EP0283342B2 - Walzgerüst mit axial verschiebbaren Walzen und Verfahren zum Steuern des Walzenprofils - Google Patents

Walzgerüst mit axial verschiebbaren Walzen und Verfahren zum Steuern des Walzenprofils Download PDF

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Publication number
EP0283342B2
EP0283342B2 EP88400372A EP88400372A EP0283342B2 EP 0283342 B2 EP0283342 B2 EP 0283342B2 EP 88400372 A EP88400372 A EP 88400372A EP 88400372 A EP88400372 A EP 88400372A EP 0283342 B2 EP0283342 B2 EP 0283342B2
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EP
European Patent Office
Prior art keywords
plane
bending
rolling mill
jacks
chock
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EP88400372A
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English (en)
French (fr)
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EP0283342B1 (de
EP0283342A1 (de
Inventor
Jacques Gérard Giacomoni
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KVAERNER CLECIM
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Individual
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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
    • B21B31/16—Adjusting or positioning rolls
    • B21B31/18—Adjusting or positioning rolls by moving rolls axially
    • 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
    • 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
    • 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

  • the invention relates to a rolling mill with axially displaceable rollers and also covers a process for adjusting the profile and distributing wear of the rolls in such a rolling mill.
  • a rolling mill comprises, inside a support cage, at least two working rolls resting, in a clamping plane, on at least two support rolls.
  • the cylinders are carried at their two ends by means of bearings, in chocks mounted mobile, parallel to the clamping plane, in windows provided on each upright of the support cage, each chock being provided with two lateral guide faces. sliding along corresponding sliding faces formed on the amount of the cage on either side of the chock.
  • a working or bending of the working rolls and possibly of the intermediate rolls is carried out by means of bending devices acting on the chocks of the corresponding cylinder.
  • the bending device consists, for each chock, of two sets of jacks placed symmetrically on either side of the chock.
  • each support part of the chock rests on two cylinders spaced in the axial direction symmetrically on either side of the median plane of the chock bearings so that the bending force is well distributed on the bearings.
  • the rolling mill stand is symmetrical with respect to a median plane perpendicular to the clamping plane and which corresponds to the median plane of the rolled product. Normally the cylinders are therefore centered on this plane with respect to which the chocks are arranged symmetrically.
  • the bending of the working rolls also ensures a balancing effect between the rolls which it is useful to maintain during the axial adjustment even when the rolling force is eliminated.
  • the subject of the invention is a device allowing axial displacement of the cylinders without ceasing to exert the bending effort.
  • Document DE-A-3.331.055 describes a rolling mill according to the preamble of claim 1 in its version for the states DE, BE, GB and IT. in which each cambering cylinder bearing on an ear of the chock is housed in a drawer-shaped part, slidingly mounted, parallel to the axis of the cylinder, inside the support block, and secured to the chock so as to follow the axial displacements thereof. Therefore, the cylinder always remains well centered relative to the chock.
  • a rolling mill with axially displaceable rollers comprising, inside a support cage, at least two working rolls based on a clamping plane P1, on at least two support cylinders and the ends of which are carried, by means of bearings, in chocks slidably mounted in the support cage, parallel to the clamping plane P1, at least one of the working rolls being associated, on the one hand, with means for moving said cylinder along its axis on either side of a position for centering the working rolls on the median plane P2 of the cage and on the other hand means for bending said cylinder comprising, for each chock and on each side of the clamping plane, at at least one cambering cylinder placed inside a support block secured to the cage and acting on a corresponding support part of the chock by means of a sliding part comprising at least one part of support extending above each cylinder and at least one foot-shaped guide portion, sliding vertically in a machining operation
  • the invention relates to a new device making it possible to carry out at the same time the bending and the axial displacement of the working rolls or the intermediate rolls without appreciably modifying the constitution of the rolling mill.
  • the invention makes it possible, in fact, to use fixed cambering cylinders housed, in a conventional manner, inside the support blocks while avoiding high friction between guide surfaces liable to disturb the vertical adjustment movements of the chocks .
  • the invention therefore applies to a rolling mill with axially displaceable rollers comprising, inside a support cage at least two working rolls resting on a clamping plane, on at least two support rolls and the ends of which are carried, by means of bearings, in chocks slidably mounted in the support cage, at least one of the working cylinders being associated, on the one hand, with means for moving said cylinder along of its axis on either side of a position for centering the working rolls on the median plane of the cage, and on the other hand, to means for bending said roll comprising, for each chock and on each side of the clamping plane, at least one cambering cylinder placed inside a support block secured to the cage and acting on a corresponding support part of the chock.
  • the cambering cylinder or cylinders bear on the corresponding part of the chock by means of a sliding part comprising at least one bearing part extending above each cylinder and at least one foot-shaped guide part, slidingly mounted vertically in a machining carried out inside the support block and on which is formed, on the side opposite to the camber cylinders, a flat and smooth face parallel to the axis of the cylinder, on which is supported, with the possibility of sliding, the corresponding support part of the chock.
  • the cambering effort is exerted by means of fixed jacks bearing at each end, on one side on the support block secured to the cage and the other on a part allowing the sliding of the chock during axial displacements, this part being slidably mounted on the support block in the direction of application of the bending effort and provided with embedding means to resist the effects of overturning in the direction of axial displacement of the cylinders.
  • the sliding part interposed between the camber or cylinders and on which the chock can slide is also provided with at least one guide foot sliding in a bore of the support block.
  • this bore has a circular section, the guide foot being a simple round rod.
  • the present invention allows, on the other hand, to make a distinction between two guide planes, the sliding part being guided between two pairs of guide faces, respectively parallel and perpendicular to the clamping plane.
  • the guidance thus produced makes it possible to resist the overturning forces resulting from the misalignment of the support parts of the chock with respect to the sliding part during axial displacements and, having regard to the length of the guide foot, the latter takes place with low friction and not penalizing vertical movements.
  • the two guide faces perpendicular to the clamping plane constitute two opposite faces of the machining between which the guide foot of the sliding part can slide and the two guide faces parallel to the clamping plane constitute two opposite faces of a transverse recess formed in the support block, between which a part of the sliding part can slide.
  • these two guide faces parallel to the clamping plane are symmetrically spaced on either side of the plane passing through the axes of the cambering cylinders and the support part of the chock is itself centered in the same plane in which thus pass all the forces applied by the bending.
  • the machining carried out in the support block comprises an enlarged external part passing over the two camber cylinders in which the external part of the T-shaped sliding part is guided, on which the chock rests on one side and, on the other, the camber cylinders and a internal part forming a central well in which the guide foot of the sliding part is guided.
  • the embedding effect of the guide foot makes it possible at the same time to carry out the axial displacement and the bending of the working rolls by opposing the overturning moment which results from the offset of the median plane of the bearing with respect to the plane of symmetry of the two pairs of bending cylinders.
  • this offset becomes too large, it results in friction which can oppose the sliding of the sliding part.
  • the offset of the working cylinder with respect to the centering position on the median plane of the product is measured at all times and the individual pressure exerted by each cylinder is permanently adjusted for each offset. measured so that, for each sliding part, the moment resulting from the sum of the moments of each cambering cylinder and that of the reaction of the chock is zero.
  • the two chocks of each movable cylinder being each associated with two symmetrical sets of camber cylinders, arranged on either side of the rolling plane, the jacks placed respectively, in each of the assemblies, in the same relative positions relative to the median plane of their respective bearings are connected in parallel to the same branch of a common circuit for supplying pressurized fluid comprising as many branches as there are jacks in each assembly, each branch being provided with an adjustment means individual fluid pressure with equal flow maintenance in all branches.
  • the means for individual adjustment of the pressures in the jacks comprise, on each branch of the supply circuit, a servo-valve controlled by a means of calculating the corrections to be made to the pressures as a function of the offset measured and displayed on the calculation means and respective positions of the cylinders supplied by the branch in question.
  • each chock can be associated with positive bending means each comprising at least two jacks.
  • positive bending means each comprising at least two jacks.
  • These sets of cylinders are formed in hydraulic blocks placed on either side of the clamping plane, in the windows of the cage; each block consists of a massive support piece comprising a central part machined to receive the T-shaped pieces on which the support ears of the chock rest, these being each provided with a face of continuous sliding parallel to the sliding axis.
  • Figure 1 shows schematically, in perspective, the arrangement of a quarto rolling mill with movable cylinders.
  • Figure 2 is a partial top view of a working cylinder and its displacement means.
  • Figure 3 is a partial view of the rolling mill cage showing the two working rolls and the bending devices, in section through a plane parallel to the rolling plane and passing through the axes of a set of bending cylinders in one embodiment using continuous beams passing through the cage and having T-shaped ends
  • Figure 4 is a partial view of the bending devices, in section through a plane parallel to the rolling plane and passing through the axes of a set of bending cylinders in the embodiment using separate intermediate parts in the shape of a T.
  • Figure 5 shows the particular section of these parts in section through a transverse plane, the chocks being spaced from one another.
  • FIG. 6 is a view of the chocks of the two working rolls and of the bending devices in section through a plane perpendicular to the rolling plane and passing through the axes of the bending cylinders.
  • FIG. 7 gives a hydraulic diagram of the balancing device in a more improved embodiment.
  • the rolled product 20 passes between the working rolls (1) and (1 ') and its median plane corresponds substantially to the transverse plane of symmetry P2 of the whole of the rolling mill stand and in particular of the supporting rolls (2) and (2 ').
  • the cylinders are all aligned and centered on the same median plane P2.
  • the working rolls (1) and (1 ') can be displaced axially relative to the centering position so that their respective transverse plane of symmetry is shifted to one side or the other with respect to the median plane P2.
  • an axial displacement force F1 is applied in one direction or the other to the working cylinders (1) and (1 ′).
  • cambering forces F2 are applied to the ends of the shafts of the working rolls (1) and (1 '), by means of their chocks so as to camber the corresponding cylinder.
  • the working rolls (1) and (1 ') can be subjected at the same time to an axial displacement force F1 and to the bending forces F2.
  • FIG. 2 shows an end of a working cylinder with a chock, and an axial displacement device.
  • the working cylinder (1) is provided at its two ends with centered trunnions, by means of bearings , inside chocks (3) forming a bearing body and sliding mounted, parallel to the clamping plane P1, in windows (40) formed in the two uprights (4) of the rolling stand.
  • each chock (3) of the working cylinder 1 is provided with sliding faces (31) parallel to the clamping plane P1 and which can slide along corresponding faces ( 51) arranged inwards on support blocks (5) fixed in the windows (40) of the stand (4) of the rolling mill.
  • each chock (3) guided between the two vertical faces (51) can move in two directions, on the one hand vertically under the action of the bending device and on the other hand parallel to the axis (10 ) of the cylinder under the action of the axial adjustment device.
  • the axial displacement force which is applied to one of the chocks must be exerted exactly in the axis of the cylinder and, for this purpose, one can use, for example, a single jack supported on a lifting beam making it possible to apply the axial displacement force on the two sides of the chock.
  • the displaced cylinder is a driving cylinder
  • displacement cylinders (42) supplied in synchronism and placed symmetrically on either side of the means (43 ) for driving the cylinder in rotation (1), the chock (3) being provided, on each side of the axis (10), with hooking lugs (35) which engage in hooking heads corresponding to the rod of each cylinder (42).
  • This attachment can advantageously be carried out in a removable manner by lateral displacement of the displacement cylinder (42) as shown in FIG. 2 for the right cylinder.
  • each chock (3) of a cylinder (1) is secured to the latter in the axial direction by means of a cap (13) for closing the bearing cage, the latter being made of so as to be able to withstand axial forces, for example tapered bearings In this way, the axial displacement force applied by the jacks (42) on one of the chocks (3) is transmitted to the working cylinder and to the second chock placed at the other end of the latter.
  • Each chock (3) is on the other hand associated with a cambering assembly which, as shown diagrammatically in FIG. 6, generally consists of two pairs of jacks (6 a , 66 a ) and (6 b , B ) placed respectively on either side of the clamping plane P1 on which the axis of the cylinder 1 is centered.
  • each chock 3 is extended beyond the sliding faces (31) by bearing parts (32) in the form of ears which extend above the block. support (5) in which are housed the camber cylinders (6). However, the bending force is not applied directly to the chocks (3), but to intermediate pieces (7) which are interposed between the bending cylinders (6) and the corresponding support parts (32).
  • Each support block (5) is common for the two working cylinders (1) and (1 ') and comprises, at each end, at the top and at the bottom, a transverse recess (52) limited by two spaced faces (54) parallel to the clamping plane
  • Each intermediate piece (7) is provided with an external horizontal part (70) housed in the recess (52) and guided in translation along corresponding sliding faces on the two opposite faces (54) of the housing (52).
  • each intermediate part (7) has the shape of a T, the external part (70) forming two horizontal wings (75) which extend symmetrically on either side of a vertical central part (73) centered in the median plane P3 of the support block (5) perpendicular to the clamping plane P1, that is to say the vertical plane of symmetry of the two pairs of camber cylinders in which the chock (3) of each is centered two working cylinders (1 and 1 ') when the latter are themselves aligned and centered on the median plane P2 of the cage.
  • the vertical central part (73) of the intermediate piece (7) extends vertically between the two cylinders (6 a, 66 a) and engages in a machining (53) forming a central well formed in the support block (5) between the bores (67) of the two cylinders (6 a, 66 a) which extends the transverse recess (52) wherein the two wings extend (75) of the intermediate piece (7) to pass over the two jacks (6 a, 66 a) .
  • the central part (73) constitutes a guide foot for the intermediate part (7) mounted to slide vertically between two guide faces (55) parallel to the plane P3 and symmetrically spaced apart on either side of it and which constitute the two opposite faces of the central machining (53).
  • the same arrangement is adopted for the cylinders (6 ′ a , 66 ′ a ) for bending the lower cylinder (1 ′).
  • the support block (5) which is common for the two working cylinders (1 and 1 ') is therefore symmetrical, on the one hand, with respect to the vertical plane P3 and on the other hand, with respect to a horizontal plane.
  • Each bore (67) is sealed by a partition (63) which constitutes the bottom of the transverse recess (52) and limits the chamber of the jack (6) closed, on the opposite side, by the partition 68 and inside which slides the piston (61) extended by a rod (62) which passes through the partition (63) to rest on the corresponding wing (75) of the intermediate piece (7).
  • the two pairs of jacks (6 a , 66 a ) (6 ′ a , 66 ′ a ) thus formed on the two faces of the support block (5) can be supplied by hydraulic circuits as shown in FIG. 7, the support piece (5) thus constituting a real fixed hydraulic block.
  • the support lug (32) of the chock (3) is supported, by means of a grain of thrusts (33) on a smooth face (76) formed on the external part (70) of the intermediate piece (7) and along which the thrust grain (33) can therefore slide continuously following the axial displacements of the cylinder 1.
  • the thrust grain (33) is placed in the transverse plane of symmetry of the chock (3) and is therefore centered in the plane P3 in the position shown in FIG. 4 for which the working rolls (1) and (1 ') are aligned and centered in the median plane P2 of the cage.
  • the support block (5) is common for the two bending systems (6 and 6 ') of the two working rollers (1 and 1'), the central parts forming the guide foot (73, 73 ') of the two intermediate parts (7, 7') engage in the same machining (53) which completely crosses the support block (5), in the axis thereof, connecting between them the transverse recesses (52 and 52 ') and passing between the chambers of the four cylinders arching.
  • each guide foot (73) of each intermediate piece (7, 7 ′) is provided, at its end opposite to the external part (70), with a notch in the form of L which provides a thinned part (74) offset laterally so that the two guide feet (73, 73 ') can overlap in the middle part of the central machining (53).
  • each guide foot (73, 73 ') can be guided practically all along the guide faces (55) formed over the entire height of the central machining (53).
  • each chock is also centered in thrust planes P4 parallel to the clamping plane P1 and passing through the axes of the two corresponding camber cylinders.
  • the thrust planes P4, P'4 of the two cambering assemblies associated with the chocks (3 and 3 ') and placed in the same support block 5 are offset on either side of the plane of symmetry of the support block 5 on which the machining is centered (53).
  • each sliding part (7) moves vertically thanks to its guide foot (73) which opposes the moment of overturning resulting from the shifting of the thrust grain (33) relative to the plane of symmetry of the forces exerted by the jacks.
  • the invention therefore makes it possible to carry out at the same time the axial adjustment and the bending of a working cylinder and if the axial displacements remain reduced, as is most often the case, the moment of overturning of the intermediate piece (7 ) which results can be easily collected by the embedding effect of the guide foot (7).
  • the intermediate pieces (7) and (7a) corresponding to the two chocks (3) and (3a) of each cylinder (1) and which are placed at the same level with respect to the axis of the cylinder, are integral with a beam (77) extending along the cylinder, parallel to its axis.
  • This beam (77) can be dimensioned so as to absorb the moments of overturning of the parts (7) and (7a) due to the movement of the chocks (3) and (3a).
  • a balancing of the forces applied by the bending cylinders is carried out as a function of the position of the corresponding chock.
  • the offset of the displaced cylinder (1) is measured relative to the median plane P2 of the cage by means of a displacement sensor (44) consisting of two sliding parts, one relative to each other, fixed, for example on the two parts of one of the jacks (42) and providing an analog or digital signal proportional to the offset of the working cylinder relative to the centering position in the median plane P2 and of sign corresponding to the direction of the shift.
  • This signal is used for balancing the pressures in the camber cylinders by means of a device (8) shown diagrammatically in FIG. 7.
  • a displaceable cylinder (1) and its two bending devices each consisting of two sets of jacks placed in hydraulic blocks (5a, 5b, 5'c, 5'd) each assembly comprising two cylinders (6a, 66 a), (6b, 66b), (6'a, 66'a) (6'b, 66'b).
  • the reference 6 is assigned to the camber cylinders, placed on the side of the cylinder, that is to say towards the inside of the cage and the reference 66 to the cylinders placed towards the outside.
  • the four jacks associated with each chock are arranged in the manner described above and are centered in two transverse planes R3 and R4 spaced from each other by a distance e.
  • the hydraulic blocks (5a, 5b) and (5c, 5d) of the two chocks are connected by a single supply circuit (80) to a source of pressurized fluid not shown but the circuit (80) is divided into two branches ( 81) and (82) making it possible to supply the jacks placed on the same side of the same pressure chock in the direction of axial movement.
  • the branch (81) therefore supplies in parallel the jacks (6 a , 6 b ,) and (66 c , 66 d ) of the two rows R3 and R'4 placed on the right in FIG. 7 while the branch 82 supplies parallel the jacks (66 a , 66 b ,) and (6 c , 6 d ) of the two rows R4 and R'3 placed on the left.
  • the hydraulic circuit is designed so that, whatever the pressures, all the cylinders are supplied with the same flow rate so as to determine equal displacements at the same speed.
  • Each branch (81), (82) of the supply circuit (8) is provided with a pressure regulator (83) which, depending on the signals received on its input (84) regulates the pressure in the corresponding circuit but in maintaining a constant flow.
  • Each cylinder (1) is associated with an axial displacement sensor (44) providing an analog or digital signal proportional to the displacement and which is applied to a calculation unit (85).
  • the latter develops the pressure setpoints S1 and S2 applied to the inputs (84) of the pressure regulators (83) of the two branches (81) and (82) according to a law programmed in the advance to ensure a distribution of pressures P1 and p2 such that the sum of the moments resulting from the thrust forces applied by the camber cylinders in the planes P4 and the reaction of the bearing part 32 of the corresponding chock on the T-shaped part is zero.
  • the two rows of cylinders R3 and R4 may not be symmetrical with respect to the median plane P5 of the chock roll and this allows the cylinders to be arranged in the most adequate manner inside the hydraulic blocks (5) whose plane of symmetry does not necessarily coincide with that of the bearing.
  • the various members used for balancing the pressures could be replaced by means fulfilling the same functions, these means being able to be hydraulic, electric or even mechanical (cam, lifting arm, etc.).
  • any technology for measuring displacements, calculating corrections and balancing pressures can be used to obtain the desired result.
  • the fixed bending devices according to the invention can adapt to different diameters of cylinders and / or adapt to a variation of the diameter due wear, within the limit of the cylinder stroke.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Soil Working Implements (AREA)
  • Transplanting Machines (AREA)
  • Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)

Claims (16)

  1. Walzgerüst mit axial verschiebbaren Walzen bestehend innen in einem Stützgerüst (4) aus mindestens zwei Arbeitswalzen (1, 1') die sich gemäss einer Anstellungsebene P1 auf mindestens zwei Stützwalzen (2, 2') abstützen und deren Enden über Wälzlager in Einbaustücken (3, 3') abgestützt sind, die gleitbar in dem Stützgerüst (1) parallel zur Anstellungsebene P1 montiert sind, wobei mindestens einer Arbeitswalze (1) einerseits Mittel (42) zum Verschieben dieser Walze (1) entlang deren Achse (10) beiderseits einer zur Mittelebene P2 des Walzgerüstes (4) zentrierbaren Lage der Arbeitswalzen sowie anderseits Mittel (6) zum Biegen dieser Walze (1) zugeordnet sind, bestehend für jedes Einbaustück (3) und beiderseits der Anstellungsebene aus mindestens einem Biegezylinder (6), der innen in einem mit dem Walzgerüst fest verbundenen Stützblock (5) angeordnet ist und auf ein entsprechendes Auflageteil (32) des Einbaustückes (3) über ein Gleitstück (7) einwirkt, das aus mindestens einem oberhalb eines jeden Zylinders (6) sich erstreckenden Auflageteil (75) und aus mindestens einem fussartig ausgebildeten Führungsteil (73) besteht, das senkrecht in einer innen in dem Stützblock (5) maschinelle bearbeiteten Bohrung (53) gleitend angeordnet ist und das an der zu den Biegezylindern (6) entgegengesetzten Seite eine glatte Planfläche (76) parallel zur Achse der Walze (1) aufweist, auf welcher das entsprechende Auflageteil (32) des Einbaustückes (3) sich gleitbar abstützt, wobei das Gleitstück (7) zwischen zwei Paar innen in dem Stützblock (5) angeordneten und jeweils parallel und senkrecht zur Anstellungsebene verlaufenden Führungsflächen (54, 55) gleitbar montiert ist.
  2. Walzgerüst nach Anspruch 1, dadurch gekennzeichnet> dass die beiden senkrecht zur Anstellungsebene P1 angeordneten Führungsflächen (55) zwei entgegengesetzte FLâchen der bearbeiteten Bohrung (5'') bilden, zwischen denen der Führungsfuss (73) des Gleitstückes (7) gleiten kann, und dass die beiden parallel zur Anstellungsebene P1 verlaufenden Führungsflächen (54) zwei entgegengesetzte Flächen einer in dem Stützblock (5) angeordneten Queraussparung (52) bilden, zwischen denen ein Teil (70) des Gleitstückes (7) gleiten kann.
  3. Walzgerüst nach einem der Ansprüche 1 und 2, dadurch gekennzeichnet, dass die parallel zur Anstellungsebene P1 in dem Stützblock (5) angeordneten Führungsflächen (54) beiderseits einer durch die Achsen der Biegezylinder (6) verlaufenden Schubebene P4 symetrisch im Abstand angeordnet sind, in welcher das Auflageteil (32) des Einbaustückes (3) ebenfalls zentriert ist, wobei die gesamten für die Biegung beaufschlagten Kräfte somit durch diese Schubebene (P4) verlaufen.
  4. Walzgerüst nach einem der Ansprüche 1 bis 3, bei dem jedem Auflageteil (32) des Einbaustückes (3) eine Biegeeinheit (6) zugeordnet ist, bestehend aus zwei im Abstand von einander angeordneten und in einer zur Anstellungsebene P1 parallelen Ebene P4 zentrierten Zylinder (6, 66), wobei das T-förmig ausgebildete Gleitstück (7) ein den Führungsfuss bildendes Mittelteil (73) sowie ein erweitertes Aussenteil (70) umfasst, das beiderseits des Fusses (73) zwei sich jeweils über je einem dieser Zylinder (6) und (66) horizontal erstreckenden Flügel (75) bildet, wobei die in dem Stützblock (5) bearbeitete Bohrung ein oberhalb der beiden Bombierungszylinder (6) verlaufendes Querteil (52) aufweist und in welcher das erweiterte Aussenteil (70) geführt wird, bestehend aus den beiden Flügeln (75) des T-förmig ausgebildeten Gleitstückes (7) und dem als Schacht ausgebildetes Mittelteil (53), in welchem das den Führungsfuss des Gleitstückes (7) bildenden Mittelteil (73) geführt wird.
  5. Walzgerüst nach Anspruch 4, dadurch gekennzeichnet, dass in jedem Walzgerüst-Ständer (4) die Biegeeinheiten (6) (6') der beiden Arbeitswalzen (1) (1') in einem einzigen Stützblock (5) montiert sind, der an seinen beiden einander gegenüberliegenden Flächen zwei Queraussparungen (52) (52') aufweist, die durch eine einzige zwischen den Biegezylindern (6) (6') verlaufenden bearbeitete Zentralbohrung (53) verbunden sind.
  6. Walzgerüst nach Anspruch 5, dadurch gekennzeichnet, dass zur Aufnahme der Umkehrwirkungen des Gleitstückes (7) während der Biegung der Führungsfuss (73) von jedem Gleitstück (7) an der Seite des entsprechenden Einbaustückes (3) einen eingebetteten Kopf mit ausreichender Breite bildet, und dass dessen Innenende an der dem Einbaustück (3) entgegengesetzten Seite im Querschnitt durch eine zur Anstellungsebene P1 parallelen Ebene einen L-förmigen Ausschnitt mit einem seitlich zur Schubebene P4 versetzten dünneren Teil (74) aufweist, so dass sich die beiden dünneren Teile (74, 74') der beiden den jeweiligen Arbeitswalzen (1) (1') zugeordneten Gleitstücke (7) und (7') in dem Mittelteil der in der Mitte des Stützblockes (5) bearbeiteten einzigen Bohrung (53) überlappen.
  7. Walzgerüst nach einem der Ansprüche 4 bis 6, dadurch gekennzeichnet, dass die beiden Schubebenen P4, P'4 der jeweils den beiden Arbeitswalzen (1) (1') zugeordneten Biegeeinheiten (6) (6') beiderseits der Mittelebene der Zentralbohrung (53) des Stützblockes (5) seitlich versetzt sind.
  8. Walzgerüst nach einem der Ansprüche 4 bis 7, dadurch gekennzeichnet, dass es eine Ausbalancierungseinrichtung (10) der Biegezylinder (6) umfasst, mit einem Mittel (44) zum Messen der Verschiebung der betreffenden Arbeitswalze (1) zur Zentrierungslage und Mittel (83) zur momentanen Einzeleinstellung des jeweiligen mit Druck beaufschlagten Biegezylinders (6) je nach der gemessenen Verlagerung und der Lage des betreffenden Zylinders (6) zur Mittelebene des Gleitstückes (7), so dass die Summe der durch die beaufschlagten Biegekräfte sich ergebende Momente und des Momentes aus der Einbaustück-Gegenwirkung auf das Gleitstück (7) gleich Null ist.
  9. Walzgerüst nach einem der vorhergehenden Ansprüche, dadurch gekennzeichnet, dass die zur Achse der Arbeitswalze (1) auf der gleichen Höhe befindlichen Gleitstücke (7, 7a) der beiden Einbaustücke (3, 3a) von ein und derselben Arbeitswalze (1) an beiden Enden eines durchlaufenden Trägers (77) angeordnet sind, der sich parallel zur Achse der Arbeitswalze (1) zwischen den beiden entsprechenden Ständer des Walzgerüstes (4) erstreckt.
  10. Walzgerüst nach Anspruch 8, dadurch gekennzeichnet, dass, wobei den beiden Einbaustücken (3) (3a) der jeweiligen Walze jeweils zwei symetrisch beiderseits der Anstellungsebene (P1) angeordneten Biegezylindereinheiten zugeordnet sind, die jeweils in den jeweiligen Einheiten in ein und denselben relativen Lagen zur Mittelebene (P5) der jeweiligen Lager angeordneten Zylinder (6a und 6b) (66d und 66c) an ein und denselben Zweig (81) (82) eines gemeinsamen Druckmedium-Versorgungskreises (80) parallel angeschlossen sind, der zahlenmässig soviel Abzweigungen wie die Anzahl Zylinder (6, 66) in jeder Einheit umfasst, wobei jeder Versorgungszweig ein Mittel (83) zur einzelnen Mediumdruckeinstellung mit Halten von gleichen Durchsätzen in sämtlichen Zweigen aufweist.
  11. Walzgerüst nach Anspruch 10, dadurch gekennzeichnet, dass die Mittel zur einzelnen Druckeinstellung in den Zylindern ein Servoventil (83) in jedem Zweig (81) (82) des Versorgungskreises umfassen, wobei diese Servoventile über ein Kalkulationsmittel (85) ausgehend von einem programmierten Gesetz der Korrekturen, die entsprechend der gemessenen und von dem Rechnungsmittel angezeigten Verschiebung und den jeweiligen Lagen der durch den betreffenden Zweig versorgten Zylinder an den Drücken vorzunehemen sind, gesteuert werden, um eine korrekte Verteilung der Druckkraft zu gewährleisten.
EP88400372A 1987-02-27 1988-02-18 Walzgerüst mit axial verschiebbaren Walzen und Verfahren zum Steuern des Walzenprofils Expired - Lifetime EP0283342B2 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8702706 1987-02-27
FR8702706A FR2611541B1 (fr) 1987-02-27 1987-02-27 Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement

Publications (3)

Publication Number Publication Date
EP0283342A1 EP0283342A1 (de) 1988-09-21
EP0283342B1 EP0283342B1 (de) 1992-04-29
EP0283342B2 true EP0283342B2 (de) 1997-01-22

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EP88400372A Expired - Lifetime EP0283342B2 (de) 1987-02-27 1988-02-18 Walzgerüst mit axial verschiebbaren Walzen und Verfahren zum Steuern des Walzenprofils

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Country Link
US (1) US4934166A (de)
EP (1) EP0283342B2 (de)
JP (1) JPH0751244B2 (de)
BR (1) BR8800841A (de)
CA (1) CA1294464C (de)
DE (1) DE3870495D1 (de)
ES (1) ES2031250T5 (de)
FR (1) FR2611541B1 (de)

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FR2611541B1 (fr) 1987-02-27 1994-04-29 Clecim Sa Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement
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FR2710567B1 (fr) * 1993-09-28 1995-12-22 Clecim Sa Laminoir à déplacement axial.
US5448901A (en) * 1994-05-03 1995-09-12 The University Of Toledo Method for controlling axial shifting of rolls
US5752404A (en) * 1996-12-17 1998-05-19 Tippins Incorporated Roll shifting system for rolling mills
US5970771A (en) * 1998-07-10 1999-10-26 Danieli United Continuous spiral motion system for rolling mills
AT407124B (de) * 1998-10-19 2000-12-27 Voest Alpine Ind Anlagen Biegevorrichtung für zwei arbeitswalzen eines walzgerüstes
IT1315119B1 (it) * 2000-09-25 2003-02-03 Danieli Off Mecc Dispositivo e metodo per curvare i cilindri di una gabbia dilaminazione.
DE10334682A1 (de) * 2003-07-30 2005-02-17 Sms Demag Ag Walzvorrichtung
AT504208B1 (de) * 2006-04-21 2008-04-15 Siemens Vai Metals Tech Gmbh Biegevorrichtung für zwei arbeitswalzen eines walzgerüstes
US20070254230A1 (en) * 2006-04-28 2007-11-01 Xerox Corporation External additive composition and process
DE102006051728B4 (de) * 2006-10-30 2013-11-21 Outokumpu Nirosta Gmbh Verfahren zum Walzen von Metallbändern, inbesondere von Stahlbändern
DE102008035702A1 (de) * 2008-07-30 2010-02-04 Sms Siemag Aktiengesellschaft Walzvorrichtung
DE102008049179A1 (de) 2008-09-26 2010-04-01 Sms Siemag Aktiengesellschaft Walzvorrichtung
DE102009058876A1 (de) * 2009-01-23 2010-07-29 Sms Siemag Ag Biege- und Ausbalanciervorrichtung für axial verschiebbare Arbeitswalzen eines Walzgerüstes
ITMI20101502A1 (it) * 2010-08-05 2012-02-06 Danieli Off Mecc Sistema integrato di bending e shifting sotto carico per gabbie ad elevata apertura tra i rulli di lavoro
WO2012049183A1 (de) * 2010-10-12 2012-04-19 Sms Siemag Ag Walzgerüst
ITMI20120598A1 (it) * 2012-04-12 2013-10-13 Danieli Off Mecc Sistema integrato di piegatura e di bilanciamento per gabbie di laminazione
EP3981522B1 (de) * 2019-10-25 2024-05-01 Primetals Technologies Japan, Ltd. Walzwerk

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BR8300010A (pt) * 1982-01-06 1983-08-30 Hitachi Ltd Laminador
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US4803865A (en) * 1987-07-17 1989-02-14 SMS Schloemann--Siemag Aktiengesellschaft Stand-supported bending device for axially slidable rolls of a multiroll rolling mill

Also Published As

Publication number Publication date
JPH0751244B2 (ja) 1995-06-05
ES2031250T3 (es) 1992-12-01
US4934166A (en) 1990-06-19
CA1294464C (fr) 1992-01-21
JPS63230208A (ja) 1988-09-26
EP0283342B1 (de) 1992-04-29
DE3870495D1 (de) 1992-06-04
BR8800841A (pt) 1988-10-04
FR2611541A1 (fr) 1988-09-09
ES2031250T5 (es) 1997-03-16
FR2611541B1 (fr) 1994-04-29
EP0283342A1 (de) 1988-09-21

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