EP0238377A1 - Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen - Google Patents

Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen Download PDF

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Publication number
EP0238377A1
EP0238377A1 EP87400319A EP87400319A EP0238377A1 EP 0238377 A1 EP0238377 A1 EP 0238377A1 EP 87400319 A EP87400319 A EP 87400319A EP 87400319 A EP87400319 A EP 87400319A EP 0238377 A1 EP0238377 A1 EP 0238377A1
Authority
EP
European Patent Office
Prior art keywords
cylinders
cylinder
chock
support
rolling mill
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP87400319A
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English (en)
French (fr)
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EP0238377B1 (de
Inventor
Jean Perret
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Clecim SAS
Original Assignee
Clecim SAS
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
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Application filed by Clecim SAS filed Critical Clecim SAS
Publication of EP0238377A1 publication Critical patent/EP0238377A1/de
Application granted granted Critical
Publication of EP0238377B1 publication Critical patent/EP0238377B1/de
Anticipated expiration legal-status Critical
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Classifications

    • 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
    • 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
    • B21B37/42—Control of flatness or profile during rolling of strip, sheets or plates using a combination of roll bending and 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
    • B21B13/001—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
    • B21B2203/00—Auxiliary arrangements, devices or methods in combination with rolling mills or rolling methods
    • B21B2203/36—Spacers
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/24—Roll wear
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/02—Roll bending; vertical bending of rolls
    • B21B2269/04—Work roll bending
    • 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
    • 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 subject of the invention is a method for adjusting the profile of cylinders which can be moved axially in a rolling mill and also covers the rolling mill which has been improved for implementing the method.
  • a rolling mill comprises, inside a support cage, at least two working rolls resting, along a rolling plane, on at least two supporting rolls.
  • the cylinders are carried at their two ends by means of bearings, in chocks mounted mobile, parallel to the rolling plane, in windows provided on the sides of the support cage.
  • "quarto" rolling mills comprising two working rolls, each resting on a support cylinder and so-called “sexto” rolling mills in which intermediate rolls are interposed between the support rolls and the working rolls.
  • the axes of the cylinders are placed in the rolling plane, generally vertical, but it is also possible to support each working cylinder on a larger number of intermediate and / or support cylinders placed symmetrically on either side. other of the rolling plan.
  • a bending 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.
  • a distinction is made between the positive bending corresponding to a spacing of the chocks on either side of the plane of the product and the negative bending corresponding to an approximation of the chocks.
  • the bending device consists, for each chock, of two sets of jacks placed symmetrically on either side of the plane of the lami swimming and each acting, in the desired direction, on a support part integral with the chock. Normally, 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 over the bearings.
  • the rolling mill stand is symmetrical with respect to a median plane perpendicular to the rolling plane and which corresponds to that of the rolled product. Normally the cylinders are therefore centered on this plane with respect to which the chocks are arranged symmetrically.
  • the torque is generally applied to a single pair of cylinders, for example the working cylinders, and transmitted to the corresponding support cylinders by friction.
  • the subject of the invention is a new device which, without substantially modifying the constitution of the rolling mill, makes it possible at the same time to bend and to move axially the working rolls or the intermediate rolls.
  • the cambering force is exerted by means of fixed jacks bearing, on one side on a support integral with the cage and on the other on a sliding face formed on the corresponding chock parallel to the axial direction of movement, and, to achieve the camber of the displaceable cylinder, the displacement of the latter is measured at all times relative to the centering position of the cylinder on the median plane of the product and is continuously adjusted for each chock, the individual pressure exerted by each cylinder as a function of the measured offset and the position at the same instant of the cylinder considered with respect to the median plane of the bearing so that, in each choke, the result of the cambering forces exerted by the all cylinders remain directed at all times along the median plane of the bearing.
  • the invention also covers an improved rolling mill for implementing the method in which the camber cylinders of each chock are mounted on a fixed support integral with the cage and bear, in the direction of the cambering force, on a sliding face formed on the chock, parallel to the axial direction of movement; in addition, the rolling mill is associated with a balancing device comprising a means for measuring the offset of the cylinder considered relative to its centering position relative to the median plane of the product and means for individual adjustment, at each instant, of the pressure exerted by each cambering cylinder, as a function of the measured offset and of the position, at the same instant of the cylinder considered with respect to the median plane of the bearing, so that the result of the cambering forces exerted by all the cylinders remains directed, at each instant according to the median plane of the bearing.
  • a balancing device comprising a means for measuring the offset of the cylinder considered relative to its centering position relative to the median plane of the product and means for individual adjustment, at each instant, of the pressure exerted
  • each displaceable 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 sets, 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 a means for individual adjustment of the fluid pressure with maintenance of equal flow rates in all branches.
  • the means for individually adjusting 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. at pressures as a function of the offset measured and displayed on the calculation means and of the respective positions in cylinders supplied by the branch considered.
  • each chock can be associated with positive and negative bending means each comprising two opposite sets of at least two jacks acting respectively in the direction of spacing of the cylinders for positive bending and in the direction of approximation for negative cambering.
  • each block consists of a solid support piece comprising a projecting central part framed by two longitudinal recesses in which the support ears of the chock engage, these being each provided with a continuous sliding face parallel to the axis and said sliding faces are placed opposite the lateral faces of the central part on which are arranged opposing bores two by two along an axis parallel to the rolling plane and each forming a cylinder body in which slides a piston secured to a rod opening into the corresponding recess to rest on the sliding surface of the chock.
  • the rods of the jacks are capped by bearing pads on the sliding surfaces associated with columns for taking up the axial forces slidingly mounted, parallel to the rod of the jack, in guide bores made in the hydraulic block, elastic washers being advantageously interposed between the support pads and the sliding surfaces.
  • FIG 1 there is shown schematically a quarto rolling mill comprising two working rolls 1 and 1 ⁇ and two support rollers 2 and 2 ⁇ .
  • the axes of the cylinders are parallel and arranged along a rolling plane P1 passing through the contact generators.
  • the rolled product 20 passes between the working rolls 1 and 1 ⁇ and its median plane P2 corresponding to the plane of symmetry of the whole of the rolling mill stand and in particular of the support rolls 2 and 2 ⁇ .
  • the cylinders are all aligned and centered on the plane P2.
  • the working rolls 1 and 1 ⁇ can be moved axially relative to the centering position so that their respective transverse plane of symmetry is offset on one side or the other by relation to the median plane P2.
  • an axial displacement force F1 is applied to the working rolls 1 and 1 ⁇ .
  • bending forces F2 are applied to the ends of the shafts of the working cylinders 1 and 1 ⁇ , by means of their chocks so as to bend a 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.
  • the working cylinder 1 is provided at its ends with centered pins 11, by means of bearings 12 inside chocks 3 forming bearing bodies and mounted slidingly, parallel to the rolling plane P1, in windows 40 provided in the two uprights 4 of the rolling stand.
  • each chock 3 of the working cylinder is provided for this purpose with sliding faces 31 parallel to the rolling plane P1 and which can slide along corresponding faces 51 formed inwards on support pieces 5 fixed in the windows 40 of the stand 4 of the rolling mill.
  • Each support part 5 is common for the two working rolls 1 and 1 ⁇ and comprises longitudinal recesses 52 placed on either side of a projecting central part 53 and limited towards the outside by lateral parts 54, the guide faces 51 being formed at the end of the central part 53 and of the lateral parts 54.
  • the chocks 3 and 3 ⁇ of the working rolls 1 and 1 ⁇ are provided with support parts or "ears" 32, 32 ⁇ which engage in the corresponding recesses 52, 52 ⁇ of the support part 5 and are provided with continuous planar faces 33, 34 facing the lateral faces 55, 56, respectively of the central part 53 and of the lateral part 54.
  • the rolling mill is provided with positive and negative bending means.
  • the positive cambering means consist, for each chock, of two pairs of jacks 6 placed on either side of the median plane P1 in the central parts 53 of the support parts 5, the camber cylinders of the two working cylinders 1 and 1 ⁇ being opposite in pairs, forming two rows centered in planes P3, P4 parallel to the median plane P2 and axially spaced apart one from the other by a distance a (figure 2).
  • FIG. 3 is a section through the axial plane of a line, for example P3.
  • central part 53 of the support part 5 are therefore provided, for each row of jacks, two opposite bores 57, 57 ⁇ centered on the axis 60 of the positive bending jacks 6 and 6 ⁇ and opening respectively on the lateral faces 55, 55 ⁇ of the central part 53.
  • the two bores 57, 57 ⁇ are separated by a central partition 58 and constitute the bodies of the two jacks 6 and 6 ⁇ inside which pistons 61, 61 ⁇ slide extended by rods 62, 62 ⁇ which pass through partitions 63, 63 ⁇ sealingly closing the bores 57, 57 ⁇ .
  • the two actuator chambers thus formed, inside each bore 57, 57 ⁇ can be supplied by a hydraulic circuit not shown, the support part 5 thus constituting a real hydraulic block.
  • each pad 64 has a diamond shape comprising two points on which are fixed the ends of guide columns 65 slidably mounted, parallel to the axis 60 of the jack in bores made in the central part 53. Furthermore, the shoe 64 rests on the face 34 of the support part 32 of the chock 3 via a pad 66 and an elastic washer 67.
  • each chock 3, 3 ⁇ is also associated with negative cambering cylinders 7, 7 ⁇ placed in bores 59, 59 ⁇ formed in the lateral parts 54, 54 ⁇ of the support piece (5) and opening onto the lateral faces 56, 56 ⁇ .
  • Each bore 59 constitutes the body of the jack 7 inside which slides a piston 71 secured to a rod 72 which passes in leaktight manner through a partition 73 closing the bore 59 inside which the piston 71 therefore limits two chambers of cylinders connected to a hydraulic circuit arranged in the support part 5.
  • each chock 3 can slide parallel to the axis 10 of the cylinder along the guide faces 51 of the support piece 5.
  • the two chocks 3 of each cylinder 1 are secured to the latter in the axial direction by means of caps 13 for closing the bearing cages 12, the latter being liable to withstand axial forces, for example tapered bearings. In this way, the two chocks 3 of each cylinder 1 follow the movements of axial displacement of the cylinder.
  • Several devices for axial displacement of the cylinders are already known, which therefore need not be described in detail. It is possible, for example, to use a jack bearing on a lifting beam making it possible to apply the axial displacement force on the two sides of the chock 3.
  • the displaced cylinder 1 is a driving cylinder
  • two displacement cylinders 42 supplied in synchronism placed symmetrically on either side of the drive means 43 in rotation of the cylinder 1 and bearing on the supports 32 of the corresponding chock 3, each jack 42 being centered in a plane parallel to the rolling plane and passing through the axes of the camber jacks 6 and 7 and supplying it in synchronism .
  • the offset of the displaced cylinder 1 is measured relative to the median plane P1 by means of a displacement sensor 44 made up of two parts sliding relative to each other, fixed, for example on the two parts of one of the cylinders 42 and providing an analog signal proportional to the offset of the working cylinder relative to the centering position in the median plane of the product and of sign corresponding to the direction of the offset.
  • This signal is used for balancing the pressures in the cambering cylinders by means of a device 8 shown diagrammatically in FIG. 5.
  • a displaceable cylinder 1 and its two cambering devices each consisting of two sets of jacks placed in hydraulic blocks 5a, 5b, 5 ⁇ a, 5 ⁇ b each set comprising two jacks 6a, 66a and 6b, 66b, (6 ⁇ a, 66 ⁇ a, 6 ⁇ b, 66 ⁇ b).
  • the four jacks are centered in two transverse planes P3 and P4 spaced from each other by a distance a.
  • the hydraulic blocks 5a, 5b and 5 ⁇ a, 5 ⁇ b of the two chocks are connected by a single supply circuit 80 to a source of pressurized fluid not shown.
  • the circuit 80 is divided into two branches 81 and 82.
  • the branch 81 supplies the jacks 6a, 6b, 6 ⁇ a, 6 ⁇ b in parallel with the two wires P3 and P ⁇ 3 while the branch 82 supplies the jacks 66a, 66b, 66 ⁇ a, 66 ⁇ b in parallel of the two queues P4 and P ⁇ 4.
  • the hydraulic circuit is designed so that all of the cylinders are supplied with the same flow rate 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 by maintaining a constant flow there.
  • the sensor 44 for the axial displacements of the cylinder 1 provides an analog signal proportional to the displacement which is applied to a computing unit 85. From the signals received, the latter develops the pressure setpoints S1 and S2 applied to the inputs 84 of the sensors 83 of the two branches 81 and 82 according to a law programmed in advance to ensure a pressure distribution such that the result of the thrust forces applied by the camber cylinders in the planes P3 and P4 always remains directed at each instant following the median plane of the corresponding bearings. In this way, as shown in FIG.
  • the two rows of cylinders P3 and P4 are not necessarily symmetrical with respect to the median plane P5 of the bearing and this makes it possible to arrange the jacks 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, electrical or even mechanical (cam, lever 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 in diameter due to wear in the limit of the stroke of the cylinders.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Control Of Metal Rolling (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
EP87400319A 1986-02-14 1987-02-12 Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen Expired - Lifetime EP0238377B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8602044 1986-02-14
FR8602044A FR2594359B1 (fr) 1986-02-14 1986-02-14 Procede de reglage du profil de cylindres deplacables dans un laminoir et laminoir perfectionne pour la mise en oeuvre du procede

Publications (2)

Publication Number Publication Date
EP0238377A1 true EP0238377A1 (de) 1987-09-23
EP0238377B1 EP0238377B1 (de) 1990-04-18

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ID=9332146

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EP87400319A Expired - Lifetime EP0238377B1 (de) 1986-02-14 1987-02-12 Steuerung von Walzendurchbiegung in einem Walzgerüst mit axial verschiebbaren Walzen

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Country Link
US (1) US4773246A (de)
EP (1) EP0238377B1 (de)
DE (1) DE3762320D1 (de)
FR (1) FR2594359B1 (de)

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2611541A1 (fr) * 1987-02-27 1988-09-09 Clecim Sa Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement
EP0340504A2 (de) * 1988-05-06 1989-11-08 Sms Schloemann-Siemag Aktiengesellschaft Biege- und Ausbalanciervorrichtung für axial verschiebbare Walzen eines Walzgerüstes
FR2648372A1 (fr) * 1989-06-19 1990-12-21 Clecim Sa Procede de changement de configuration d'un laminoir et installation de laminage pour la mise en oeuvre du procede

Families Citing this family (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US5592846A (en) * 1992-08-07 1997-01-14 Kawasaki Steel Corporation Endless hot rolling method
DE19500336A1 (de) * 1995-01-07 1996-07-11 Schloemann Siemag Ag Verfahren zur Regelung des Walzspaltprofils
IT1280176B1 (it) * 1995-05-25 1998-01-05 Danieli Off Mecc Blocco di curvatura-bilanciamento per gabbia di laminazione a quarto per nastri o lamiere
DE19618712B4 (de) * 1996-05-09 2005-07-07 Siemens Ag Regelverfahren für ein Walzgerüst zum Walzen eines Bandes
US5752404A (en) * 1996-12-17 1998-05-19 Tippins Incorporated Roll shifting system for rolling mills
DE19730262C1 (de) * 1997-07-09 1998-10-22 Mannesmann Ag Verfahren zum Walzen von Flachmaterial und Band
IT1297585B1 (it) * 1997-12-24 1999-12-17 Danieli Off Mecc Blocco di curvatura per gabbia di laminazione a quarto
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
WO2021205548A1 (ja) * 2020-04-07 2021-10-14 Ｐｒｉｍｅｔａｌｓ Ｔｅｃｈｎｏｌｏｇｉｅｓ Ｊａｐａｎ 株式会社 圧延機、圧延機の製造方法、および圧延機の改造方法

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3334506A (en) * 1964-04-24 1967-08-08 Nat Steel Corp Rolling mill
US3398564A (en) * 1963-07-29 1968-08-27 Achenbach Sohne G M B H Arrangement for counter-balancing the working rollers of a roller stand
EP0067040A2 (de) * 1981-06-03 1982-12-15 Hitachi, Ltd. Walzwerk
EP0084927A1 (de) * 1982-01-06 1983-08-03 Hitachi, Ltd. Walzwerk

Family Cites Families (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS525304B2 (de) * 1972-07-07 1977-02-12
US3943742A (en) * 1973-08-24 1976-03-16 Hitachi, Ltd. Rolling mill
JPS6018210A (ja) * 1983-07-13 1985-01-30 Ishikawajima Harima Heavy Ind Co Ltd 圧延機

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3398564A (en) * 1963-07-29 1968-08-27 Achenbach Sohne G M B H Arrangement for counter-balancing the working rollers of a roller stand
US3334506A (en) * 1964-04-24 1967-08-08 Nat Steel Corp Rolling mill
EP0067040A2 (de) * 1981-06-03 1982-12-15 Hitachi, Ltd. Walzwerk
EP0084927A1 (de) * 1982-01-06 1983-08-03 Hitachi, Ltd. Walzwerk

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
PATENT ABSTRACTS OF JAPAN, vol. 9, no. 135 (M-386)[1858], 11 juin 1985; & JP-A-60 18 210 (ISHIKAWAJIMA HARIMA JUKOGYO K.K.) 30-01-1985 *

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2611541A1 (fr) * 1987-02-27 1988-09-09 Clecim Sa Dispositif de reglage du profil et de repartition d'usure de cylindres dans un laminoir a cylindres deplacables axialement
EP0283342A1 (de) * 1987-02-27 1988-09-21 Clecim Walzgerüst mit axial verschiebbaren Walzen und Verfahren zum Steuern des Walzenprofils
EP0340504A2 (de) * 1988-05-06 1989-11-08 Sms Schloemann-Siemag Aktiengesellschaft Biege- und Ausbalanciervorrichtung für axial verschiebbare Walzen eines Walzgerüstes
EP0340504A3 (en) * 1988-05-06 1990-06-06 Sms Schloemann-Siemag Aktiengesellschaft Device for bending and balancing axial movable rolls of a rolling stand
FR2648372A1 (fr) * 1989-06-19 1990-12-21 Clecim Sa Procede de changement de configuration d'un laminoir et installation de laminage pour la mise en oeuvre du procede

Also Published As

Publication number Publication date
DE3762320D1 (de) 1990-05-23
US4773246A (en) 1988-09-27
EP0238377B1 (de) 1990-04-18
FR2594359A1 (fr) 1987-08-21
FR2594359B1 (fr) 1988-06-10

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