EP0100743B1 - Verfahren zum Kaltwalzen von Rohren mittels eines Pilgerwalzwerkes und Vorrichtung zur Durchführung des Verfahrens - Google Patents

Verfahren zum Kaltwalzen von Rohren mittels eines Pilgerwalzwerkes und Vorrichtung zur Durchführung des Verfahrens Download PDF

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Publication number
EP0100743B1
EP0100743B1 EP83420126A EP83420126A EP0100743B1 EP 0100743 B1 EP0100743 B1 EP 0100743B1 EP 83420126 A EP83420126 A EP 83420126A EP 83420126 A EP83420126 A EP 83420126A EP 0100743 B1 EP0100743 B1 EP 0100743B1
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EP
European Patent Office
Prior art keywords
blank
upstream
cam
advance
downstream
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Expired
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EP83420126A
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English (en)
French (fr)
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EP0100743A1 (de
Inventor
Pierre Peytavin
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Vallourec SA
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Vallourec SA
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Priority to AT83420126T priority Critical patent/ATE21636T1/de
Publication of EP0100743A1 publication Critical patent/EP0100743A1/de
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Publication of EP0100743B1 publication Critical patent/EP0100743B1/de
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B21/00—Pilgrim-step tube-rolling, i.e. pilger mills
    • B21B21/04—Pilgrim-step feeding mechanisms
    • B21B21/045—Pilgrim-step feeding mechanisms for reciprocating stands

Definitions

  • the present invention relates to a cold rolling process for the manufacture of tubes by means of a pilgrim step rolling mill.
  • This rolling mill comprises, in a known manner, fluted rolls mounted in a movable roll-carrying cage which performs a reciprocating movement along the axis of the tube blank which is periodically advanced, the rolls being driven in rotation by a known means.
  • a mandrel is arranged in the axis of the blank which is thus laminated between the cylinders and the mandrel.
  • French patent n ° 1 602 013 describes a vocational step rolling mill comprising devices which imprint on the preform periodic movements of advance along its axis and of rotation about this same axis, this when the rolls are in neutral and release the draft at the end of their alternative back-and-forth journey.
  • the rotational movements are printed on the blank by tube clamps arranged on either side of the cylinder holder cage.
  • the periodic and discontinuous movements of advance are printed on the blank by an articulated pusher, mounted on a carriage which supports the rear of the blank and advances continuously towards the cage.
  • this lever in the form of a lever, is articulated about an axis.
  • a cam controls the axial advance movement of the blank by imparting to the pusher a periodic tilting movement synchronized with the reciprocating movement of the cylinder carrier cage, this when the cage is in the vicinity of the dead center. end of travel of one of its outward or return movements and the cylinders release the blank.
  • the upstream side designates the inlet side of the blank to be laminated in the cylinder cage, and the downstream side, the outlet side of the tube of the cage after reduction of its section by rolling between the rolls.
  • the upstream-downstream movement of the cage and the cylinders is designated by the forward path and by the return path, the downstream-upstream movement along the axis of the blank.
  • Laminating according to the technique described in patent FR 1 602 013, is usually carried out only during the outward journey, either from upstream to downstream of the cylinders, the grooves of the cylinders being designed to allow the free passage of the blank to be laminated for a short time near the upstream dead center.
  • the rolls efficiently work the metal by deforming it only during the outward journey of the cage.
  • the cylinders only pass over an already rolled product, without performing any deformation work.
  • FR 2 442 674 teaches, however, that it is advantageous to advance and rotate the blank only when it is released from the grip of the two cylinders, while they are at the end of the race in the vicinity of the downstream dead center.
  • This patent further teaches that the deformation of the blank is distributed between the outward and return paths of the cylinders although the blank is not advanced in the vicinity of the upstream dead center.
  • FR 2 463 646 teaches that, in order to obtain the highest possible yield, the blank is advanced and rotated in the vicinity of each of the two dead centers upstream and downstream of the back and forth movement of the cylinders, the advance upstream being different from the downstream advance.
  • This patent teaches that the maximum advance of the blank can, depending on the circumstances, be done either upstream or downstream.
  • This document does not, however, teach the criteria on which one must base oneself to define the upstream advance and the downstream advance. It also does not teach the means of achieving these advances, nor does it teach the means making it possible to ensure, under satisfactory conditions, rolling during the return journey.
  • the cold rolling process of tubes which is the subject of the present invention, relates to a pilgrim step rolling mill, comprising a cylinder-carrying cage driven in a cyclic movement back and forth, in which one advances the tube blank in the vicinity of each of the upstream and downstream dead centers. It is characterized in that the recoil of the upstream part of the blank is allowed for the entire duration of the rolling carried out during the return path of the cylinder holder cage.
  • the ratio between the downstream advance and the upstream advance is substantially equal to a, a being the coefficient of elongation of the blank produced by means of the rolling mill.
  • the invention also relates to a device for controlling the advance of a tube blank on a cold rolling mill with vocational steps in which this advance is achieved by means of a cam which makes a revolution while the cage is carrying cylinders back and forth, this cam comprising two bosses of diametrically opposite unequal thicknesses which act on the blank by means of a transmission means, one of the bosses being wedged to act on the blank when the cylinder holder cage is in the vicinity of the upstream dead center and the other boss being wedged to act on the blank when the cylinder holder cage is in the vicinity of the downstream dead center, the gripper device tubes allowing the backward movement of the upstream part of the blank for the entire duration of the return path of the cylinder holder cage.
  • the thinner boss is preferably wedged to act on the rear of the blank in the vicinity of the upstream dead center of the cylinder holder cage.
  • any blank undergoes, in the rolling direction, an elongation proportional to its thinning.
  • the outward path of the roll cage does not pose any problem.
  • a pusher such as, for example, that described in FR 1 602 013, or any other pusher of known type, advances the whole of the blank by an optimal length that 'is designated by " ⁇ 1".
  • the blank itself lengthens by a length (a-1) 01 a being the coefficient of elongation.
  • This coefficient a is defined as being the ratio of the length of the tube after rolling to the length of the blank before rolling.
  • the blank With regard to the second rolling phase, which comprises moving the blank to the downstream dead center, then the return path of the roll cage, it appeared that, in order to obtain an optimal yield from the rolling mill, it was desirable to do substantially the same rolling job as in the first phase.
  • the rear of the blank is effectively advanced by a residual length of approximately ⁇ 1 substantially equal to its advance during the first rolling phase.
  • the invention also relates to a device for controlling the advance of the blank for implementing the method which has just been described.
  • This device makes it possible, under particularly favorable conditions, to carry out the periodic advance of the blank according to the laws which have just been established.
  • It comprises, in known manner, a pusher in the form of a tilting lever, similar to a rocker arm, which is advantageously mounted on a carriage such as, for example, that described in FR 1 602 013.
  • This carriage supports the rear of the draft while advancing at a practically constant speed in the direction of the cylinder holder cage.
  • the tilting of the pusher is controlled by a cam which rotates one complete revolution while the cylinder holder cage goes back and forth.
  • the particularity of the device according to the invention consists in that the cam comprises two diametrically opposite bosses, which each control a rocking movement of the pusher and, consequently, a movement in advance of the blank.
  • the cam is calibrated so that the advances of the blank occur when the cylinder cage is located in the vicinity of each of the two upstream and downstream dead centers.
  • the thickness of the first boss is such that the corresponding tilting of the pusher transmits to the blank an optimal advance of ⁇ 1 in the vicinity of the upstream dead center, before the outward journey of the cylinder holder cage.
  • This value ⁇ 1 is determined in a known manner as a function of various parameters such as: quality of the metal, dimensions of the blank and of the tube to be produced, characteristics of the grooves of the cylinders and of the mandrel, or others.
  • the second boss diametrically opposite on the cam, is substantially as thick as that which allows the pusher to transmit to the blank an advance substantially equal to ⁇ 1 in the vicinity of the downstream dead center, before the return path of the carrier cage. -cylinders.
  • the thickness, e 1 of the first boss is substantially k ⁇ 1 (1- ⁇ ⁇ t ) and the thickness e 2 of the second boss of k ⁇ 1 ( ⁇ - ⁇ ⁇ t ).
  • FIG. 1 a cold rolling mill with a design similar to that which is, for example, described in FR 1 602 013.
  • the cylinder holder cage (1) is shown in phantom.
  • the connecting rods (2-2 ') give it an alternating back and forth movement along the axis (XX') of the blank (3).
  • a carriage (4) comprising a pusher (5) shown in more detail in FIG. 2, supports the rear of the blank (3).
  • This carriage (4) is driven by a screw (6) which makes it move continuously and regularly at the speed ⁇ 1 / At in the direction of the cage (1), that is to say in the direction of the arrow (F) defining the upstream-downstream direction.
  • Tube clamps (7-7 ') hold the blank (3) upstream and downstream of the cage (1).
  • these tube clamps (7-7 ') periodically rotate the blank (3) around its axis (XX') by an angle of, for example, 60 °, this when the cage ( 1) arrives at one of its dead centers at the end of the outward or return journey.
  • the blank (3) slides in the clamps (7-7 ') when the pusher (5) advances it relative to the carriage (4).
  • a rod clamp (8) located at the rear of the rolling mill, maintains an internal mandrel (9) and periodically rotates it in synchronism with the rotations of the blank (3). This mandrel does not undergo any axial displacement.
  • the blank (3) is pushed forward by the combination on the one hand, of the continuous movement of the carriage (4) driven by the screw (6) at constant speed A1 / ⁇ t and, on the other hand , periodic thrust of the fingers (14) of the plunger (5) which oscillates around the axis (15).
  • the pusher (5) is controlled by a roller rod (16) and a cam (17) acting in opposition to the sleeve (10).
  • the cam (17) has two diametrically opposite bosses (18-19), as shown in FIG. 3.
  • the thickness (e 1 ) of the boss (18) measured beyond the minimum radius (r) of the cam is determined so that, when this boss acts on the pusher (5) via the rod to roller (16), this pusher moves the blank (3) upstream via the sleeve (10) and the sleeve (11) of length ⁇ 1 when the cage is in the vicinity of the upstream dead center .
  • the thickness (e 2 ) of the boss (19) measured beyond this same radius (r) is determined so that, via the pusher (5), this boss causes an advance of the blank by ⁇ 1, when the cylinder carrier cage is in the vicinity of the downstream dead center.
  • the thickness (e1) of the boss (18) is substantially k ⁇ 1 (1 - ⁇ ⁇ t ) and the thickness (e 2 ) of the boss (19) is substantially k ⁇ 1 (a ⁇ ⁇ t ).
  • the profile of the cam (17) corresponds substantially to the profile of the staircase curve (0 C 2 C 3 C 4 C 5 ...) of Figure 5, which represents the displacement of the rear part of the blank in function time.
  • the cam (17) can be traced by giving it, for the thickness of the bosses, the difference between the ordinates of the curve (OC 2 C 3 C 4 C 5 ...) and the ordinates of the straight line (OY) representing the displacement of the carriage (4) along the axis (XX ') at a constant speed ⁇ ⁇ t .
  • the angular points of the curve (0 C 2 C 3 C 4 C 5 ...) are obviously rounded on the cam (17).
  • the mandrel (9) is rotated around the axis (XX ') during the neutral time ⁇ before each rolling pass back or forth, this at the same time as the blank (3) but is never moved along the axis (XX ').
  • this mandrel (9) has a cylindrical rear part and a front part which tapers in accordance with a profile known per se to best conform to the deformation of the blank (3) during of a rolling pass.
  • the plane orthogonal to the axis XX ', along which the cylindrical part and the thinned front part of the mandrel (9) are connected is here marked at (AA').
  • the blank (3) is pressed against the mandrel (9) by the last return phase as shown in FIG. 4a.
  • the reference (C 1 ) is in the marked plane (BB ').
  • the blank (3) is advanced by the carriage (4) and the pusher. (5) of length ⁇ 1, this for the time available at the upstream dead center ⁇ 1 of the cylinder holder cage (1).
  • the reference (C 1 ) comes at (C 2 ) at a distance ⁇ 1 downstream from the plane (BB '), as shown in FIG. 4b.
  • the blank (3) detaches from the mandrel (9) as is particularly apparent near the plane (AA ') in Figure 4b.
  • the outward path either in the direction (F) of the cage (1), then thins the blank by lengthening it and pressing it against the mandrel (9), as shown in FIG. 4c.
  • the reference (C) remained in (C 3 ) at the same distance ⁇ 1 from the plane (BB ').
  • the point (D) of the blank (3) advanced in (D 3 ) at a distance aA1 from the front end (20) of the mandrel (9).
  • the front end of the blank does not move, as shown by the reference (D5) which does not move relative to (D 4 ).
  • the metal of the blank is however forced backwards and the mark (C) comes at (C 5 ) at a distance 2 ⁇ 1 downstream from the plane (BB '), as shown in FIG. 4e.
  • We can then start a new round-trip rolling cycle which will start with a new advance from the rear of the blank (materialized by point C) with a new length ⁇ l.
  • the backward movement of the rear of the blank (3) during the return path of the cage (1) is made possible by the control of the pusher (5) by the descending part (C 4 C 5 ) of the boss (19) of the cam (17).
  • the shape of the descending part (C 4 C 5 ) of this boss (19) corresponds to a recoil of the fingers (14) of the pusher (5) which allows the recoil of the sleeve (10) and of the sleeve (11) pushed by the rear end of the blank.
  • the shape of the cam (17) can easily be deduced from the diagram of FIG. 5 where, on the abscissa (OT), is plotted the time and, on the ordinate (OL), the advance from the rear of the blank materialized by the mark C.
  • the continuous advance of the carriage (4) along the axis (XX ') is materialized by the right (OY).
  • the slope of this line is ⁇ 1 / ⁇ t.
  • FIG. 6 represents the displacements of the front part of the blank as a function of time.
  • the scales used are the same as in FIG. 5.
  • the point (D 1 ) is confused with the origin 0.
  • the points (D 2 , D 3 , D 4 and D 5 ) correspond to the same instants as the points (C 2 , C 3 , C 4 , C 5 ) of FIG. 5. It can be seen that, during a complete cycle, the front (D) advances by 2 ⁇ 1, while the rear (C) advances by 2 ⁇ 1.
  • point (C) remains substantially stationary at (C 2 ), because the fingers (14) of the pusher (5) do not exert pressure on the sleeve (10). Indeed, the advance ⁇ 1 (1- ⁇ ⁇ t ) of the carriage (4) is compensated by the recoil of the fingers (14) corresponding to the descending part (C 2 C 3 ) of the boss (18). Simultaneously, point (D) advances from (D 2 to D 3 ) by a length ( ⁇ -1) ⁇ 1.
  • the circumferential speed at the bottom of the groove is greater than the translation speed and the cylinder tends, on the contrary, to drive the metal in the opposite direction from the direction of movement of the cage.
  • a very great advantage of the method and of the device according to the invention is that they make it possible to give the cam bosses the desired shape to accompany relative displacement of the rear of the blank relative to the carriage during travel paths. rolling.
  • a force limiting means such as a calibrated spring which can be inserted at a suitable point in the mechanical transmission between the rear of the and the cam.
  • This device can also be accommodated at the level of the drive means of the cam-carrying carriage.
  • Such an arrangement makes it possible to reduce the importance of the masses in movement, to shorten the mechanical transmissions and to reduce the clearances for the advance of the blank, compared to an arrangement according to which the cam system is mounted at a fixed station.
  • the advance modifications can be carried out easily by changing the cam or even by using a transmission comprising an amplitude adjustment.
  • a domestic pitch rolling mill is used for cold rolling capable of blanks with an outside diameter of between 70 and 140 mm, equipped with working rolls of 500 mm in diameter working at the rate of 120 round-trip cycles per minute.
  • a blank tube 80 mm in outside diameter and 8 mm thick is used.
  • This rolling mill is equipped with a feed system by means of a pusher controlled by a cam which performs one turn while the cylinder holder cage makes a round trip.
  • the working parameters are chosen to be a feed of the blank ⁇ 1 of 10 mm and an elongation coefficient a of 4.
  • This rolling mill is first used in a conventional manner, the cam comprising a single boss, and a single advance ⁇ 1 per cycle is thus produced at the upstream dead center.
  • the blank therefore advances by 1.2 m / min and 4.8 m / min of laminated tube is obtained.
  • the cam with a single boss is then replaced by a cam according to the invention comprising two bosses whose thickness ratios and profiles are determined in accordance with the invention, so as to allow an advance of the blank equal to ⁇ 1 at upstream neutral and equal to ⁇ 1 at downstream neutral. It is found, under these conditions, that by operating at the same rate of 120 cycles per minute, the blank advances by 2.4 m / min and we obtain 9.6 m / min of laminated tube.
  • the invention therefore makes it possible to double production without modifying the rate of operation of the cylinder holder cage.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Metal Rolling (AREA)
  • General Factory Administration (AREA)
  • Forging (AREA)
  • Shaping Metal By Deep-Drawing, Or The Like (AREA)
  • Control Of Metal Rolling (AREA)
  • Heat Treatment Of Steel (AREA)

Claims (14)

1. Verfahren zum Kaltwalzen von Rohren unter Verwendung eines Pilgerschrittwalzwerks mit einem Walzentragkäfig (1), der in einer zyklischen Hin- und Rückbewegung betätigt wird, bei der der Rohrrohling (3) in Nähe jedes der vorderen und hinteren Totpunkte vorgeschoben wird, dadurch gekennzeichnet, dass während der gesamten Dauer des beim Rückweg des Walzentragkäfigs (1) ausgeführten Walzens der Rücklauf des hinteren Teils des Rohlings ermöglicht wird.
2. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass das Verhältnis zwischen dem vorderen Vorschub und dem hinteren Vorschub im wesentlichen gleich a ist, wobei αder Längskoeffizient des Rohlings ist.
3. Verfahren nach Anspruch 1, dadurch gekennzeichnet, dass der Rücklauf des hinteren Teils des Rohrrohlings gegenüber einem festen Bezugspunkt im wesentlichen gleich dem effektiven Vorschub am hinteren Totpunkt multipliziert mit (a-1) ist.
4. Verfahren nach einem der Ansprüche 1 bis 3, dadurch gekennzeichnet, dass der Rücklauf des hinteren Teils des Rohlings kontrolliert wird.
5. Vorrichtung zur Durchführung eines Verfahrens zum Kaltwalzen von Rohren unter Verwendung eines Pilgerschrittwalzwerks mit einem Walzentragkäfig (1), der in einer zyklischen Hin-und Rückbewegung betätigt wird, wobei die Vorrichtung eine Steuerung des Vorschubs des Rohrrohlings (3) in Nähe jedes der hinteren und vorderen Totpunkte gestattet, dadurch gekennzeichnet, dass die Steuerung dieses Vorschubs mittels wenigstens eines Nockens (17) erfolgt, der eine Umdrehung ausführt, während der Walzentragkäfig (1) eine Hin- und Rückbewegung ausführt, wobei dieser Nocken zwei diametral gegenüberliegende Vorsprünge (18-19) von ungleicher Dicke hat, die über eine Übertragungseinrichtung axial auf den Rohling einwirken, wobei der eine der Vorsprünge so festgelegt ist, dass er auf den Rohling in dem Augenblick einwirkt, in dem sich der Walzentragkäfig in Nähe des hinteren Totpunkts befindet, während der andere so festgelegt ist, dass er auf den Rohling in dem Augenblick einwirkt, in dem sich der Walzentragkäfig in Nähe des vorderen Totpunktes befindet, und dass die Rohrklemmvorrichtung (7, 7') den Rücklauf des hinteren Teils des Rohlings während der gesamten Dauer des Rückwegs des Walzentragkäfigs (1 ) gestattet.
6. Vorrichtung nach Anspruch 5, dadurch gekennzeichnet, dass der Vorsprung (18) mit der geringeren Dicke so festgelegt ist, dass er auf den Rohling in Nähe des hinteren Totpunkts des Walzentragkäfigs einwirkt.
7. Vorrichtung nach Anspruch 5 oder 6, dadurch gekennzeichnet, dass der Nocken (17) mit einem Schlitten (4) fest verbunden ist, der sich während des Walzens mit konstanter Geschwindigkeit nach vorn bewegt.
8. Vorrichtung nach Anspruch 5, 6 oder 7, dadurch gekennzeichnet, dass der Nocken (17) über einen Drücker (5) auf den Rohling (3) einwirkt.
9. Vorrichtung nach Anspruch 8, dadurch gekennzeichnet, dass zwischen dem Nocken (17) und dem Drücker (5) eine Übertragungseinrichtung (16) angeordnet ist.
10. Vorrichtung nach Anspruch 8 oder 9, dadurch gekennzeichnet, dass der Drücker (5) oder die Übertragungseinrichtung (16) eine Amplitudeneinstellung aufweist.
11. Vorrichtung nach einem der Ansprüche 6 bis 10, dadurch gekennzeichnet, dass das Verhältnis e2/e1 zwischen den Dicken der beiden Vorsprünge in der Nähe von a liegt.
12. Vorrichtung nach einem der Ansprüche 6 bis 11, dadurch gekennzeichnet, dass die Dicke (e1) des Vorsprungs (18) im wesentlichen gleich kA1 (1- Δθ Δt ) ist und dass die Dicke (e2) des Vorsprungs (19) im wesentlichen gleich k 01 (a- AO ) ist, wobei in diesen Ausdrücken: k der Vervielfachungskoeffizient des Drückers ist, Δθ die Betätigungszeit ist, die an den vorderen und hinteren Totpunkten zur Verfügung steht, um den Rohling frei vorzuschieben und zu drehen, und At die Dauer einer Walzphase einschliesslich Δθ ist.
13. Vorrichtung nach einem der Ansprüche 5 bis 12, dadurch gekennzeichnet, dass an der mechanischen Übertragung zwischen dem hinteren Teil des Rohlings und dem Nocken oder auch an der Antriebseinrichtung des Schlittens eine Kraftbegrenzungseinrichtung angeordnet ist.
14. Vorrichtung nach Anspruch 13, dadurch gekennzeichnet, dass die Kraftbegrenzungseinrichtung eine geeichte Feder ist.
EP83420126A 1982-07-21 1983-07-19 Verfahren zum Kaltwalzen von Rohren mittels eines Pilgerwalzwerkes und Vorrichtung zur Durchführung des Verfahrens Expired EP0100743B1 (de)

Priority Applications (1)

Application Number Priority Date Filing Date Title
AT83420126T ATE21636T1 (de) 1982-07-21 1983-07-19 Verfahren zum kaltwalzen von rohren mittels eines pilgerwalzwerkes und vorrichtung zur durchfuehrung des verfahrens.

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
FR8213035A FR2530503A1 (fr) 1982-07-21 1982-07-21 Procede de laminage a froid de tubes au moyen d'un laminoir a pas de pelerin et dispositif pour la mise en oeuvre du procede
FR8213035 1982-07-21

Publications (2)

Publication Number Publication Date
EP0100743A1 EP0100743A1 (de) 1984-02-15
EP0100743B1 true EP0100743B1 (de) 1986-08-27

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EP83420126A Expired EP0100743B1 (de) 1982-07-21 1983-07-19 Verfahren zum Kaltwalzen von Rohren mittels eines Pilgerwalzwerkes und Vorrichtung zur Durchführung des Verfahrens

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Country Link
US (1) US4541262A (de)
EP (1) EP0100743B1 (de)
JP (1) JPS5933013A (de)
AT (1) ATE21636T1 (de)
DE (1) DE3365660D1 (de)
FR (1) FR2530503A1 (de)

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE3708943C1 (de) * 1987-03-18 1987-12-03 Mannesmann Ag Verfahren sowie Dreh- und Vorschubantrieb zur Durchfuehrung des Verfahrens zum Walzen von Rohren oder Stangen nach einem Pilgerschrittverfahren
EP0908245B1 (de) * 1997-10-08 2002-05-15 SMS Demag AG Verfahren und Vorrichtung zur Herstellung von Rohren nach dem Kaltpilgerschrittverfahren
CN100395043C (zh) * 2006-06-16 2008-06-18 林深 冷轧管机轧制主运动和管坯送进回转运动的协调机构

Family Cites Families (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
GB1086357A (en) * 1963-09-30 1967-10-11 Mannesmann Meer Ag Pilger rolling mills
FR1602013A (de) * 1968-12-31 1970-09-28
DE2002408A1 (de) * 1970-01-20 1971-08-26 Wseseojusij Ni I P Ki Metall M Vorrichtung fuer den Rohlingsvorschub in Rohrkaltwalzwerken
FR2230427B1 (de) * 1973-05-24 1977-07-29 Vallourec
DE2449862C3 (de) * 1974-10-17 1979-02-01 Mannesmann Ag, 4000 Duesseldorf Vorschubeinrichtung für von hinten geladene Kaltpilgerwalzwerke
FR2379326A1 (fr) * 1977-02-03 1978-09-01 Vallourec Lorraine Escaut Laminoir a pas de pelerin
US4184352A (en) * 1978-06-08 1980-01-22 Moskovsky Institut Stali I Splavov Method for pilger rolling of tubes and mill for effecting same
DE2934391C2 (de) * 1979-08-23 1986-11-27 Mannesmann AG, 4000 Düsseldorf Verfahren zum Kaltwalzen von Rohren
DE3227082C2 (de) * 1982-07-16 1986-12-04 Mannesmann AG, 4000 Düsseldorf Verfahren und Vorrichtung zum Kaltwalzen von Rohren im Pilgerschrittverfahren

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FR2530503B1 (de) 1985-03-08
US4541262A (en) 1985-09-17
ATE21636T1 (de) 1986-09-15
DE3365660D1 (en) 1986-10-02
JPH0377006B2 (de) 1991-12-09
FR2530503A1 (fr) 1984-01-27
EP0100743A1 (de) 1984-02-15
JPS5933013A (ja) 1984-02-22

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