EP1005923B1 - Walzwerk mit Mitteln zur Biegung der Arbeitswalzen - Google Patents

Walzwerk mit Mitteln zur Biegung der Arbeitswalzen Download PDF

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Publication number
EP1005923B1
EP1005923B1 EP99402958A EP99402958A EP1005923B1 EP 1005923 B1 EP1005923 B1 EP 1005923B1 EP 99402958 A EP99402958 A EP 99402958A EP 99402958 A EP99402958 A EP 99402958A EP 1005923 B1 EP1005923 B1 EP 1005923B1
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EP
European Patent Office
Prior art keywords
chock
cylinders
resting
chocks
plane
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Expired - Lifetime
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EP99402958A
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English (en)
French (fr)
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EP1005923A1 (de
Inventor
Germain Le Viavant
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Clecim SAS
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Kvaerner Metals Clecim SA
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Publication of EP1005923A1 publication Critical patent/EP1005923A1/de
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    • 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
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
    • B21B31/203—Balancing rolls

Definitions

  • Rolling metal products in the form of tape is normally carried out in a train of rolling mills each consisting of a cage comprising two support columns spread apart and connected by sleepers, between which is mounted a set of superimposed cylinders having parallel axes and placed substantially in the same clamping plane substantially perpendicular to the direction of displacement of the product.
  • the so-called "quarto" rolling mills therefore have four superimposed cylinders, respectively two associated working cylinders, respectively, with two more supporting cylinders large diameter.
  • cylinders intermediaries are interposed between each cylinder and the corresponding support cylinder.
  • the cylinders are supported one on the others along substantially support lines parallel, and directed along a generator whose the profile, normally straight, depends on the forces applied and resistance of the cylinders.
  • the clamping force is applied by screws or cylinders interposed between the cage and the support cylinder shaft ends upper, the lower support cylinder taking support by these ends directly on the cage. AT apart from the latter, the other cylinders must therefore ability to move relative to the cage and at this effect, are carried by mounted support members sliding vertically in two windows in the two columns of the cage.
  • Clamping means such as screws or jacks, leaning on the cage, exert a vertical force in the direction of tightening of the cylinders for the rolling of the product passing between the cylinders of job.
  • each cylinder is mounted rotatable, around its axis, on bearings carried by two support members called chocks and this one are slidably mounted, parallel to the plane of clamping passing through the axes of the working cylinders, each between two flat guide faces provided respectively on either side of said plane of clamping on both sides of the window corresponding from the cage.
  • the level of support chocks may vary and, to ensure precise control of the profile of the working cylinders, it is preferable that the cambering cylinders bear directly on the cage.
  • positive camber cylinders and negative are housed in support parts projecting inward from the window and provided with guide faces at their ends lateral of the chock, the ears thereof extending outwardly between said parts in projection.
  • each support block usually has three projecting parts, respectively a central part placed at the level of the rolling plan, in which the cylinders are housed of positive bending of the two chocks and two parts support placed, respectively, above and in below the rolling plane and in which are housed the negative camber cylinders of both cylinders, respectively upper and lower.
  • each support block therefore has an E shape comprising, on either side of the projecting part central, two notches in which extend, respectively, the ears of the two chocks. These notches must therefore have a sufficient height to allow the relative levels to be varied cylinders.
  • the rolls of a rolling mill and, in particular, the working cylinders wear enough quickly and their diameter can therefore vary, as well that, of course, the relative positions of cylinders applied to each other.
  • the figure 1 shows, for example, the relative positions of the new and used cylinders, respectively on the right and to the left of the clamping plane.
  • the heights of the guide faces and the strokes of the cylinders should be increased depending on the range wear to allow height adjustment necessary cylinders.
  • the central part of the support blocks in which the cylinders are placed positive camber, as well as the notches in which extend the ears of the chocks, must have each a minimum height to ensure the necessary stroke.
  • the central part of the support block can be removed the cylinders positive camber of a chock that can be placed next to the cylinders of negative arching of the other chock.
  • the rolling plan should normally be placed at a substantially constant level and one is brought like the shows, Figure 1, to perform, respectively for the upper working cylinder and for working cylinder lower, special chocks having guide faces side extended downward to provide guidance correct over all the necessary height, taking into account the wear range.
  • the camber cylinders are placed in two diagonal planes which intersect along a vertical axis of symmetry. he as a result that the forces applied to each chock, respectively to left and right of the clamping plane passing through the axes of the cylinders work are axially offset on either side of the median plane of the chock, orthogonal to the axis of the cylinder. Such an axial offset can present disadvantages for the centering of the rolling effort.
  • the object of the invention is therefore to solve the whole of these problems avoiding the drawbacks mentioned upper.
  • the invention therefore generally applies to a rolling mill comprising, inside a holding cage having two spaced apart columns, a set of cylinders comprising at least two working cylinders, mounted rotary, around axes substantially parallel to a rolling plane, each on two chocks strung respectively in windows of the two columns of the cage and sliding mounted along fixed guide faces parallel to a clamping plane, each by means of lateral holding faces, the rolling mill being equipped with means for applying bending forces on the chocks from the two working rolls comprising, for each column of the cage, a set of cylinders arranged on either side of the clamping plane and acting respectively on support ears of each chock extending projecting, respectively, relative to the lateral retaining faces of the chock and each having an internal bearing face facing the plane of rolling and an external bearing face turned to the opposite side, each set bending cylinders comprising at least two positive bending cylinders bearing, respectively, on the internal faces of the ears of the two chocks and at least two negative cambering cylinders supported, respectively on the external faces
  • the ear a first working chock placed on a first side of the plane of rolling comprises a single support part centered on a median plane of said chock perpendicular to the axis of the cylinder and two free spaces, arranged on either side of said single support part and the ear of the second chock placed on the second side of the rolling plane has only one free space centered on the median plane and two support parts arranged on either side of said single space, each set of jacks comprising, on the one hand a positive camber cylinder and a negative camber cylinder supported respectively on the internal and external faces of the single support part of the ear of the first working chock and, on the other hand, two cylinders of positive cambering and two negative cambering cylinders arranged on both sides of the median plane and bearing respectively on the internal faces and external of the two support parts of the second working chock.
  • the fixed elements of the cylinders of bending, respectively positive and negative of the two chocks are mounted respectively in parts in projection of two support blocks respectively fixed on each column of the cage, on either side of the plane of tightening, each support block being symmetrical about in the rolling plane and comprising, between said parts in projection, a unique central notch in which extend the support ears of the chocks of the two cylinders, respectively upper and lower, and each chock is provided, on each side of the clamping plane, with a single lateral holding face extending on the side opposite to rolling plane with respect to the support ear and sliding along a fixed guide face arranged at the end of a corresponding projecting part of the block of support.
  • each chocks are offset towards the rolling plane with respect to the axis of the corresponding cylinder so that the faces internal support for positive camber cylinders are almost in contact with each other in the wear position maximum of the working cylinder.
  • the two ears of a first working choke extending, respectively, on either side of the clamping plane comprise, one, a support part one framed by two free spaces and the other, a single framed free space by two support parts, the arrangement being reversed for the ears of the second work chock.
  • the chocks of the working cylinders and the support blocks of all the cages are identical.
  • the invention applies to new rolling mill stands but it is particularly advantageous for the modernization of existing cages, for which the dimensional constraints of columns and chocks of existing support cylinders can complicate or prevent installing a design arching system classic.
  • Figure 1 there is shown in section transverse, the classic layout of a rolling mill type quarto comprising, inside a cage having two spread columns 1, two working cylinders, respectively upper 2 and lower 2 ', which take support, respectively, on two support cylinders, upper 21 and lower 21 'and define an air gap for the passage of an M strip to be laminated, passing along a rolling plan P1.
  • Figure 1 shows the central part of a window of a column 1 of the cage, in cross section at the axis of the cylinders, the second column being identical.
  • Each working cylinder 2, 2 ' is rotatably mounted, at its ends, on trunnions turning in bearings housed in chocks 4, 4 '.
  • support cylinders 21, 21 ' are carried by chocks 41, 41 '.
  • the axes of the cylinders are parallel and must be held substantially in a clamping plane P2 perpendicular to the rolling plane P1. Usually the latter is horizontal, the plane of clamp P2 being substantially vertical.
  • the cylinders are tight, and their levels may vary depending on their wear.
  • the half view on the right represents the relative positions of the new cylinders and the half view left represents the positions of used cylinders smaller diameter.
  • the chocks 41, 41 'of the support cylinders 21, 21 ' which have a large diameter, are mounted sliding along guide faces 11a, 11b formed directly along the two uprights 1a, 1b which frame window 10 of column 1.
  • the chocks 4, 4 ′ of the cylinders of work 2, 2 'smaller diameter are less wide that the chocks 41, 41 ′ of the support cylinders 21, 21 'and their guide faces must therefore be less apart. Therefore, according to a provision conventional, the guide faces 12a, 12b of the chocks are arranged on the faces opposite two machined blocks 3a, 3b which are mounted respectively on the two uprights 1a, 1b of the column and extend inwardly projecting from window 10.
  • the rolling plan P1 is maintained at a level substantially constant, especially when the band to laminate M passes successively in several rolling mills operating in tandem.
  • Level of upper support cylinder 2 is adjusted by clamping means not shown, such as screws or cylinders, which are mounted at the upper part of the two columns 1 of the cage for build on chocks 41 and which allow, in addition, to apply the necessary rolling force thickness reduction.
  • the cylinders in especially the working cylinders, must be periodically removed from the cage for maintenance or replacement and, for this, their chocks roll or slide on fixed guide rails.
  • These rails (not shown in the figure) are mounted on the cage columns and placed at a constant level for which all the cylinders are spread apart others.
  • To place the cylinders in the position replacement lower the support cylinder lower 21 'to its lower level by means of lower wedges and the cylinder is raised higher support 21 at its higher level through clamping means and possibly cylinders auxiliaries 15 mounted in the support blocks 3a, 3b and bearing on the chocks 41 of the cylinder of upper support 21. In service, these cylinders 15 also serve to balance the weight of cylinder 21 and its chocks 41.
  • the supporting cylinders being thus spaced of a large opening, the relative levels of working cylinders 2, 2 'can be adjusted by cylinders housed in the support blocks 3a, 3b.
  • these jacks also serve, in service, to apply bending efforts, respectively positive or negative, on chocks working cylinders.
  • Figure 1 shows the most classic in which each chock 4, 4 'is associated with two sets of cylinders placed respectively on either side of the clamping plane P2 and comprising, for each working cylinder, respectively upper 2 or lower 2 ', at least a positive cambering cylinder 5, 5 'and at least one 6,6 'negative camber cylinder.
  • these cylinders act on support parts provided on either side of each chocks and which form opposite ears 7, 7 ' each projecting from the side corresponding side 42 of the chock.
  • each support block 3 has a E-shape comprising three holding parts in projection, respectively an upper part 32, a central part 33 and a lower part 32 ', which frame two notches, respectively upper 31 and lower 31 ′, into which the ears 7, 7 'of the working chocks, respectively upper 4 and lower 4 '.
  • Camber cylinders resting on the ears of the chock are housed in these three holding parts whose ends facing each other form the guide faces 12a, 12b the along which the lateral sides 42a slide, 42b, 42'a, 42'b, of the two chocks 4, 4 '.
  • the two chocks 4, 4 ′ come practically into contact one from the other.
  • the dimensioning of the different parts support blocks 3 and working chocks must therefore take the wear range into account, especially when you want to keep the rolling plan at a level constant.
  • the underside 43 of the chock 4 is located below the rolling plane in the wear position Max.
  • each block of support 3a, 3b has a single notch 35a, 35b which extends on either side of the rolling plane P1, the part protruding center 33 of the known arrangement being, therefore, deleted.
  • each support block has a section in C and not in E.
  • each support block 3 the camber cylinders must all be housed in two support parts, respectively upper 32 and lower 32 'framing a central notch 35.
  • each camber cylinder positive 5 must be placed next to the body 61 'of the actuator 6 'negative camber, in the lower projection 32 ', and the rod 52 of the jack 5 must cross the ear 7 'of the lower chock 4' to pass to the other side of the rolling plane P1 and lean on the internal face 71 of the ear 7 of the top working chock 4.
  • the jacks camber are placed next to each other and centered, respectively in two planes Pa, Pb parallel to the clamping plane P2 and spaced apart symmetrically on either side of it.
  • FIG 3 schematically shows a mode of realization of the ears of the chocks allowing to get this result.
  • Each 7 'ear of the chock therefore has a stepped profile comprising a part 73 ′ for supporting the cambering cylinder negative 6 'which covers only part of the length of the chock, in the longitudinal direction of the axis of the cylinder, so as to leave a free space 74 'allowing passage of the cylinder rod 5 of positive camber.
  • the ear 7'a of the lower chock 4 'lying at left of clamping plane P2 has a stepped profile comprising a portion 73'a for supporting the actuator 6'a negative camber which is placed in front of the plane median P3 of the bearings, and extends at most over the half the length (L) of the chock, so that leave a free space 74 'placed behind the same median plane P3, for the passage of the rod of the jack 5a positive camber of the upper chock 4.
  • the ear 7'b of the lower chock 4 'placed to the right of the clamping plane P2 has a reverse stepped profile comprising a part 73'b for supporting the cambering cylinder negative 6'b, which is placed behind the median plane P3 and leaves a free space 74'b placed in front of the same plane median P3 for the passage of the cylinder rod 5b for bending positive of the upper chock 4.
  • the bodies 51, 61 of the different cylinders which are single acting, can be made simply bores in opposite angles of the corresponding projecting parts 32, 32 ′, of the blocks of support 3.
  • Figure 6, which is a cross section, by a plane passing through the axes of the cylinders, of the support block 3a placed to the left of the clamping plane P1 in FIG. 5, shows that the lower holding part 32 ′ of said block 3a has two bores placed side by side, respectively 61 'forming the body of the negative camber cylinder 6' and 51 forming the body of the cylinder 5 for positive cambering of the chock superior 4.
  • the cylinders of positive camber 5a, 5b of the upper working cylinder 2 are thus placed in two opposite angles parts of lower support 32'a, 32'b of the two support blocks 3a, 3b and are therefore centered on a first diagonal plane Q1 inclined at a non-right angle to the clamping plane P2. It is the same with the free spaces 74'a, 74'b provided in the ears 7'a, 7'b of the lower chock 4 '.
  • the negative camber cylinders 6'a, 6'b of the cylinder lower work 2 ' are placed on either side of the plane P2, in the other two angles of the holding parts 32'a, 32'b of the two support blocks 3a, 3b and centered in a second diagonal plane Q2, as well as the support parts 73'a, 73'b of the two ears 7'a, 7'b.
  • Figure 4 which shows schematically, in perspective, the set of two chocks 4, 4 ', we see that the layout is reversed for the working chock upper 4 and upper holding parts 32a, 32b support blocks 3a, 3b; the positive camber cylinders 5'a, 5'b of the lower cylinder 2 'are centered in the second diagonal plane Q2 while the camber cylinders negative 6a, 6b of the upper working cylinder 2 are centered in the first diagonal plane Q1.
  • the entire arrangement therefore includes an axis central symmetry 10 placed at the intersection of the plane of clamping P2 with the median plane P3 of the chocks and by which pass the two diagonal planes Q1 and Q2.
  • camber cylinders acting on two opposite ears of a chock are offset axially on either side of the median plane P3
  • the action of camber exerted on the chock remains well centered by relation to turnover, in the positive direction as in the negative sense.
  • the arrangement shown in the figures is particularly simple and can be easily adapted to an existing cage.
  • the bending effort could be applied, on each side of chock, by a greater number of cylinders arranged so as to ensure the centering of the result of the efforts applied.
  • FIG. 7 shows an arrangement according to the invention in which the bending force is applied on one side of the chock by a single jack and on the other by two jacks supplied in parallel.
  • each ear of a chock has a stepped profile having two free spaces on either side of a support part or else two support parts on either side of a free space.
  • the ear 7'a of the lower working chock 4 ' placed to the left of the clamping plane P2, comprises a support part 73'a which is centered on the median plane P3 of the bearings, on which take support the positive 5'a and negative 6'a camber cylinders.
  • This support portion 73'a is framed by two free spaces 74'a 1 , 74'a 2 through which pass the rods of two jacks 5a 1 , 5a 2 of positive bending of the upper working cylinder which are supplied in parallel.
  • the ear 7'b comprises two support parts 73'b 1 , 73'b 2 symmetrically spaced apart on either side of the median plane P3, on which two pairs of cylinders operating in parallel, respectively 5'b 1 , 5'b 2 of positive bending and 6'b 1 , 6'b 2 of negative bending of the lower cylinder 2 '. Between these two support parts 73'b 1 , 73'b 2 is placed a central recess 74'b for the passage of the rod of the jack 5b for positive bending of the upper chock 4.
  • the support ears 7a, 7b of the upper working chock 7 shown in phantom in Figure 7 are arranged in reverse and therefore comprise, on the left, two parts 73a 1 , 73a 2 , for supporting the two jacks of positive camber 5a 1 , 5a 2 and, on the right, a support part 73b framed by two free spaces 73b 1 , 73b 2 for passage of the rods of the jacks 5'b 1 , 5'b 2 of positive camber of the lower cylinder 2 '.
  • the two chocks 4, 4 ′ penetrate into the same notch central 35 of each support block 3, the faces of lateral support 42, 42 'of each chock 4, 4' extend on one side of the ear 7, 7 'of so as to slide along the guide faces 36, 36 ' formed at the ends of the holding parts in projection 32, 32 '. Therefore, the two chocks can be symmetrical with respect to the rolling plane P1. As a result, chocks can be used identical for the two working cylinders, the chock being simply turned 180 ° according to whether it is placed above or below the plane of rolling P1.
  • each holding part respectively upper 32 or lower 32 ', from a support block 3 is determined based on the stroke of the cylinder positive camber which itself depends on the length that we have to give to the cylinder rod to make it lean on the ear of the chock placed from the other side of the rolling plane P1, the cylinders of negative camber with a lower stroke.
  • the invention has the advantage of allowing a reduction in the overall height of each block of support compared to usual arrangements since we remove the protruding central part which was previously necessary to house the positive camber cylinders. This results in a decrease in height of the area that should remain available between chocks 41, 41 'of the cylinders support to allow the implantation of the blocks of support. This provision is particularly interesting in the case of the modernization of a existing rolling stand because it allows facilitate the installation of the cambering system positive and negative between the support cylinders without notable modification of the cage columns.
  • the internal faces 71a, 71b of the two ears 7a, 7b are then placed substantially at the level of the internal face 43 of chock 4 facing the rolling plane. This one is itself separated from the axis of the cylinder by a distance a little less than the smallest radius of the working cylinder 2. In this way, when the cylinders are in their maximum state of wear, the internal faces 71, 71 'of the ears 7, 7' of the two chocks 4, 4 'being almost in contact with one of the other, in the rolling plane P1, taking into account the necessary adjustments for negative bending.
  • the number of guide faces fixed and lateral chock holding faces is decreased.
  • the surfaces of slip must be fitted with attachments made of a material with a coefficient of friction suitable for use and which constitute parts wear.
  • the decrease in their number through the adoption of all the arrangements according to the invention, reduces the cost of installation as well as production costs by simplifying operations maintenance and by reducing the necessary duration of interventions.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
  • Control Of Metal Rolling (AREA)
  • Preliminary Treatment Of Fibers (AREA)
  • Soil Working Implements (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Shaping Of Tube Ends By Bending Or Straightening (AREA)

Claims (5)

  1. Walzwerk, umfassend im Inneren eines Haltegestells, das zwei beabstandete Ständer (1a, 1b) hat, einen Aufbau von Zylindern, der wenigstens zwei Arbeitszylinder (2, 2') hat, die drehbar um Achsen montiert sind, welche im wesentlichen parallel zu einer Walzebene (P1) sind, wobei jeder auf zwei Einbauteilen, die jeweils in Fenstern (10) der beiden Ständer des Gestells aufgereiht und verschiebbar längs fester Führungsflächen (12), die parallel zu einer Druck- bzw. Pressungsebene (P2) sind, jedes mit Hilfe von seitlichen Halteflächen (42), montiert sind, wobei das Walzwerk mit Mitteln für das Anlegen von Biegungskräften an die Einbauteile (4, 4') der beiden Arbeitszylinder (2, 2') ausgerüstet ist, umfassend für jeden Ständer (1a, 1b) des Gestells einen Aufbau von Stellantrieben, die beiderseits der Druck- bzw. Pressungsebene (P2) angeordnet sind und jeweils auf Auflageohren (7a, 7'a, 7b, 7'b) jedes Einbauteils (4, 4') einwirken, die sich jeweils mit Bezug auf die seitlichen Halteflächen (42) des Einbauteils überhängend bzw. vorspringend erstrecken und von denen jedes eine innere Auflagefläche (71) hat, die zur der Walzebene (P1) hin gewandt ist, und eine äußere Auflagefläche (72), die nach der entgegengesetzten Seite gewandt ist, wobei jeder Aufbau von Stellantrieben für die Durchbiegung wenigstens zwei Stellantriebe (5, 5') für die positive Durchbiegung umfasst, die jeweils auf den inneren Flächen (71, 71') der Ohren (7, 7') der beiden Einbauteile (4, 4') zur Auflage kommen, und wenigstens zwei Stellantriebe (6, 6') für die negative Durchbiegung, welche jeweils auf den äußeren Flächen (72, 72') der Ohren (7, 7') der beiden Einbauteile (4, 4') zur Auflage kommen, ein Walzwerk, in welchem jedes Ohr (7') eines ersten Einbauteils (4') ein gestuftes Profil mit wenigstens einem Auflageteil (73'a) und wenigstens einem freien Raum (74'a) für den Durchgang des beweglichen Elements (52a) von wenigstens einem Stellantrieb (5a) für die positive Durchbiegung des zweiten Einbauteils (4) aufweist, wobei die gestuften Profile der Ohren (7a, 7'a) der beiden Einbauteile (4, 4') jeweils derart umgekehrt sind, dass ein Auflageteil (73'a) eines ersten Einbauteils (4') einem freien Raum (74a) des zweiten Einbauteils (4) entspricht,
       dadurch gekennzeichnet, dass auf jeder Seite der Druck- bzw. Pressungsebene (P2), das Ohr (7'a) eines ersten Arbeitseinbauteils (4'), welches auf einer ersten Seite der Walzebene (P1) platziert ist, einen einzigen Auflageteil (73'a) hat, der auf eine Mittelebene (P3) des genannten Einbauteils (4') zentriert ist, die senkrecht zu der Achse des Zylinders ist, und zwei freie Räume (74'a1, 74'a2), die beiderseits des genannten einzigen Auflageteils (73'a) angeordnet sind, und das Ohr (7a) des zweiten Einbauteils (4), das auf der zweiten Seite der Walzebene (P1) platziert ist, einen einzigen freien Raum (74a) hat, der auf die Mittelebene (P3) zentriert ist, und zwei Auflageteile (73a, 73b), die beiderseits des genannten einzigen Raums (74a) angeordnet sind, wobei jeder Satz von Stellantrieben einerseits einen Stellantrieb (5'a) für die positive Durchbiegung und einen Stellantrieb (6'a) für die negative Durchbiegung umfasst, die auf der inneren bzw. äußeren Fläche des einzigen Auflageteils (73'a) des Ohrs (7'a) des ersten Arbeitseinbauteils (4') zur Anlage kommen, und andererseits zwei Stellantriebe (5a1, 5a2) für die positive Durchbiegung und zwei Stellantriebe (6a1, 6a2) für die negative Durchbiegung, die beiderseits der Mittelebene (P3) angeordnet sind und auf der inneren bzw. äußeren Fläche der beiden Auflageteile (73a, 73b) des zweiten Arbeitseinbauteils (4) zur Anlage kommen.
  2. Walzwerk gemäß dem Anspruch 1, dadurch gekennzeichnet, dass die festen Elemente (51, 51', 61, 61') der Stellantriebe für die positive (5, 5') bzw. negative (6, 6') Durchbiegung der beiden Einbauteile (4, 4') jeweils in den vorspringenden Teilen (32, 32') der beiden Halteblöcke (3a, 3b) montiert sind, die jeweils auf jedem Ständer (1a, 1b) des Gestells (1) beiderseits der Druck- bzw. Pressungsebene (P2) befestigt sind, und dass jeder Halteblock (3a, 3b) symmetrisch mit Bezug auf die Walzebene (P1) ist und zwischen den genannten vorspringenden Teilen (32, 32') einen einzigen zentralen Ausschnitt (35a, 35b) umfasst, in welchem sich die Auflageohren (7a, 7'a) (7b, 7'b) der Einbauteile (4, 4') der beiden Zylinder, des oberen (2) bzw. unteren (2') erstrecken, wobei jedes Einbauteil (4, 4') auf jeder Seite der Druck- bzw. Pressungsebene (P2) mit einer einzigen seitlichen Haltefläche (42) ausgerüstet ist, die sich auf der Seite, die der Walzebene (P1) mit Bezug auf das Auflageohr (7) entgegengesetzt ist, erstreckt und sich längs einer festen Führungsfläche (12) verschiebt, welche am Ende eines entsprechenden vorspringenden Teils (32) des Halteblocks (3) angeordnet ist.
  3. Walzwerk gemäß dem Anspruch 2, dadurch gekennzeichnet, dass die Auflageohren (7, 7') jedes Einbauteils (4, 4') zur Walzebene (P1) hin mit Bezug auf die Achse des entsprechenden Zylinders derart versetzt sind, dass sich die inneren Anlageflächen (71, 71') der Stellantriebe (5, 5') für die positive Durchbiegung nahezu in Kontakt miteinander in der Position maximalen Verschleißes der Arbeitszylinder (2, 2') befinden.
  4. Walzwerk gemäß einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass sich die beiden Ohren (7'a, 7'b) eines ersten Arbeitseinbauteils (4') jeweils beiderseits der Druck- bzw. Pressungsebene (P2) erstrecken, wobei das eine einen einzigen Auflageteil (73'a) umfasst, der durch zwei freie Räume (74'a1, 74'a2) eingerahmt ist, und der andere einen einzigen freien Raum (74'b), der durch zwei Auflageteile (73'b1, 73'b2) eingerahmt ist, wobei die Anordnung für die Ohren (7a, 7b) des zweiten Arbeitseinbauteils umgekehrt ist.
  5. Walzwerk gemäß einem der vorhergehenden Ansprüche, anwendbar auf eine Walzanlage, die wenigstens zwei in Tandem funktionierende Gestelle aufweist, dadurch gekennzeichnet, dass die Einbauteile (4, 4') der Arbeitszylinder (2, 2') und die Halteblöcke (3) aller Gestelle identisch sind.
EP99402958A 1998-11-30 1999-11-26 Walzwerk mit Mitteln zur Biegung der Arbeitswalzen Expired - Lifetime EP1005923B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR9815077A FR2786415B1 (fr) 1998-11-30 1998-11-30 Laminoir equipe de moyens de cambrage des cylindres de travail
FR9815077 1998-11-30

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EP1005923A1 EP1005923A1 (de) 2000-06-07
EP1005923B1 true EP1005923B1 (de) 2003-02-12

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EP (1) EP1005923B1 (de)
AT (1) ATE232425T1 (de)
DE (1) DE69905332T2 (de)
ES (1) ES2189366T3 (de)
FR (1) FR2786415B1 (de)

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US6073474A (en) * 1999-06-24 2000-06-13 Danieli United, A Divison Of Danieli Corporation "C" block roll bending
DE10150690A1 (de) * 2001-10-17 2003-04-30 Sms Demag Ag Walzvorrichtung
FR2851942B1 (fr) * 2003-03-05 2006-04-28 Procede de changement de configuration d'un laminoir et laminoir perfectionne pour la mise en oeuvre du procede
EP1843414A4 (de) * 2005-01-25 2008-05-14 Ihi Corp Einrichtung zur bildung einer batterieelektrodenplatte
CN106670236B (zh) * 2017-03-21 2018-07-13 北京京诚之星科技开发有限公司 板带轧机双重导向工作辊弯辊及平衡装置
JP6979437B2 (ja) * 2019-10-25 2021-12-15 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ株式会社 圧延機および圧延方法
CN113950383B (zh) * 2019-10-25 2023-08-29 普锐特冶金技术日本有限公司 轧机
JP2023510090A (ja) * 2019-12-11 2023-03-13 エス・エム・エス・グループ・ゲゼルシャフト・ミト・ベシュレンクテル・ハフツング 熱間圧延機のため、および、金属の平板製品の製造のための熱間圧延スタンド、熱間圧延機、並びに、熱間圧延機の作動のための方法

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5666307A (en) * 1979-10-04 1981-06-04 Hitachi Ltd Rolling mill
JPS58168407A (ja) * 1982-03-31 1983-10-04 Hitachi Ltd 圧延機のロ−ルベンデイング装置
FR2613641B1 (fr) * 1987-04-09 1990-12-14 Clecim Sa Procede et installation de laminage d'un produit sous forme de bande, plus specialement une tole metallique ou un feuillard
JPH0734928B2 (ja) * 1987-06-30 1995-04-19 株式会社日立製作所 圧延機のロ−ルベンデイング装置
JPH02280910A (ja) * 1989-04-20 1990-11-16 Kawasaki Steel Corp 圧延機
DE4203189A1 (de) * 1992-02-05 1993-08-12 Achenbach Buschhuetten Gmbh Einrichtung zum ausbalancieren und durchbiegen der arbeitswalzen eines walzgeruestes
US5970771A (en) * 1998-07-10 1999-10-26 Danieli United Continuous spiral motion system for rolling mills
US6073474A (en) * 1999-06-24 2000-06-13 Danieli United, A Divison Of Danieli Corporation "C" block roll bending

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ATE232425T1 (de) 2003-02-15
ES2189366T3 (es) 2003-07-01
EP1005923A1 (de) 2000-06-07
US6244090B1 (en) 2001-06-12
DE69905332T2 (de) 2003-10-23
FR2786415B1 (fr) 2001-02-09
FR2786415A1 (fr) 2000-06-02
DE69905332D1 (de) 2003-03-20

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