (15) des Einbaustücks (E1) so erstreckt, dass es mit den Durchbiegezylindern (V1, V2) zusammenwirkt, dadurch gekennzeichnet, dass die Auflageorgane (11, 12), (11', 12') der Einbaustücke (E1 , E'1) der zwei Arbeitswalzen (C1, C'1) in jeder Konfiguration im Wesentlichen auf dem Niveau (H1) der Walzebene (P1) zwischen den vorspringenden Teilen (6, 6') jedes Hydraulikblocks (B1, B2) angeordnet sind, und dass jedes Auflageorgan (11) eines ersten Arbeitseinbaustücks (E1), das auf einer ersten Seite der Walzebene (P1) angeordnet ist, mit mindestens einer Aussparung (13a) zum Durchgehen des Schafts mindestens eines Durchbiegezylinders (V1 a), der auf der ersten Seite angeordnet ist und die Walzebene (P1) durchquert, versehen ist, um in die positive Richtung auf ein entsprechendes Auflageorgan (11') des zweiten Arbeitseinbaustücks (E'1), das auf der zweiten Seite der Walzebene (P1) angeordnet ist, aufzuliegen, das mit mindestens einer Aussparung (13') zum Durchgehen des Schafts mindestens eines Durchbiegezylinders (V'1) versehen ist, der auf der zweiten Seite angeordnet ist und die Watzebene (P1) durchquert, um in die positive Richtung auf dem Auflageorgan (11) des ersten Arbeitseinbaustücks (E1) aufzuliegen.
  14. Walzwerk nach Anspruch 13, dadurch gekennzeichnet, dass zu jeder Seite der Spannebene (P1) jeder vorstehende Teil (6, 6') eines Hydraulikblocks (B1), (B2) zwei Gruppen einfach wirkender Zylinder trägt, jeweils (V1, V'1), (V2, V'2), die auf die Walzebene (P1) einwirken, und (V3, V'3), (V4, V'4), die auf der entgegengesetzten Seite zu diesem einwirken und dabei auf dem vorspringenden Teil (6.6') aufliegen, und dass die entsprechenden Auflageorgane der Einbaustücke (E1, E'1) auf drei Niveaus angeordnet sind, die im Wesentlichen in allen Konfigurationen gleich bleiben, respektive ein zentrales Niveau (H1) zum Aufliegen der Arbeitseinbaustücke, das im Wesentlichen der Walzebene entspricht, und zwei Niveaus, jeweils ein oberes (H2) und ein unteres (H'2) zum Aufliegen der Zwischeneinbaustücke, die jeweils oberhalb und unterhalb der vorstehenden Teile (6, 6') der Hydraulikblöcke (B1, B2) angeordnet sind.
  15. Walzwerk nach einem der Ansprüche 5 bis 14, dadurch gekennzeichnet, dass die Durchbiegezylindereinheiten, jeweils die obere (V) und die untere (V') im Wesentlichen in zwei Ebenen (Q1, Q2), die zu der Spannebene (P2) parallel und symmetrisch zu beiden Seiten von dieser beabstandet sind, zentriert sind.
  16. Walzwerk nach einem der Ansprüche 14 und 15, dadurch gekennzeichnet, dass auf jeder Seite der Spannebene (P2) und auf jeder Seite der Walzebene (P1) jeder vorstehende Teil (6) eines Hydraulikblocks (B1) mindestens einen zentralen Zylinder (V1) trägt, der in die Richtung der Walzebene (P1) einwirkt, und zwei seitliche Zylinder (V3a, V3b), die in die entgegengesetzte Richtung zu der Walzebene (P1) einwirken.
  17. Walzwerk nach Anspruch 16, dadurch gekennzeichnet, dass die seitlichen Zylinder (V3a, V3b) (V'3a, V'3b) in der Quarta-Konfiguration in die positive Richtung auf die Einbaustücke (E1) (E'1) der Arbeitswalzen, jeweils der oberen (C1) und der unteren (C'1) einwirken.
  18. Walzwerk nach einem der Ansprüche 5 bis 17, dadurch gekennzeichnet, dass jedes Einbaustück (E1), (E2) einer Walze mit großem Durchmesser (C1) oder mittlerem Durchmesser (C2) aus drei aneinander gefügten Teilen, jeweils einem zentralen Teil (1) zum Stützen eines entsprechenden Zentrierlagers der Walze (C1, C2) und zwei Endteilen (2a, 2b) besteht, die jeweils zwei Auflageorgane (11a, 12a), (11b, 12b) tragen, die sich zu beiden Seiten der Spannebene (P2) erstrecken und an den zwei seitlichen Seiten senkrecht zu der Achse des zentralen Teils (1) abnehmbar befestigt sind und einerseits erlauben, den zentralen Teil (1) mit den zwei Endteilen (2a, 2b) für das Übertragen der Durchblegekräfte zu verbinden und andererseits die Endteile (2a, 2b) in Bezug auf den zentralen Teil (1) nach Trennen der drei Teile umzukehren.
  19. Walzwerk nach Anspruch 18, dadurch gekennzeichnet, dass der zentrale Teil (1) jedes Einbaustücks (E1) auf jeder Seite der Spannebene (P2) mit einem Auflageorgan (11) (12) für mindestens einen ersten zentralen Durchbiegezylinder (V1) versehen Ist, der auf einer ersten Seite der Walzebene (P1) angeordnet ist, wobei das Auflageorgan (11) (12) mindestens eine Aussparung (13) für das Durchgehen des Schafts mindestens eines zweiten zentralen Durchbiegezylinders (V'1) aufweist, der auf der anderen Seite der Walzebene (P1) angeordnet ist.
  20. Walzwerk nach Anspruch 19, dadurch gekennzeichnet, dass jeder Durchbiegehydraulikblock (B1), der auf einer Seite der Spannebene (P2) angeordnet ist, eine zentrale Gruppe von Zylindern aufweist, die mindestens zwei Paare entgegengesetzter Zylinder aufweisen, die jeweils auf die Auflageorgane (11, 11') der zentralen Teile (1, 1') der zwei Arbeitseinbaustücke (E1, P1'), die zu beiden Seiten der Walzebene (P1) angeordnet sind, einwirken, wobei jedes Paar zwei entgegengesetzte Zylinder aufweist, die jeweils in die positive Richtung (V'1, V1a) und in die negative Richtung (V1, V'1a) auf ein Auflageorgan (11, 11') eines der Einbaustücke (E1, E1') einwirken, wobei jeder Zylinder (V'1) zum positiven Durchbiegen eines ersten Einbaustücks (E1), das auf einer ersten Seite der Walzebene (P1) angeordnet ist, auf einem vorstehenden Teil (6') des Hydraulikblocks aufliegt, der auf der zweiten Seite der Walzebene (P1) angeordnet ist und diese durchquert, indem eine Aussparung (13') durchlaufen wird, die in einem entsprechenden Auflageorgan (11') eines zweiten Einbaustücks (E'1), das auf der zweiten Seite der Walzebene (P1) angeordnet ist, eingerichtet ist.
  21. Walzwerk nach Anspruch 20, dadurch gekennzeichnet, dass der zentrale Teil (1) eines ersten Arbeitseinbaustücks (E1), das auf einer ersten Seite der Walzebene (P1) angeordnet ist, auf einer ersten Seite der Spannebene (P2) ein Auflageorgan (11) aufweist, das einen einzigen Auflageteil aufweist, der mit einem Paar entgegengesetzter Durchbiegezylinder (V1, V'1) zusammenwirkt und von zwei Aussparungen (13a, 13b) umgeben ist, und, auf der zweiten Seite der Spannebene (P2), ein Auflageorgan, das zwei Auflageteile (12a, 12b) aufweist, die zu beiden Seiten einer einzigen Aussparung (14) beabstandet sind und jeweils mit einem Paar entgegengesetzter Zylinder zusammenarbeiten, wobei die Anordnung der Auflageorgane und der Zylinder für das zweite Arbeitseinbaustück (E'1), das auf der anderen Seite der Walzebene (P1) angeordnet ist, umgekehrt ist.
  22. Walzwerk nach einem der Ansprüche 18 bis 21, dadurch gekennzeichnet, dass die seitlichen Zylinder (V3a, V3b), die auf jeden vorstehenden Teil (6) eines Hydraulikblocks (B1), (B2) aufliegen, in die positive Richtung auf Auflageorgane (21a, 21b), (22a, 22b) einwirken, die jeweils auf den Endteilen (2a, 2b) eines Einbaustücks (E1) mit größerem Durchmesser angeordnet sind, das mindestens ein Zwischeneinbaustück in der Sexto-Konfiguration oder in der Z.High-Konfiguration bildet.
  23. Walzwerk nach Anspruch 22, dadurch gekennzeichnet, dass die seitlichen Zylinder (V3a, V3b) in die positive Richtung auf die Auflageorgane (21a, 21b) einwirken, die jeweils auf die Endteile (2a, 2b) eines Einbaustücks mit größerem Durchmesser (E1), das ein Arbeitseinbaustück In einer Quarto-Konfigurafion bildet, einwirken.
  24. Walzwerk nach einem der Ansprüche 18 bis 23, dadurch gekennzeichnet, dass die Auflageorgane (21a, 21b). (22a, 22b), die auf den Endteilen (2a. 2b) jeweils eines Einbaustücks (E1) einer Walze (C1) mit großem Durchmesser (E2) oder einer Walze (C2) mit mittlerem Durchmesser mit Rollen (G) zum Laufen auf Schienen (R, 7) parallel zu der Walzebene (P1) und zu der Spannebene (P2) zur Demontage und Rückmontage der entsprechenden Walze durch paralleles Verschieben zu ihrer Achse versehen sind.
  25. Walzwerk nach einem der Ansprüche 18 bis 24, dadurch gekennzeichnet, dass jedes Einbaustück (E3) einer Walze mit kleinem Durchmesser (C3), die als Arbeitswalze in der Z.High-Konfiguration verwendet wird, aus drei aneinander gefügten Teilen besteht, jeweils einem zentralen (3) Tragteil eines Zentrierlagers der entsprechenden Walze (C3), auf jeder Seite der Spannebene (P2) mit einem Auflageorgan (31, 32) für mindestens zwei entgegengesetzte Durchbiegezylinder, jeweils ein positiver (V'1) und ein negativer (V1) versehen, und zwei Endteilen (4a, 4b), die fest mit dem zentralen Teil (3) verbunden und jeder auf jeder Seite der Spannebene (P2) mit einem Auflageorgan (41 a, 41 b), (42a, 42b) versehen sind, die mindestens eine Rolle (G) zum Rollen auf einer Schiene (R) parallel zu der Walzebene (P1) und zu der Spannebene (P2) für die Demontage der entsprechenden Walze (C3) durch Verschieben parallel zu ihrer Achse tragen.
  26. Walzwerk an einem der Ansprüche 24 und 25, dadurch gekennzeichnet, dass das Gerüst (A) mit Demontageschienen (R) versehen ist, die auf drei Niveaus angeordnet sind, jeweils einem zentralen Niveau (H1), das im Wesentlichen dem der Walzebene (P1) entspricht, die zwei übareinanderliegende Schienen (72, 72') zum Rollen der Einbaustücke der Arbeitswalzen, nämlich der oberen und der unteren aufweisen, und zwei Niveaus, jeweils ein oberes (H2) und ein unteres (H'2), die jeweils eine Schiene (71,71') zum Rollen der Einbaustücke der Zwischenwalzen, jeweils einer oberen (C1) und einer unteren (C'1) aufweisen,
  27. Walzwerk nach einem der Ansprüche 7 bis 26, dadurch gekennzeichnet, dass mindestens ein Teil (63, 64) jedes vorstehenden Teils, jeweils des oberen (6) und des unteren (6'), der eine Einheit Durchbiegezylinder trägt, parallel zu der Walzebene (P1) und zu der Spannebene (P2) auf dem entsprechendem Hydraulikblock (B1, B2) gleitend installiert ist, und dass das Walzwerk Mittel zum Steuern des gleichzeitigen axialen Gleitens mit den Durchbiagezylindern und einer entsprechenden Walze der bewegliche Teile (63, 64) der vorstehenden Teile (6) aufweist, die jeweils zu beiden Seiten der Spannebene (P2) und auf einer gleichen Seite der Walzebene angeordnet sind.
  28. Walzwerk nach Anspruch 27, dadurch gekennzeichnet, dass es Mittel zum Steuern des Gleitens jedes Paars vorstehender Teile (6), die jeweils zu beiden Seiten der Spannebene (P2) und auf der gleichen Seite der Walzebene (P1) angeordnet sind, mit einer Zwischenwalze mit großem Durchmesser (C1) in der Sexto-Konfiguration und mit einer Zwischenwalze mit mittlerem Durchmesser (C2) in der Z.High-Konfiguration aufweist.
  29. Walzwerk nach einem der Ansprüche 27 und 28, dadurch gekennzeichnet, dass auf jeder Seite der Spannebene (P2) jeder vorstehende Teil, jeweils der obere (6) oder der untere (6') eines Hydraulikblocks (B1, B2) einen zentralen stationären Teil (62) in Bezug auf das Gerüst (A) und zwei bewegliche seitliche Teile (63, 64) aufweist, die zu beiden Seiten des zentralen Teils (62) angeordnet und axial auf dem Hydraulikblock (B1, B2) gleitend montiert sind, wobei jede Durchbiegezylindereinheit, jeweils die obere (V) oder die untere (V'), mindestens einen zentralen Zylinder (V1) aufweist, der auf dem stationären zentralen Teil (62) des vorspringenden Teils aufliegt und zu der Walzebene einwirkt, und mindestens zwei seitliche Zylinder (V3a, V3b), die jeweils auf den zwei seitlichen beweglichen Teilen (63, 64) des vorstehenden Teils (6) aufliegen und auf der entgegengesetzten Seite zu der Walzebene (P1) einwirken, und wobei jedes Einbaustück einen zentralen Teil (1) aufweist, der auf jeder Seite mit einem Auflageorgan (11) für mindestens einen zentralen Zylinder (V1) versehen ist, und mit zwei Endteilen (2a, 2b), die zu beiden Seiten des zentralen Teils (1) angefügt sind und jeweils auf jeder Seite der Spannebene mit einem Auflageorgan (21a, 22a), (21b, 22b) für einen seitlichen Zylinder (V3a, V3b) versehen sind, der auf einem entsprechenden beweglichen Teil (63, 64) des vorstehenden Teils (6) installiert ist.
  30. Walzwerk nach Anspruch 29, dadurch gekennzeichnet, dass die Auflageorgane (21a, 21b), die auf jedem Endteil (2a) eines Einbaustücks angeordnet sind, in der Höhe in Bezug auf die Achse (x'x) der Walze so versetzt sind, dass sie durch Drehen des Endteils (2a) um die Achse zwei Niveaus der Auflageorgane in Bezug auf die Achse bestimmen, jeweils ein Niveau (H1), das zu der Walzebene (P1) verschoben ist, für ein Arbeitswalzeneinbaustück in Quarto-Konfiguration, und ein Niveau (H2), das auf der entgegengesetzten Seite zu der Walzebene (P1) für ein Zwischenwalzeneinbaustück in Sexto-Konfiguration versetzt ist.
  31. Walzwerk nach einem der Ansprüche 5 bis 30, dadurch gekennzeichnet, dass man in einer Sexto-Kontiguration Arbeitswalzen und Zwischenwalzen verwendet, die jeweils einen mittleren (C2) und einen großen (C3) Durchmesser haben, die an die Höhe (h) der Fenster (A3) der zwei Ständer (A) des Gerüsts angepasst sind, und dass man Unterlagen (M, M') zwischen jedem Ende des Fensters (A3) und dem entsprechenden Einbaustück (S1, S'1) einer Stützwalze (S, S') so einfügt, dass die Höhe der Fenster (A3) für die Quarto- und die Z.High-Konfigurationen verringert wird.
  32. Walzwerk nach einem der Ansprüche 5 bis 31, dadurch gekennzeichnet, dass die Mittel (V, V') zum Anlegen der Durchbiegekräfte In Hydraulikblöcken (B1, B2) angeordnet sind, die in allen Konfigurationen eine Höhe haben, die im Wesentlichen die Summe der Durchmesser der zwei Walzen mit größerem Durchmesser (C1, C'1), die als Arbeitswalzen in der Quarto-Konfiguration verwendet werden, nicht überschreitet.
EP04717667A 2003-03-05 2004-03-05 Verfahren zum ändern der konfiguration eines walzgerüstes sowie ein zur durchführung des verfahrens geeignetes walzgerüst Expired - Lifetime EP1601474B1 (de)

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JPH01154803A (ja) * 1987-12-10 1989-06-16 Ishikawajima Harima Heavy Ind Co Ltd 多段圧延機
FR2710567B1 (fr) * 1993-09-28 1995-12-22 Clecim Sa Laminoir à déplacement axial.
FR2786415B1 (fr) * 1998-11-30 2001-02-09 Kvaerner Metals Clecim Laminoir equipe de moyens de cambrage des cylindres de travail
DE10046426A1 (de) * 2000-09-20 2002-03-28 Sms Demag Ag Kombinierter Antrieb für ein Vierwalzen- bzw. Sechswalzengerüst sowie Betriebsverfahren hierfür
WO2002047837A1 (fr) * 2000-12-13 2002-06-20 Hitachi, Ltd. Materiel et procede de remplacement d'un ensemble cylindres

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ATE367215T1 (de) 2007-08-15
DE602004007631D1 (de) 2007-08-30
RU2005130760A (ru) 2006-07-27
FR2851942A1 (fr) 2004-09-10
FR2851942B1 (fr) 2006-04-28
BRPI0408106A8 (pt) 2016-11-08
EP1601474A2 (de) 2005-12-07
US7302820B2 (en) 2007-12-04
WO2004080621A3 (fr) 2004-10-28
CN1780702B (zh) 2010-05-26
DE602004007631T2 (de) 2008-04-10
ES2290680T3 (es) 2008-02-16
US20060196243A1 (en) 2006-09-07
WO2004080621A2 (fr) 2004-09-23
BRPI0408106B1 (pt) 2019-08-06
RU2333808C2 (ru) 2008-09-20
CN1780702A (zh) 2006-05-31
BRPI0408106A (pt) 2006-03-01

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