EP0144480B1 - Laminoir à pas de pélerin à froid - Google Patents

Laminoir à pas de pélerin à froid Download PDF

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Publication number
EP0144480B1
EP0144480B1 EP19830402403 EP83402403A EP0144480B1 EP 0144480 B1 EP0144480 B1 EP 0144480B1 EP 19830402403 EP19830402403 EP 19830402403 EP 83402403 A EP83402403 A EP 83402403A EP 0144480 B1 EP0144480 B1 EP 0144480B1
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EP
European Patent Office
Prior art keywords
rolling
motor
mandrel
saddles
turning
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.)
Expired
Application number
EP19830402403
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German (de)
English (en)
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EP0144480A1 (fr
Inventor
Yukio Kondoh
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.)
Nippon Steel Corp
Original Assignee
Sumitomo Metal Industries Ltd
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Filing date
Publication date
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Application filed by Sumitomo Metal Industries Ltd filed Critical Sumitomo Metal Industries Ltd
Priority to EP19830402403 priority Critical patent/EP0144480B1/fr
Priority to DE8383402403T priority patent/DE3376806D1/de
Publication of EP0144480A1 publication Critical patent/EP0144480A1/fr
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Publication of EP0144480B1 publication Critical patent/EP0144480B1/fr
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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
    • B21B21/06—Devices for revolving work between the steps
    • B21B21/065—Devices for revolving work between the steps for reciprocating stands
    • 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
    • B21B21/005—Pilgrim-step tube-rolling, i.e. pilger mills with reciprocating stand, e.g. driving the stand

Definitions

  • the present invention relates to a cold pilger mill, and more particularly to such a mill of a simple mechanical construction and easy in adjustment and maintenance.
  • a starting tubular material 10 is intermittently fed over a tapered mandrel 12 from its base end towards its tip end, and each time the material 10 is stationary with respect to the mandrel 12 a pair of grooved dies or rolls 14 which embrace the material 10 from above and below are reciprocated once along the tapered portion of the mandrel 12 from its base end X to its tip end Y for rolling the material 10 to a reduced diameter and wall thickness pipe 16.
  • This cold-pilgering process is advantageous over the other seamless pipe manufacturing processes since a large cross-sectional area reduction, namely, large diameter and wall thickness reductions can be achieved, with the result of very high efficiency of pipe production.
  • it is possible to produce pipes with greatly reduced eccentricities and closer tolerances in inner diameter, outer diameter and wall thickness.
  • the cold pilgering process itself is not so complicated.
  • the actual machines for carrying out this process have had to be very complicated in order to ensure that at each reciprocation of the grooved rolls, i.e., at the completion of each rolling stroke, the material 10 is axially advanced a predetermined distance and at the same time the material 10 and the mandrel 12 are turned around their longitudinal axes by a predetermined angle.
  • the shown cold pilger mill comprises one main motor 20 as a driving source, which is adapted to rotate a crank shaft 22 at a constant speed through a chain-and-wheel mechanism 20a.
  • the crank shaft 22 has a pair of crank pins 22a which are in turn connected respectively to a pair of saddles 24 shown in chain-line in Figure 2 through a coupling rod 22 b .
  • These saddles 24 have two grooved rolls 26, similar to those shown in Figure 1, mounted on roll shafts 26a pivotally supported in the saddles.
  • Each shaft 26a is firmly connected to a pinion 28a in mesh with a stationary rack 28 b affixed to a saddle bed side plate (not shown).
  • crank shaft 22 is connected through a gear train 30, a bevel gear mechanism 32, a line shaft 34 and another bevel gear mechanism 36 to a feed cam 38, so that the rotation of the shaft 22 is transmitted to the cam 38.
  • This cam 38 is in contact with the rear end of a feed screw 40 which is in turn screwed through a feed carriage 42 slidable in the rolling direction.
  • This feed carriage 42 is adapted to engage and push the rear end of a starting tubular material (not shown) towards the pair of rolls 26.
  • the feed screw 40 has a gear 44 fixed thereto at such a position as to mesh with a driving gear 46a when the screw 40 is moved to the most forward position, so that the feed screw 40 is rotated with respect to the feed carriage 42 by the gear 46a so as to be returned to its most rearward position keeping the carriage 42 in a stationary condition.
  • the gear 46a is rotated through a gear train 46 b by a gear box 48 which is driven by a gear 50 fixed to the line shaft 34.
  • the gear 44 meshes with the gear 46a and on the other hand the cam 38 is thereafter gradually separated from the rear end of the screw 40. Therefore, after the completion of the forward feed of the material, the screw 40 is rotated by the gear 46a to be returned to its rearmost i.e., its original position while maintaining the carriage 42 in the advanced position.
  • the above arrangement constitutes a feeding mechanism.
  • the line shaft 34 has mounted on the rear end thereof a turning cam 52 adapted to push a cam follower 54 connected to the end of a transverse shaft 56.
  • the transverse shaft 56 is spring-biased toward the cam 52 and has fixed to its other end a worm gear 58a which is in mesh with a worm wheel 58 b mounted on the rear end of a turning shaft 60.
  • This turning shaft 60 has a gear 62a fixed thereto in mesh through a gear train 62 b with a gear 62, mounted on a mandrel chuck 64 which is rotatably located behind the feed carriage 42.
  • the turning shaft 60 also has another gear 66a mounted on a forward end thereof in mesh through a gear train 66 b with a gear 66 e fixed to an entry pipe turning chuck 68, which is rotatably located between the feed carriage 42 and the saddle 24.
  • the gear 66a is also in mesh through a gear train 66 d with a gear 66 e mounted on an exit pipe turning chuck 70, which is rotatably located at the side of the saddles 24 opposite to the entry turning chuck 68.
  • the mandrel (not shown) is set in such a manner as to be grasped at its tail end by the mandrel chuck 64 and extends through a hole in the feed carriage 42 and the entry pipe turning chuck 68 so that its tapered portion is located between the pair of rolls 26.
  • the starting tubular material to be rolled is set over the mandrel in such a manner that the material is rotatably supported and abutted at its rear end by the feed carriage 42 and is axially movably but unrotatably grasped by the entry and exit pipe turning chucks 68 and 70.
  • the turning cam 52 pushes the transverse shaft 56 and hence the worm gear 58a so as to rotate the worm wheel 58 b and hence the turning shaft 60.
  • This rotation of the turning shaft 60 is transmitted to the mandrel chuck64, the entry pipe turning chuck 68 and the exit pipe turning chuck 70 through the gears 62a, 62 b , 62 c , 66a, 66 b , 66 c , 66d and 66 e , so that the mandrel and the material held by these chucks are turned for example about 60 to 90 degrees.
  • this arrangement constitutes a turning mechanism.
  • the conventional cold pilger mill uses a very complicated arrangement in order to make the feeding of the material and the turning of the material and mandrel in precise synchronism with the intermittent rolling operation.
  • the elements excluding the motor 20, the crank shaft 22, the saddles 24, the rolls 26, the feed carriage 42, the mandrel chuck 64, and the entry and exit pipe turning chucks 68 and 70 are provided only for power transmission.
  • a considerable portion of the conventional cold pilger mill is constituted by the power transmission mechanism attendant to the above mentioned main elements, and since the transmission mechanism is very complicated, the overall construction of the pilger mill has become very complicated.
  • a cold pilger mill comprising:
  • Said detector may be a rotational angle detector adapted to generate a pulse signal for each predetermined amount of angular displacement.
  • each of said second, third, fourth and fifth motors is a pulse motor
  • said main controller provides predetermined numbers of power pulses to said pulse motors upon completion of each rolling stroke in response to signal input from said detector.
  • said main controller includes a pulse generator and preset counters for counting the number of pulses to be supplied to each of said pulse motors, said main controller providing power pulses until the respective counters reach predetermined count values.
  • each of said second, third, fourth and fifth motors communicates with a rotational angle detector and a local controller, and in that said main controller provides an operation signal to each local controller upon completion of each rolling stroke in response to signal input from said rolling phase detector, each of said local controllers being operative to place the motor associated therewith in an operating condition responsive to said operation signal from said main controller and to monitor output from the associated rotational angle detector so as to stop said associated motor when the associated motor rotates a predetermined amount.
  • FIG 3 there is shown a schematic perspective view of a first embodiment of the present invention.
  • portions similar to those shown in Figure 2 are given the same Reference Numerals.
  • the shown cold pilger mill comprises a rolling mechanism, a feeding mechanism and a turning mechanism as in the conventional mill shown in Figure 2, and in addition has a controller 72 for synchronizing operations of the feeding and turning mechanisms with the operation of the rolling mechanism.
  • the rolling mechanism comprises one main motor 20 adapted to rotate a crank shaft 22 at a constant speed through a chain-and-wheel mechanism 20a.
  • the crank shaft 22 has a pair of crank pins 22g which are in turn connected to a pair of saddles 24 shown in chain-line in Figure 3, respectively, through a coupling rod 22 b .
  • These saddles 24 have two grooved rolls 26, similar to those shown in Figure 1, mounted on roll shafts 26a pivotally supported in the saddles.
  • the roll shaft 26a is firmly connected to a pinion 28a in mesh with a stationary rack 28 b affixed to a saddle bed side plate (not shown).
  • the rolling mechanism of the shown embodiment has a rotational angle detector 74 coupled to the crank shaft 22.
  • This rotational angle detector 74 is provided to detect from the rotational angle of the crank shaft 22 the phase of rolling, i.e., what stage of each rolling stroke the mill is presently in. In other words, the phase of rolling is detected for recognizing where the saddles 24 are or where the grooved rolls 26 are in their rotational position. Therefore, the rolling phase detector may instead be a detector which directly detects the position of the saddles 24 or the rotational angle of the rolls 26.
  • the detector 74 is of the type which generates one pulse for each predetermined angular displacement.
  • the detector 74 has an output connected to the controller 72.
  • the feeding mechanism includes a feed screw 40 threadedly received through a feed carriage 42 which is longitudinally movably located at the entry side of the saddles 24.
  • the feed screw 40 is rotatably but axially immovably supported.
  • the feed screw 40 has fixed to the rear end thereof a gear 40a in mesh with a gear 40 b mounted on a rotating shaft of a pulse motor 76 which is controlled by the controller 72. Therefore, if the motor 76 is energized by the controller 72, the feed screw 40 is rotated through the gears 40 b and 40a to forwardly and backwardly move the carriage 42 and the material to be rolled.
  • the turning mechanism is constituted by a mandrel chuck 64 adapted to grasp the tail end of a tapered mandrel as shown in Figure 1, and entry and exit pipe turning chucks 68 and 70 located at opposite sides of the saddles 24 in the longitudinal, i.e., rolling direction.
  • These turning chucks 68 and 70 are adapted to axially movably but unrotatably grasp the tubular material to be rolled.
  • the mandrel chuck 64 has a gear 64a fixed thereto and in mesh with a gear 64 b mounted on a shaft of a pulse motor 78 which is controlled by the controller 72. Therefore, if the motor 78 is driven under the control of the controller 72, the mandrel chuck 64 is rotated to turn the mandrel (not shown) grasped by the chuck 64.
  • the entry pipe turning chuck 68 has fixed thereto a gear 68a in mesh with a gear 68 b driven by a pulse motor 80.
  • the exit pipe turning chuck 70 has fixed thereto a gear 70a in mesh with a gear 70 b driven by a pulse motor 82.
  • These pulse motors 80 and 82 are controlled by the controller 72. If these motors 80 and 82 are energized under the control of the controller 72, these chucks 68 and 70 are turned.
  • the pulse motors 76, 78, 80 and 82 are energized, the material to be rolled abutted by the carriage 42 and grasped by the pipe turning chucks 68 and 70 is advanced in the axial direction and turned around the longitudinal axis, and at the same time, the mandrel inserted in the material to be rolled is turned together with the material without being axially moved.
  • the controller 72 receives the rotational angle signal from the detector 74 and outputs power pulse trains to the pulse motors 76, 78, 80 and 82 of the feeding and turning mechanisms. Specifically, the controller 72 receives pulses generated one for each predetermined amount of angular displacement by the rotational angle detector 74 coupled to the crank shaft 22. When the number of the pulses received reaches a predetermined number, the controller 72 decides that one actual rolling stroke has been completed, i.e., that the rolls 26 have returned to a position just before the advanced limit X.
  • the controller 72 supplies to the pulse motor 76 of the feeding mechanism a predetermined number of power pulses (Na) necessary to advance the carriage 42 and hence the material to be rolled (not shown) a predetermined distance in the material feeding direction.
  • the controller 72 supplies to the pulse motors 78, 80 and 82 of the turning mechanism another predetermined number of power pulses (Nb) required for turning the chucks 64, 68 and 70 and hence the mandrel and the material to be rolled (both not shown) by a predetermined angle.
  • the controller 72 is adapted to freely move the carriage 42 in accordance with an external input.
  • controller 72 comprises a preset counter 84 having an input connected to the rotational angle detector 74, so that the counter 84 counts pulses outputted from the rotational angle detector 74.
  • This counter 84 has an output connected to a monostable circuit 86, so that when the counter 84 counts up to a predetermined number N R corresponding to one rolling stroke, the counter 84 triggers the monostable circuits 86.
  • the monostable circuit 86 has an output connected to a reset terminal of the counter 84 and one input of an AND gate 88, so that when the monostable circuit 86 is triggered, it outputs a logical-high signal to the AND gate 88 so as to open the AND gate 88 and resets the counter 84 by the leading edge of the logical-high signal.
  • the AND gate 88 has another input connected to a pulse generator 90 and an output connected to one input of AND gates 92a and 92 b and preset counters 94a and 94 b .
  • the AND gate 92a has an output connected to an amplifier 96a whose output is connected to the pulse motor 76 of the feeding mechanism.
  • the AND gate 92 b has an output connected to another amplifier 96 b whose output is connected to the pulse motors 78, 80 and 82 of the turning mechanism.
  • the AND gates 92a and 92 b have another input connected to the output of preset counters 94a and 94 b , respectively. These preset counters 94a and 94 b are reset by the leading edge of the logical-high signal outputted from the counter 84 when the counter 84 counts to the aforementioned predetermined number N R .
  • the preset counter 94a is adapted to supply a logical-high signal to the associated AND gate 92a so as to open it until the counter reaches the aforementioned predetermined count number Na. After the counter 94a reaches the predetermined count number Na, it supplies a logical-low signal to the AND gate 92a so as to close the AND gate 92a. Therefore, Na pulses are fed from the AND gate 88 through the AND gate 92a to the amplifier 96a, so that the amplifier 96a supplies Na power pulses to the pulse motor 76 of the feeding mechanism.
  • the counter 94 b is adapted to supply a logical-high signal to the associated AND gate 92 b so as to open it until the counter 94 b reaches the aforementioned predetermined count number Nb. After the counter 94 b reaches the predetermined count Nb, it supplies a logical-low signal to the AND gate 92 b so as to close the AND gate 92 b . Therefore, Nb pulses are fed from the AND gate 88 through the AND gate 92 b to the amplifier 96 b , so that the amplifier 96 b supplies Nb power pulses to the pulse motors 78, 80 and 82 of the turning mechanism.
  • a tapered mandrel as shown in Figure 1 is set by grasping the tail end of the mandrel by the mandrel chuck 64 and locating the tapered portion of the mandrel between the rolls 26.
  • the feed carriage 42 is returned to its retreated limit by inputting an external command to the controller 72.
  • a starting tubular material to be rolled (not shown) is set by bringing the tail end of the material into abutment with the carriage 42, passing the forward portion of the material through the entry turning chuck 68 between the rolls 26, and unrotatably but axially movably grasping the material by the entry and exit turning chucks 68 and 70.
  • the motor 20 is brought into an energized condition. This rotation of the motor 20 causes the rotation and reciprocation of the rolls 26 between the advanced limit X and the retreated limit Y so that the material is intermittently rolled at a constant cycle.
  • the preset counter 84 of the controller 72 counts the pulse signals generated by the rotational angle detector 74.
  • the counter 84 outputs a logical-high signal to the preset counters 94a and 94 b and the monostable circuit 86.
  • the counters 94a and 94 b are reset to be ready to count inputted pulses and also to supply a logical-high signal to the associated AND gates 92a and 92 b so as to open the same AND gates.
  • the monostable circuit 86 outputs a logical-high signal to the counter 84 to reset the same counter so that it starts counting from its initial count value again.
  • the logical-high signal from the monostable circuit 86 is fed to the AND gate 88 to open the same AND gate, so that the pulses are fed from the pulse generator 90 through the AND gate 88 to the AND gates 92a and 92 b and the counters 94a and 94 b .
  • the counter 94a is adapted to output the logical-high signal to the associated AND gate 92a so as to maintain the same AND gate in the open condition until the counted value reaches the predetermined value Na, the predetermined number of pulses Na are supplied from the pulse generator 90 through the AND gates 88 and 92a to the amplifier 96a where they are amplified to be fed as power pulses to the pulse motor 76.
  • the counter 94 b is adapted to output the logical-high signal to the associated AND gate 92 b so as to maintain the same AND gate in the open condition until the counted value reaches the predetermined value Nb
  • the predetermined number of pulses Nb are supplied from the pulse generator 90 through the AND gates 88 and 92 b to the amplifier 96 b where they are amplified to be fed as power pulses to the pulse motors 78, 80 and 82.
  • the controller 72 supplies the predetermined numbers of power pulses Na and Nb to the motor 76 of the feeding mechanism and the motors 78, 80 and 82 of the turning mechanism, respectively, so that the feed carriage 42 is advanced toward the saddles 24 the predetermined distance and at the same time the mandrel chuck 64, the entry pipe turning chuck 68 and the exit pipe turning chuck 70 are turned the predetermined amount of angle.
  • the material to be rolled is advanced the predetermined distance by the carriage 42, and the material and the mandrel are turned together by the predetermined angle by the chucks 64, 68 and 70. Accordingly, the material is intermittently rolled by predetermined lengths while changing the rolling direction in each rolling stroke.
  • the carriage 42 is moved to its retreated limit by inputting an external command to the controller 72, and then the next tubular material is set in the aforementioned manner.
  • the controller 72 determines whether the rolling is performed as mentioned above and is completed.
  • the AND gate 92 b , the preset counter 94 b and the amplifier 96 b are provided common to the pulse motors 78, 80 and 82 of the turning mechanism. However, if each of motors 78, 80 and 82 is individually associated with one set of the AND gate 92 b , the preset counter 94 b and the amplifier 96 b , even if the gear pairs 64a and 64 b , 68a and 68 b , and 70a and 70 b are different in gear ratio, the chucks 64, 68 and 70 can be easily synchronized by adjusting the preset values of the three respective counters 94 b .
  • FIG 5 there is shown a second embodiment of the present invention. Portions shown in Figure 5 similar to those of the first embodiment shown in Figure 3 are given the same Reference Numerals and explanation on those portions will be omitted.
  • servo motors 76a, 78a, 80a and 82a are coupled to the gears 40 b , 64 b , 68 b and 70 b , respectively, and are also associated with rotational angle detectors 76 b , 78 b 80 b and 82 b , respectively.
  • These servo motors 76a, 78a, 80a and 82a and the rotational angle detectors 76 b 78 b , 80 b and 82 b are connected to local controllers 76 c , 78 c , 80, and 82 c , respectively, which are adapted to operate the associated servo motors 76a, 78a, 80a and 82a in response to the operation signal from the controller 72 and at the same time to count a pulse signal generated by the associated rotational detectors 76 b , 78 b , 80 b and 82 b for each predetermined angular displacement. When the respective count values reach respective predetermined values, the local controllers operate to stop the associated servo motors.
  • the controller 72 counts the pulse signals from the rotational angle detector 74 coupled to the crank shaft 22 and outputs the operation signal to each of the local controllers 76 b , 78 c , 80. and 82 b .
  • the controller 72 counts the operation signals outputted to compute the number of the rolling strokes performed N, and outputs a rolling completion signal when N reaches a predetermined value No.
  • the cold pilger mill of the second embodiment operates as follows: Similarly to the first embodiment, a starting tubular material (not shown) is set in the mill, and then, the main motor 20 is put in an operating condition to start the rolling. In this condition, every time the controller 72 receives and counts a pulse signal from the rotational angle detector 74, it determines whether or not the count value has reached a predetermined number, i.e., whether or not the rotational angle 8 of the crank shaft 22 has reached a predetermined degree of angle 8 0 , as shown in the flowchart of Figure 6. When the rotational angle 8 reaches the predetermined angle 8 0 , the controller 72 outputs an operation signal to the local controllers 76, 78 c , 80c and 82 c . At the same time, the controller 72 counts up the number of rolling strokes performed N by 1 and starts to count again the pulse signal from the detector 74 until the number of rolling strokes reaches the predetermined value No.
  • the local controllers 76 c 78 c , 80 c and 82 c bring the associated servo motors 76a, 78a, 80a and 82a into operating condition, respectively, and at the same time start to count a pulse signal from the respective associated rotational angle detectors 76 b , 78 b , 80 b and 82 b .
  • the feed carriage 42 is advanced toward the saddles 24 the predetermined distance by the servomotor 76a, and at the same time, the chucks 64, 68, and 70 are turned by the predetermined angle by the servo motors 78a, 80a and 82a. Accordingly, the material is intermittently rolled by the predetermined lengths while changing the rolling direction in each idle period in which the material is free from the restraint of the rolls 26.
  • the local controllers 76 c , 78 c , 80 c and 82 r are used. However, these local controllers may be omitted so that the controller 72 directly receives the output of the rotational angle detectors 76 b , 78 b , 80 b and 82 b and directly controls the servo motors 76a, 78a, 80a and 82a.
  • the mill of the present invention requires the rotational angle detector 74, the driving pulse motors 76, 78, 80 and 82, the controller 72, and, in the second embodiment, also the local controllers 76 c , 78 c , 80 c and 82 c , but does not require the power transmission means such as the bevel gear 32, the line shaft 34, the bevel gear mechanism 36, the feed cam 38, the gear box 48, the turning cam 52, and the like which are required in the conventional mill. Therefore, the mill of this invention as claimed is very simple in construction in comparison with the conventional mill. This simplicity in construction makes the mill inexpensive and maintenance easy.
  • the feeding mechanism in the conventional cold pilger mill is such that the carriage 42 is advanced together with the feed screw 40 by the feed cam 38 and after the carriage 42 is advanced only the feed screw 40 is returned to its original position by rotating the screw 40 while maintaining the carriage 42 in the advanced position.
  • the feeding mechanism of the conventional mill requires advancing means and returning means.
  • the feed mechanism is such that the carriage 42 can be intermittently advanced only by turning the feed screw 40. Therefore, the feed mechanism is extremely simple.
  • the feeding mechanism and the turning mechanism are driven by the motor of the rolling mechanism through mechanical coupling means which necessarily becomes complicated for ensuring synchronism between the mechanisms but inevitably has play or backlash between each pair of mechanical elements.
  • the feeding mechanism and the turning mechanism are separately driven by the respective individual motors independent of the motor for the rolling mechanism, so that the rolling mechanism, the feeding mechanism and the turning mechanism are synchronized by electrical control means without use of mechanical coupling means. Since the electrical synchronism is free from the mechanical play or backlash in the mechanical couplings, all the mechanisms are precisely synchronized in the mill of the present invention as claimed.
  • the mill of the present invention as claimed eliminates a substantial portion of the power transmission mechanism required in the conventional mill, so that the power loss in the transmission system becomes substantially zero. Therefore, the efficiency of power utilization is excellent and power costs can be reduced.
  • the synchronism between the feeding and turning mechanisms can be easily maintained only by changing the preset values of the counters 94a and 94 b without exchange and adjustment of the gears and the cams with very troublesome operations, as in the conventional cold pilger mill.
  • the rolling mechanism, the feeding mechanism and the turning mechanism are not coupled by mechanical means but are driven by individual motors synchronized under electrical control.
  • the mill of the present invention as claimed is very simple in overall construction, and accordingly is inexpensive and easy in adjustment and maintenance.

Claims (5)

1. Laminoir à pas de pélerin à froid comprenant:
- un mécanisme de laminage (20, 22, 24, 26) pour laminer par intermittence un matériau tubulaire sur un mandrin afin de produire un tuyau de diamètre réduit, ledit mécanisme de laminage comportant une paire de cylindres rainurés (26) portée de façon tournante par une paire de cavaliers (24), lesdits cylindres rainurés étant disposés de façon à enserrer ledit matériau tubulaire de part et d'autre de celui-ci, lesdits cavaliers étant animés d'un mouvement de va-et-vient pour définir une course de laminage du matériau, par un vilebrequin (22) entraîné en rotation par un premier moteur (20), chacun desdits cylindres rainurés ayant, fixé à celui-ci, un pignon (28a) en prise avec une crémaillère stationnaire (28b) pour tourner avec le cylindre respectif,
- un détecteur (74) communiquant avec ledit mécanisme de laminage pour détecter la phase de laminage dans ledit mécanisme de laminage,
- un mécanisme d'avance (40, 42) entraîné par un second moteur (76, 76a) pour faire avancer ledit matériau tubulaire dans une direction axiale, et
- un contrôleur principal (72) recevant un signal fourni en entrée par ledit détecteur (74) et fournissant un signal de fonctionnement au moteur (76, 76a) dudit mécanisme d'avance de façon à ce que ledit mécanisme d'avance soit activé lors de l'achèvement de chaque course de laminage, caractérisé en ce qu'il comprend également:
- un porte-mandrin (64) entraîné par un troisième moteur (78, 78a) pour la saisie d'une extrémité arrière dudit mandrin,
- un porte-pièce tournant d'entrée (68) entraîné par un quatrième moteur (80, 80a), ledit porte-pièce tournant étant situé au voisinage d'un côté d'entrée desdits cavaliers (24) dans la direction de laminage desdits cavaliers, pour le maintien dudit matériau tubulaire sur ledit mandrin, et
- un porte-pièce tournant de sortie (70) entraîné par un cinquième moteur (82, 82a), ledit porte-pièce tournant de sortie étant situé au voisinage d'un côté desdits cavaliers opposé audit porte-pièce tournant d'entrée (68) dans la direction de laminage desdits cavaliers, pour le maintien dudit matériau tubulaire sur ledit mandrin,
et en ce que ledit contrôleur principal (72) fournit également un signal de fonctionnement aux moteurs respectifs (78, 80, 82; 78a, 80a, 82a) dudit porte-mandrin (64) et desdits porte-pièces tournants (68, 70) de façon à ce que lesdits porte-mandrin et porte-pièce soient également activés lors de l'achèvement de chaque course de laminage.
2. Laminoir à pas de pélerin à froid selon la revendication 1, caractérisé en ce que ledit détecteur (74) est un détecteur d'angle de rotation adapté à engendrer un signal impulsionnel pour chaque quantité prédéterminée de déplacement angulaire.
3. Laminoir à pas de pélerin à froid selon l'une quelconque des revendications 1 et 2, caractérisé en ce que chacun desdits second, troisième, quatrième et cinquième moteurs (76, 78, 80, 82) est un moteur impulsionnel, et en ce que ledit contrôleur principal (72) fournit des nombres prédéterminés d'impulsions de courant auxdits moteurs impulsionnels lors de l'achèvement de chaque course de laminage en réponse au signal fourni en entrée par ledit détecteur (74).
4. Laminoir à pas de pélerin à froid selon la revendication 3, caractérisé en ce que ledit contrôleur principal (72) comporte un générateur d'impulsions (90) et des compteurs préréglés (94a, 94b) pour le comptage du nombre d'impulsions à fournir à chacun desdits moteurs impulsionnels, ledit contrôleur principal fournissant des impulsions de courant jusqu'à ce que les compteurs respectifs atteignent des valeurs de comptage prédéterminées.
5. Laminoir à pas de pélerin à froid selon l'une quelconque des revendications 1 et 2, caractérisé en ce que chacun desdits second, troisième, quatrième et cinquième moteurs (76a, 78a, 80a, 82a) communique avec un détecteur d'angle de rotation (76b, 78b, 80b, 82b) et un contrôleur local (76c, 78c, 80c, 82c), et en ce que le contrôleur principal (72) fournit un signal de fonctionnement à chaque contrôleur local lors de l'achèvement de chaque course de laminage en réponse au signal fourni en entrée par ledit détecteur de phase de laminage, chacun desdits contrôleurs locaux ayant pour fonction de faire passer le moteur qui lui est associé dans un mode de fonctionnement en réponse audit signal de fonctionnement provenant dudit contrôleur principal et de contrôler la sortie du détecteur d'angle de rotation associé de façon à arrêter ledit moteur associé lorsque le moteur associé tourne d'une quantité prédéterminée.
EP19830402403 1983-12-13 1983-12-13 Laminoir à pas de pélerin à froid Expired EP0144480B1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
EP19830402403 EP0144480B1 (fr) 1983-12-13 1983-12-13 Laminoir à pas de pélerin à froid
DE8383402403T DE3376806D1 (de) 1983-12-13 1983-12-13 Cold pilger mill

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP19830402403 EP0144480B1 (fr) 1983-12-13 1983-12-13 Laminoir à pas de pélerin à froid

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EP0144480A1 EP0144480A1 (fr) 1985-06-19
EP0144480B1 true EP0144480B1 (fr) 1988-06-01

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Publication number Priority date Publication date Assignee Title
FR2759483B1 (fr) 1997-02-12 1999-04-30 Zircotube Procede de fabrication d'un tube-guide d'un assemblage de combustible d'un reacteur nucleaire, mandrin de formage d'un tube-guide et tube-guide obtenu

Family Cites Families (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR1165727A (fr) * 1956-02-08 1958-10-28 Dalmine Spa Perfectionnements apportés aux dispositifs de réglage des mécanismes d'actionnement des cylindres et du dispositif d'alimentation des laminoirs, notamment des laminoirs à pas de pélerin
US4037444A (en) * 1977-01-10 1977-07-26 Wean United, Inc. Shell feed system for a cold pilger mill
FR2379326A1 (fr) * 1977-02-03 1978-09-01 Vallourec Lorraine Escaut Laminoir a pas de pelerin
DE2951264C2 (de) * 1979-12-17 1981-11-19 Mannesmann AG, 4000 Düsseldorf Einrichtung an Warmpilgerwalzwerken zum Walzen von nahtlosen Rohren

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DE3376806D1 (de) 1988-07-07
EP0144480A1 (fr) 1985-06-19

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