EP1703999B1 - Procede et cage de laminoir pour influer de maniere multiple sur des profils - Google Patents

Procede et cage de laminoir pour influer de maniere multiple sur des profils Download PDF

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Publication number
EP1703999B1
EP1703999B1 EP04798032A EP04798032A EP1703999B1 EP 1703999 B1 EP1703999 B1 EP 1703999B1 EP 04798032 A EP04798032 A EP 04798032A EP 04798032 A EP04798032 A EP 04798032A EP 1703999 B1 EP1703999 B1 EP 1703999B1
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EP
European Patent Office
Prior art keywords
roll
profile
displacement
rolls
rolling gap
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Application number
EP04798032A
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German (de)
English (en)
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EP1703999A2 (fr
Inventor
Günter KNEPPE
Wolfgang Rohde
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SMS Siemag AG
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SMS Demag AG
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Publication of EP1703999A2 publication Critical patent/EP1703999A2/fr
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Classifications

    • 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
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/142—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC
    • 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
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B37/00—Control devices or methods specially adapted for metal-rolling mills or the work produced thereby
    • B21B37/28—Control of flatness or profile during rolling of strip, sheets or plates
    • B21B37/40—Control of flatness or profile during rolling of strip, sheets or plates using axial shifting of the rolls
    • 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
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/147—Cluster mills, e.g. Sendzimir mills, Rohn mills, i.e. each work roll being supported by two rolls only arranged symmetrically with respect to the plane passing through the working rolls
    • 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
    • B21B27/00—Rolls, roll alloys or roll fabrication; Lubricating, cooling or heating rolls while in use
    • B21B27/02—Shape or construction of rolls
    • B21B27/021—Rolls for sheets or strips

Definitions

  • the invention relates to a method and a roll stand for rolling sheets or strips, with work rolls, which are supported on support rolls or intermediate rolls with support rollers, wherein the adjustment of the roll gap profile is carried out by axially displacing provided with curved contours roller pairs.
  • the rolls of selected pairs of rolls are in pairs axially displaceable against each other and each roll of such a pair of rolls is provided with a curved contour which extends on both rolls of the roll pair to opposite sides over the entire length of the roll barrel.
  • Known embodiments are quarto scaffolding, six-high rolling stands and the various forms of multi-roll stands arranged as one-way stands, reversing stands or tandem rolling stands.
  • Roll stands with effective adjusting mechanisms for the presetting of the required roll gap and for the change of the roll gap under load are in the EP 0 049 798 B1 described and are therefore already prior art. Used here are work rolls and / or back-up rolls and / or intermediate rolls, which are axially displaceable against each other.
  • the rollers are provided with a curved contour extending towards a bale end, which extends on the two rollers of a pair of rollers respectively to opposite sides over the entire length of the bale rolls and which has a shape in which the two bale contours are exclusively in a certain relative Complement complementary axial position of the rollers.
  • the feature of complementary complementation in a particular axial position determines all point-symmetric functions to the nip center as appropriate.
  • the 3rd degree polynomial has been found. So is out of the EP 0543 014 B1 a six-high rolling stand with axially displaceable intermediate and work rolls, in which the intermediate rolls have crowns which are point-symmetrical with respect to the framework center point and whose crowning can be expressed by a third-degree equation.
  • This function of the roll contours, which is point-symmetrical with regard to the nip center manifests itself in the load-free nip as a polynomial of the second degree, ie as a parabola.
  • Such a nip has the particular advantage that it is suitable for rolling different Walzgutbreiten.
  • the achievable by the roller displacement change in the profile height allows a targeted Adaptation to the influencing variables described above and already covers most of the required profile setting with high flexibility.
  • the object of the present invention is to solve the above-exemplified problem with a simple mechanism and to achieve a further improvement of the adjusting mechanisms and the strategy for producing absolutely flat sheets or strips with a predetermined thickness profile over the entire width of the rolled rolled material.
  • the object is achieved with the characterizing features of claim 1, characterized in that the setting of the roll gap is performed by at least two independently axially displaceable roller pairs with different curved contours whose different contours by splitting the effective in the nip gap setpoint profile in at least two different Roll nip nominal profiles are calculated and transferred to the roller pairs.
  • a roll stand for rolling sheets or strips is characterized by the features of claim 6 and the features of further subclaims.
  • the function of the unloaded roll gap required for setting the roll gap profile is first developed for two selected shift positions as polynomial of the nth degree with even exponents.
  • each of these two functions to be used for a pair of rollers is split into a second-order polynomial with the known positive properties for presetting and a residual polynomial with higher even powers, which yields profile 0 in roll center (the profile height in FIG Roller center is identical to the profile height at the edges) and has two maxima on both sides of the roller center, which are suitable for influencing quarter-wave.
  • the function of the roll gap is thus revealed as the difference between the axial spacing of the rolls and twice the sum of even powers, that is to say as a function symmetrical to the middle of the framework. Obviously, this result is achieved without specifying a specific radius function and therefore applies to every differentiable function.
  • the chosen radius function determines only the coefficients of the power elements via its derivatives.
  • Equation (G7) describes the roller profile with which the ideal roller is to be equipped in a certain displacement position.
  • the polynomial must be split into individual polynomials, each of which can be dimensioned with a value that can be understood for operational practice.
  • R ⁇ i 2 - q 0 ⁇ z 0 + c 2 ⁇ z 2 + q 2 ⁇ z 2 for the share Second degree
  • R ⁇ i 4 - q 2 ⁇ z 2 + c 4 ⁇ z 4 + q 4 ⁇ z 4 for the share 4th degree
  • R ⁇ i 6 - q 4 ⁇ z 4 + c 6 ⁇ z 6 + q 6 ⁇ z 6 for the share 6th degree
  • the value q 6 is 0 for the highest 6th degree considered here, since it is assigned to the nonexistent 8th degree. It is therefore also necessary numerically to start the resolution with the highest degree.
  • Ri 0 of equation (G9) is freely selectable as nominal radius of the roller.
  • two displacement positions s 1 and s 2 are to be selected, for each of which the desired profile is to be determined by selecting the crown values of Cr 2 to Cr n .
  • the profiles will change continuously due to the roll displacement. Since the individual power levels can be dimensioned independently of one another, eliminating the mandatory requirement of a complementary complement of the roll profiles of upper roll to lower roll. However, this can easily be brought about by deliberately setting the profile height 0 for one of the two freely selectable displacement positions, if necessary also outside the real displacement path, uniformly for all degrees of power.
  • Equation (G7) consists, as already described above, for two shift positions s 1 and s 2 . Equating the two equations (G7) with Eq. (G6) yields the determinative equations necessary for the coefficients a i of the polynomial for the roll grinding, corresponding to the selected power level. The individual equations of equations are from the coefficient scheme of FIG. 2 immediately readable.
  • the coefficient a 1 remains indefinite because it has no influence on the profile shape of the roller. It determines the taper of the roller and therefore requires a different design criterion, which will be explained below on contact of a profiled roller with a cylindrically shaped intermediate roller or back-up roller.
  • the raised profile areas of the profiled roller will embed in the contact area by elastic deformation in the cylindrical roller and possibly bring about a non-parallel position of the two rollers to each other.
  • the pitch a 1 of the work roll contour must be dimensioned such that the center lines of the two rolls are parallel to one another.
  • a rolling line forms in the contact zone, which is also parallel to the center lines of both rolls.
  • the radius of this rolling line with respect to the work roll is R w .
  • the force element dF generated over the distance z a moment element dM K , which causes a tilting of the rollers.
  • the length-related spring constant may be set as constant over the contact length.
  • Equation (G25) is also valid for profiled rolls which are in contact with the profiled roll of another roll pair, if the coefficient a 1 of this contact roll has also been dimensioned by equation (G25).
  • the at least two pairs of rollers will be chosen differently depending on the framework construction.
  • z. B the slidable intermediate rolls provided with a profile which generates the polynomial 2nd degree in the nip.
  • the movable work rolls are suitable for the remaining polynomial and serve to influence the quarter waves or other special profile influencing.
  • the profile heights of the profiles to be set by the respective pair of rollers will be increased in a manner known per se in order to improve penetration through the nip, in particular with pairs of rollers located further from the nip.
  • the two maxima in the residual polynomial are in a position symmetrical to the roll center, which is variable over the degree of the polynomial. This results in - depending on the framework construction - the possibility to create a further adjustment for eighth-waves or edge waves on another sliding pair of rollers. Of course it is also possible to introduce this variant in the simplest way on the roll change.
  • FIGS. 3 to 5 the possible displacement ranges of individual displaceable roller pairs (P1, P2, P3) with differently curved contours are shown on exemplarily selected rolling stands (1, 1 ', 1 ")
  • Fig. 3 is shown in a side view a quartz scaffolding 1. It consists of a displaceable pair of rollers P1, the work rolls 2, and a further displaceable pair of rollers P2, the support rollers 4. Between the work rolls 2, the rolling stock 5 is rolled in the nip 6.
  • FIGS. 3a and 3b in which the quarto scaffolding 1 of the FIG. 3 is shown rotated by 90 °, the possible displacement ranges of the roller pairs P1 and P2 pointed out.
  • respective displacement paths of the roll centers 7 are possible by the amount sp1 for the pair of rolls P1 and sp2 for the pair of rolls P2 to the right or to the left.
  • the shifts are limited by the reference width bo, when a roll edge is shifted in the vicinity of the rolling stock edge of a rolling stock width corresponding to the reference width.
  • FIG. 4 is a side view of a 6-roll stand 1 'shown. It consists of a displaceable pair of rollers P1, the work rolls 2 and a displaceable pair of rollers P2, the intermediate rollers 3 and a further, non-displaceable pair of rollers, the support rollers 4th
  • FIGS. 4a and 4b in which the 6-roll stand 1 'of Fig. 4 is shown rotated by 90 °, the possible displacement ranges of the roller pairs P1 and P2 are shown. The shift takes place here in the same way as in the FIGS.
  • FIG. 5 is a side view, as an example of a multi-roll stand, a 10-roll stand 1 "is shown. It consists of a displaceable pair of rollers P1, the work rolls 2, a displaceable pair of rollers P2, the intermediate rolls 3 ', a further displaceable pair of rollers P3, the intermediate rollers 3 "and the two support roller pairs 4' and 4".
  • FIGS. 5a and 5b in which the 10-Walzengerüst 1 "the Fig. 5 is shown rotated by 90 °, are in a section through the rollers 4'-3'-2-2-3'4 'the possible displacement ranges of the roller pair P1, the work rolls 2 and the roller pair P2, in the Fig. 5 shown intermediate rolls 3 'shown.
  • the maximum displacement is sp1 or sp2.
  • FIGS. 5c and 5d point in a section through the rollers 4 "-3" -2-2-3 “-4" again the pair of rollers P1, but this time together with the pair of rollers P3, ie with the in the Fig. 5 arranged on the right intermediate rolls 3 "with the maximum displacement sp3.
  • the displacement paths of all three roller pairs are independent of each other within the maximum values sp1, sp2 and sp3 in direction and magnitude.
  • the two pairs of support rollers 4 'and 4 are also formed immovable in this embodiment of the 10-roll stand 1".
  • the 10-roll stand 1 is thus clear, with which variety of different combinations with a correspondingly large number of sliding pairs of rollers with different curved roll contours, the paired roll displacement and thus a sensitive influence of the roll gap 6 can be performed.
  • FIGS. 6 and 7 are in an inventive form of representation, the predetermined roll gap profiles for the two selected shift positions of a pair of rollers of the prior art in the shares of a polynomial 2nd degree and a residual polynomial 4th degree separated.
  • FIGS. 10 to 17 is shown as the in the FIGS. 6 to 9 selected roll gap contours with polynomials 2nd and 4th degree according to the invention can be transmitted to two independently displaceable pairs of rollers.
  • FIGS. 14 and 15 the selected nip nominal profiles 22 and 23 of the FIGS. 6 and 7 known polynomial 4th degree. They lead to the in the FIGS. 16 and 17 illustrated roller contours of the upper roller 32 and the lower roller 32 'and are also continuously variable within the displacement range.
  • roller pair P1, P2, P3, which has the profile of a 4th degree polynomial, it is thus possible to sensitively influence the so-called quarter waves from +50 ⁇ m to 0 to -50 ⁇ m, without the adjustment of the set of rolls for the 2nd. Degree of adverse change is subject.
  • a nearly parallel nominal roll gap profile 25 is required, which is intended to open only at the rolling stock edges. It is formed by the addition of the function curves 24 of polynomials with the degrees 2, 4, 6, 8, 10, 12, 14 and 16 with the profile heights 400, 100, 60, 43, 30, 20, 14, and 10 microns.
  • FIGS. 20 and 21 the corresponding roller contours 33 for the upper roller and 33 'for the lower roller are shown. It can be seen that the desired opening of the roll gap by the drop of the nominal roll gap profile 25 ( Fig. 20 ) at the edges of the rolling stock, which is displaced in the direction of -100 mm ( Fig. 21 ) reduced to 0. At -100 mm there is a parallel nip with a slight s-shaped curvature at the rolling stock edges.
  • a roller pair designed in this way allows the sensitive correction of the thickness decrease at the rolling stock edges. According to the invention, such a pair of rollers can be used advantageously in conjunction with a pair of rollers for the parabolic contour corresponding to FIGS. 10 to 13 be used. Also, with appropriate scaffolding design, the additional inclusion of a correction option with rollers according to the FIGS. 14 to 17 conceivable.
  • each movable roller pair P1, P2, P3 are described by two freely selectable symmetrical profiles arbitrarily high degree, which are also assigned two freely selectable shift positions.
  • the profile heights of the individual degrees of power for the two freely selectable displacement positions are different when choosing a profile shape from more than one power degree. This has the consequence that the displacement position to achieve the profile height 0 for the different degrees of power is different, so that a complementary complement of the roll contours is deliberately avoided.
  • the profile height of all powers is set to 0, to complement each other To force roller contours in this displacement position.
  • the selected displacement position for the profile 0 can also be outside the real displacement range.
  • the profile heights of the individual degrees of power for the two freely selectable displacement positions are chosen such that the distance between the two profile maxima of a minimum by the roller displacement continuously changed to a maximum.
  • the invention is not limited to the use of polynomials.
  • the transcendental functions or exponential functions are mathematically resolved into power series.
  • the operational application or the actual displacement of the individual pairs of rollers takes place in a known manner in that the displacement systems of the roller pairs P1, P2, P3 are used as adjusting systems in a closed flatness control loop.
  • the current flatness of the rolling stock is determined and compared with a target value.
  • the deviations across the bandwidth are analyzed according to degrees of power and assigned to the individual roller pairs P1, P2, P3 as manipulated variables in accordance with the degrees of power that can be influenced by them.
  • Example shown would assign to the pair of rollers for generating the nominal nip profiles 20, 21 control values for the elimination of center shafts and the pair of rollers for generating the desired nip profiles 22, 23 control values for the removal of quarter waves.
  • the direct measurement measurement in the form of a measurement of the thickness distribution over the rolling stock width takes the place of the flatness measurement in the control loop by measuring the tensile stress distribution.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Metal Rolling (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Paper (AREA)
  • Bending Of Plates, Rods, And Pipes (AREA)
  • Machines For Manufacturing Corrugated Board In Mechanical Paper-Making Processes (AREA)
  • Rolls And Other Rotary Bodies (AREA)

Claims (16)

  1. Procédé pour la laminage de tôles ou de bandes dans une cage de laminage (1, 1', 1") avec des cylindres de travail (2), qui s'appuient sur des cylindres d'appui (4) ou des cylindres intermédiaires (3, 3', 3") avec des cylindres d'appui (4, 4', 4"), le réglage du profil de la fente de laminage (6) étant réalisé par un déplacement axial de paires de cylindres (P1, P2, P3) pourvues de contours courbés (30, 30', 31, 31', 32, 32', 33, 33') caractérisé
    en ce que le réglage du profil de la fente de laminage (6) est réalisé par au moins deux paires de cylindres (P1, P2, P3) pouvant être déplacées axialement indépendamment l'une de l'autre avec des contours courbés différemment (30, 30' ; 31, 31' ; 32, 32' ; 33, 33'), dont les contours différents sont calculés par fractionnement du profil de consigne (10, 11) de la fente de laminage résultante décrivant le profil (6) de la fente de laminage en au moins deux profils de consigne (20, 21 ; 22, 23 ; 25, 26) de fente de laminage différents et transférés aux paires de cylindres (P1, P2, P3).
  2. Procédé selon la revendication 1, caractérisé
    en ce qu'à une parmi deux paires de cylindres (P1, P2, P3) pouvant être déplacées axialement indépendamment l'une de l'autre sont associés profils de consigne (20, 21) de fente de laminage du 2ème degré, qui conduisent à des contours de cylindre courbés du 3ème degré (31, 31') avec lesquels on obtient un maximum de profil au centre du cylindre (8) pouvant être modifié par le déplacement des cylindres, alors que la deuxième paire de cylindres obtient des profils de consigne de fente de laminage du 4ème degré (22, 23) qui conduisent à des contours de cylindre courbés du 5ème degré (32, 32'), qui résultent en un profil de fente de laminage avec deux maximums de profil identiques symétriques par rapport au centre du cylindre (8), pouvant être modifié par déplacement des cylindres.
  3. Procédé selon la revendication 1, caractérisé
    en ce qu'on développe d'abord les profils de consigne (10, 11) de la fente de laminage résultants à fixer pour la définition du profil (6) de la fente de laminage modifiable par le déplacement de cylindres en polynômes du degré n avec des exposants pairs, puis ceux-ci sont fractionnés en profils de consigne (20, 21) de fente de laminage avec des polynômes du 2ème degré et en profils de consigne (22, 23 ; 25, 26) de fente de laminage avec les polynômes résiduels, qui recouvrent tous les autres degrés de puissance.
  4. Procédé selon l'une quelconque des revendications 1 à 3, caractérisé
    en ce que pour le réglage du profil (6) de la fente de laminage, on utilise plusieurs paires de cylindres (P1, P2, P3) avec des profils de consigne (20, 21 ; 22, 23 ; 25, 26) de fente de laminage, pour lesquels chaque distance des maximums du profil (6) de fente de laminage obtenu par rapport au centre (8) du cylindre est différente.
  5. Procédé selon l'une quelconque des revendications 1 à 4, caractérisé
    en ce que pour une paire de cylindres (P1, P2, P3), le profil de consigne (25) de la fente de laminage pour une position déplacée est formée sous forme de somme de profils (24) avec des puissances paires du degré 2, 4, 6...n par le choix des hauteurs de profil associées, de manière telle qu'on obtient, sur une large zone de la largeur une allure quasiment droite du profil de consigne (25) de la fente de laminage, qui ne s'écarte de la ligne droite qu'au niveau des bords et en ce que le profil de consigne (26) de la fente de laminage pour la deuxième position déplacée, pour toutes les puissances choisies, obtient une hauteur de profil égale à 0, suite à quoi on obtient entre les contours de cylindre (33, 33') une fente de laminage (6) quasiment parallèle qui ne s'écarte du parallélisme qu'au niveau de la zone des bords.
  6. Cage de laminage (1, 1', 1 ") pour la laminage de tôles ou de bandes avec des cylindres de travail (2), qui s'appuient sur des cylindres d'appui (4) ou des cylindres intermédiaires (3, 3', 3") avec des cylindres d'appui (4, 4', 4"), le réglage du profil (6) de la fente de laminage étant réalisé par un déplacement axial de paires de cylindres (P1, P2, P3) pourvues de contours courbés (30, 30', 31, 31', 32, 32', 33, 33') pour la réalisation du procédé selon l'une quelconque des revendications, caractérisée
    en ce qu'au moins deux paires de cylindres (P1, P2, P3) peuvent être déplacées axialement indépendamment l'une de l'autre et présentent des contours de cylindre (30, 30' ; 31, 31'; 32, 32'), différents, les contours des cylindres d'une paire de cylindres (P1, P2, P3) étant réalisés de manière telle qu'ils résultent dans la fente de laminage (6) en un profil (20, 21) symétrique par rapport au centre du cylindre (8) avec un maximum de profil au centre (8) du cylindre, modifiable par le déplacement des cylindres, alors que les contours des cylindres d'au moins une deuxième paire de cylindres (P1, P2, P3) conduisent dans la fente de laminage (6) à un profil symétrique (22, 23) par rapport au centre du cylindre (8), qui est caractérisé par deux maximums identiques, modifiables par déplacement des cylindres, symétriques par rapport au centre (8) du cylindre.
  7. Cage de laminage (1, 1', 1 ") selon la revendication 6, caractérisée
    en ce qu'on a prévu plusieurs paires de cylindres (P1, P2, P3) avec deux maximums situés symétriquement par rapport au centre du cylindre (8), où la chaque distance des maximums par rapport au centre (8) des cylindres est différente.
  8. Cage de laminage (1, 1', 1 ") selon la revendication 6, caractérisée
    en ce que des parties de polynôme d'un degré supplémentaire sont superposées à la paire de cylindres (P1, P2, P3) avec le maximum de profil (20, 21) central.
  9. Cage de laminage (1, 1', 1") selon l'une quelconque des revendications 6 à 8, caractérisée
    en ce que les formes de profil (20, 21 ; 22, 23 ; 25, 26) pouvant être obtenues dans la fente de laminage (6) de chaque paire de cylindres (P1, P2, P3) pouvant être déplacée sont décrites par à chaque fois deux profils symétriques pouvant être choisis librement d'un degré supérieur quelconque, qui sont associés à deux positions de déplacement pouvant également être choisies librement.
  10. Cage de laminage (1, 1', 1") selon la revendication 9, caractérisée
    en ce que lors du choix d'une forme de profil (20, 21 ; 22, 23 ; 25, 26) parmi plus d'un degré de puissance, les hauteurs de profil des différents degrés de puissance pour les deux positions de déplacement pouvant être choisies librement sont différentes, de manière telle qu'un complément complémentaire des contours de cylindre (30, 30', 31, 31', 32, 32', 33, 33') est évité consciemment.
  11. Cage de laminage (1, 1', 1") selon la revendication 9, caractérisée
    en ce que lors du choix d'une forme de profil (20, 21 ; 22, 23 ; 25, 26) parmi plus de deux degrés de puissance, les zones de réglage des différents degrés de puissance pour les deux positions de déplacement pouvant être choisies librement sont choisies de manière telle que la distance des deux maximums de profil est modifiée en continu d'un minimum à un maximum par le déplacement des cylindres.
  12. Cage de laminage (1, 1', 1") selon la revendication 6, caractérisée
    en ce que les contours (31, 31') des cylindres de la paire de cylindres (P1, P2, P3) avec un maximum de profil (20, 21) central suivent la fonction mathématique d'un polynôme du 3ème degré, alors que les contours (32, 32') des cylindres (P1, P2, P3) avec deux maximums de profil (22, 23) symétriques par rapport au centre du cylindre (8) suivent la fonction mathématique d'un polynôme du 5ème degré, qui présente, au centre du cylindre (8) et au bord de la zone de référence la hauteur de profil 0.
  13. Cage de laminage (1, 1', 1") selon la revendication 6, caractérisée
    en ce que pour une des deux positions de déplacement pouvant être choisies librement, les hauteurs de profil de toutes les puissances sont mises à 0 pour forcer un complément complémentaire des contours de cylindre dans cette position de déplacement.
  14. Cage de laminage (1, 1', 1") selon la revendication 13, caractérisée
    en ce que la position de déplacement choisie pour le profil 0 se situe également en dehors de la zone de déplacement réelle.
  15. Cage de laminage (1, 1', 1") selon l'une quelconque des revendications 6 à 14, caractérisée
    en ce que les coefficients pouvant être choisis librement pour les proportions linéaires sur un profil de cylindre de chaque paire cylindre (P1, P2, P3) sont choisis de manière telle que les axes des deux cylindres de la paire de cylindres (P1, P2, P3) sous la charge de laminage tournent parallèlement aux axes des cylindres sur lesquels ils s'appuient.
  16. Cage de laminage, en particulier cage sexto (1'), selon l'une quelconque des revendications 6 à 15, caractérisée
    en ce que les cylindres intermédiaires (3) pouvant être déplacés sont pourvus d'un profil (31, 31') qui produit, dans la fente de laminage (6) le polynôme avec un maximum de profil central (20, 21) et les cylindres de travail (2) pouvant être déplacés sont pourvus d'un profil (32, 32') qui produit dans la fente de laminage (6) le polynôme résiduel (22, 23) avec deux maximums situés symétriquement par rapport au centre du cylindre (8).
EP04798032A 2003-12-23 2004-11-22 Procede et cage de laminoir pour influer de maniere multiple sur des profils Active EP1703999B1 (fr)

Applications Claiming Priority (3)

Application Number Priority Date Filing Date Title
DE10361490 2003-12-23
DE102004020132A DE102004020132A1 (de) 2003-12-23 2004-04-24 Verfahren und Walzgerüst zur mehrfachen Profilbeeinflussung
PCT/EP2004/013214 WO2005065853A2 (fr) 2003-12-23 2004-11-22 Procede et cage de laminoir pour influer de maniere multiple sur des profils

Publications (2)

Publication Number Publication Date
EP1703999A2 EP1703999A2 (fr) 2006-09-27
EP1703999B1 true EP1703999B1 (fr) 2008-11-19

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US (1) US8210015B2 (fr)
EP (1) EP1703999B1 (fr)
JP (1) JP4682150B2 (fr)
KR (1) KR101146928B1 (fr)
CN (1) CN1898036B (fr)
AT (1) ATE414573T1 (fr)
AU (1) AU2004311504B2 (fr)
BR (1) BRPI0418012A (fr)
CA (1) CA2547957C (fr)
DE (2) DE102004020132A1 (fr)
EG (1) EG24833A (fr)
ES (1) ES2317072T3 (fr)
MY (1) MY135939A (fr)
RU (1) RU2353445C2 (fr)
TW (1) TWI322045B (fr)
WO (1) WO2005065853A2 (fr)

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WO2010118862A2 (fr) * 2009-04-17 2010-10-21 Sms Siemag Ag Procédé de fourniture d'au moins un cylindre de travail pour le laminage d'un produit laminé

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CN100333845C (zh) * 2004-08-30 2007-08-29 宝山钢铁股份有限公司 一种辊形设计方法和抑制高次浪形的轧辊
DE102007031333A1 (de) * 2007-07-05 2009-01-15 Siemens Ag Walzen eines Bandes in einer Walzstraße unter Nutzung des letzen Gerüsts der Walzstraße als Zugverringerer
CN102641892B (zh) * 2012-04-28 2014-07-02 北京科技大学 兼顾热轧不锈钢二次和高次浪形工作辊辊形的设计方法
US10357903B2 (en) 2012-12-06 2019-07-23 Scivax Corporation Roller-type pressurization device, imprinter, and roller-type pressurization method
CN104209339B (zh) * 2013-05-30 2016-08-10 宝山钢铁股份有限公司 一种利用粗轧逆道次立辊辊缝测量进行板坯宽度控制的方法
US10421218B2 (en) * 2014-06-03 2019-09-24 Scivax Corporation Roller-type depressing device, imprinting device, and roller-type depressing method
RU2690580C2 (ru) * 2015-03-16 2019-06-04 Смс Груп Гмбх Способ изготовления металлических полос
EP3124130A1 (fr) 2015-07-28 2017-02-01 Primetals Technologies Austria GmbH Meule de cylindre destinee a l'evitement cible de quarts d'onde
CN105618487B (zh) * 2016-01-27 2017-07-25 山西太钢不锈钢股份有限公司 一种均压精轧支承辊辊形设计方法
JP6813101B2 (ja) * 2017-10-31 2021-01-13 東芝三菱電機産業システム株式会社 圧延スタンドのロール摩耗分散方法および圧延システム
CN114769326B (zh) * 2022-03-25 2023-05-30 北京首钢股份有限公司 热轧辊缝轮廓构建方法及系统

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US4519233A (en) * 1980-10-15 1985-05-28 Sms Schloemann-Siemag Ag Roll stand with noncylindrical rolls
DE3213496A1 (de) 1982-04-10 1983-10-20 SMS Schloemann-Siemag AG, 4000 Düsseldorf Walzgeruest mit axial verschiebbaren walzen
DE3245090A1 (de) * 1982-12-06 1984-06-07 SMS Schloemann-Siemag AG, 4000 Düsseldorf Verfahren und einrichtung zum walzen von metallbaendern
JPS61279304A (ja) * 1985-06-05 1986-12-10 Ishikawajima Harima Heavy Ind Co Ltd 圧延機
DE3620197A1 (de) * 1986-06-16 1987-12-17 Schloemann Siemag Ag Walzwerk zur herstellung eines walzgutes, insbesondere eines walzbandes
DE3712043C2 (de) * 1987-04-09 1995-04-13 Schloemann Siemag Ag Walzgerüst mit axial verschiebbaren Walzen
EP0543014B2 (fr) 1991-05-16 2004-10-27 JFE Steel Corporation Laminoir a six etages
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DE4309986A1 (de) * 1993-03-29 1994-10-06 Schloemann Siemag Ag Verfahren und Vorrichtung zum Walzen eines Walzbandes
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IT1310776B1 (it) * 1999-09-14 2002-02-22 Danieli Off Mecc Procedimento di controllo del profilo del nastro in una gabbiadi laminazione per nastri e/o lamiere
DE10037004B4 (de) * 2000-07-29 2004-01-15 Sms Demag Ag Walzgerüst für bandkantenorientiertes Verschieben der Zwischenwalzen in einem 6-Walzen-Gerüst
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WO2010118862A2 (fr) * 2009-04-17 2010-10-21 Sms Siemag Ag Procédé de fourniture d'au moins un cylindre de travail pour le laminage d'un produit laminé
DE102010014867A1 (de) 2009-04-17 2010-11-18 Sms Siemag Ag Verfahren zum Bereitstellen mindestens einer Arbeitswalze zum Walzen eines Walzguts
WO2010118862A3 (fr) * 2009-04-17 2010-12-09 Sms Siemag Ag Procédé de fourniture d'au moins un cylindre de travail pour le laminage d'un produit laminé
CN102395434A (zh) * 2009-04-17 2012-03-28 Sms西马格股份公司 用于提供至少一个用于轧制轧件的工作辊子的方法
CN102395434B (zh) * 2009-04-17 2014-03-26 Sms西马格股份公司 用于提供至少一个用于轧制轧件的工作辊子的方法

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Publication number Publication date
EP1703999A2 (fr) 2006-09-27
CN1898036A (zh) 2007-01-17
AU2004311504A1 (en) 2005-07-21
CN1898036B (zh) 2011-03-30
RU2006126713A (ru) 2008-01-27
US8210015B2 (en) 2012-07-03
DE502004008503D1 (de) 2009-01-02
BRPI0418012A (pt) 2007-04-17
EG24833A (en) 2010-09-29
AU2004311504B2 (en) 2010-11-18
MY135939A (en) 2008-07-31
US20070240475A1 (en) 2007-10-18
JP4682150B2 (ja) 2011-05-11
KR101146928B1 (ko) 2012-05-22
TWI322045B (en) 2010-03-21
CA2547957C (fr) 2011-01-11
RU2353445C2 (ru) 2009-04-27
ES2317072T3 (es) 2009-04-16
WO2005065853A3 (fr) 2006-11-30
TW200526335A (en) 2005-08-16
WO2005065853A2 (fr) 2005-07-21
CA2547957A1 (fr) 2005-07-21
KR20060125819A (ko) 2006-12-06
DE102004020132A1 (de) 2005-07-28
JP2007515296A (ja) 2007-06-14
ATE414573T1 (de) 2008-12-15

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