EP3393689B1 - Kaltpilgerwalzanlage - Google Patents

Kaltpilgerwalzanlage Download PDF

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Publication number
EP3393689B1
EP3393689B1 EP16813355.1A EP16813355A EP3393689B1 EP 3393689 B1 EP3393689 B1 EP 3393689B1 EP 16813355 A EP16813355 A EP 16813355A EP 3393689 B1 EP3393689 B1 EP 3393689B1
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EP
European Patent Office
Prior art keywords
roll stand
rollers
pilger rolling
rolling system
gear rack
Prior art date
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Active
Application number
EP16813355.1A
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German (de)
English (en)
French (fr)
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EP3393689A1 (de
Inventor
Thomas FROBÖSE
Christofer HEDVALL
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.)
Alleima GmbH
Original Assignee
Sandvik Materials Technology Deutschland GmbH
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Publication of EP3393689A1 publication Critical patent/EP3393689A1/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
    • B21B21/005—Pilgrim-step tube-rolling, i.e. pilger mills with reciprocating stand, e.g. driving the stand
    • 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
    • B21B31/02—Rolling stand frames or housings; Roll mountings ; Roll chocks
    • B21B31/028—Prestressing of rolls or roll mountings in stand frames
    • 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
    • B21B31/07—Adaptation of roll neck bearings

Definitions

  • the present invention relates to a pilger rolling mill for forming a billet into a tube with a first roll stand which is mounted so as to be linearly movable in a direction of movement, two rolls for forming the billet into the tube being rotatably mounted on shafts on the roll stand, one of the rolls having a drive gear is arranged on a shaft and wherein the drive gear engages in a fixed rack which is fastened to a rack holder in such a way that a translational movement of the roll stand causes a rotational movement of the drive gear and the roll, and a crank drive connected to the roll stand, which is in operation during the pilger rolling mill converts a rotary movement of a drive motor via an push rod into an oscillating translational movement of the roll stand.
  • an extensive hollow cylindrical blank is reduced by compressive stresses.
  • the blank is formed into a tube with a defined reduced outside diameter and a defined wall thickness.
  • the most common reduction method for pipes is known as cold pilgrims, the blank being called Luppe.
  • the billet is pushed over a calibrated rolling mandrel that defines the inner diameter of the finished tube and is surrounded from the outside by two likewise calibrated rollers that define the outer diameter of the finished tube and is rolled out in the longitudinal direction over the rolling mandrel.
  • the blanks undergo a gradual advance in the direction of the rolling mandrel or over it, while the rollers are rotated horizontally back and forth over the mandrel and thus the blanks.
  • the horizontal movement of the rolls is predetermined by a roll stand on which the rolls are rotatably mounted.
  • the roll stand is moved back and forth in a direction parallel to the rolling mandrel with the aid of a crank drive.
  • DE 6752062 U and DE10 2012 112398 A1 disclose examples of such crawl rolling mills.
  • DE 6752062 U discloses a pilger rolling mill for forming a billet into a tube with a first rolling stand which is mounted so as to be linearly movable in a direction of movement, two rolls for shaping the billet into the tube being rotatably mounted on shafts, one of the rolls having a drive gear (1) is arranged on a shaft and wherein the drive gear (1) engages in a fixed rack (2) which is fastened to a rack holder (3) in such a way that a translational movement of the roll stand causes a rotational movement of the drive gear (1) and the roller, and a crank drive connected to the roll stand, which during operation of the pilger rolling mill converts a rotary movement of a drive motor via a push rod into an oscillating translational movement of the roll stand, the rack holder (2) being designed such that the first roll stand against a second roll stand with one of the first Dimension different second dimension a is interchangeable.
  • DE 10 2012 112396 discloses a pilger rolling mill which has two toothed rack holders arranged in mirror symmetry to a reference plane running perpendicular to the shafts of the rolls, with toothed racks attached thereto, the shaft of one of the two rolls, preferably the lower roll, carrying a drive gear on both sides of the reference plane, the two Drive gearwheels each engage in one of the toothed racks and a cylinder axis of the blank to be accommodated between the rollers lies in the reference plane.
  • the crank mechanism is connected to a torque and mass balancing system, which stores the kinetic energy released at the reversal points during the back and forth movement of the roll stand and this for subsequent acceleration of the mill stand after reversing the direction of movement.
  • the rollers themselves, on the other hand, receive their rotary movement through a toothed rack which is fixed relative to the roll stand and into which toothed wheels which are firmly connected to the roller axes engage.
  • the feed clamping slide with the blank is moved in the so-called feed direction over the mandrel.
  • the conically calibrated rollers which are arranged vertically one above the other in the roll stand, rotate at the same angular speed in opposite directions to one another while the feed clamping carriage holds the blank.
  • the two rollers each roll in the same direction parallel to the cylinder axis of the blank and counter to the direction of advance on the surface of the blank.
  • the caliber shape of the essentially circularly calibrated rolls is always reduced until the diameter of the finished tube is reached in the last cross section of the caliber.
  • the cross-section of the caliber shape consists of a working caliber, which comprises a conical pilgrim's mouth, a constant circular smoothing caliber and a subsequent, slightly larger spout, and an idling caliber with a larger opening.
  • the vocational's mouth which is formed by the rollers, detects the shell and the rollers press a small material wave from the outside, which is stretched by the smoothing caliber of the rollers and the mandrel to the intended wall thickness until the idling caliber of the rollers releases the finished tube.
  • the roll stand with the rollers attached to it moves against the feed direction of the blank.
  • the slug is pushed a further step towards the rolling mandrel, while the rolls with the roll stand return to their horizontal starting position.
  • the blanks undergo a rotation about their axis in order to achieve a uniform shape of the finished tube also in the circumferential direction.
  • a state-of-the-art pilger rolling mill is limited to the production of finished tubes with a narrow range of inside and outside diameters of the finished tubes, since the rolling stand used in the respective pilger rolling mill is only ever designed for a narrow range of inside and outside diameters of the tube to be processed is.
  • the rolling stand used in the respective pilger rolling mill is only ever designed for a narrow range of inside and outside diameters of the tube to be processed is.
  • a large number of pilger rolling mills with different rolling stands must also be kept available.
  • the roll stands must be selected for the respective requirements for the diameter of the pipes to be processed.
  • a mill stand with a certain size is designed for a special parameter range of the diameter of the pipes to be manufactured, in which the billet is as good as possible, i. H. is processed as evenly as possible. Rolling of billets outside of this parameter range is possible, but the rolls work outside their optimal range. As a result, the precision of the machining process decreases and the finished tubes are of poorer quality compared to the finished tubes, which were processed in the optimal parameter range.
  • the caliber shape of the rolls of the second roll stand has a different configuration in the circumferential direction of the rolls from the caliber form of the rolls of the first roll stand, so that loops with a slightly different diameter are grasped by the pilgrim mouth of the second pair of rolls, shaped in the smooth caliber and via the outlet to the Idle calibers can be passed to release the finished tube.
  • the outside diameter of the finished pipe can thus be changed within a narrow range of values.
  • the present invention is based on the object of providing a pilger rolling mill which, in the same pilger rolling mill, enables the production of pipes with a range of values of inside and outside diameters which extends the narrow range of values according to the prior art. It is also an object of the present invention to ensure greater flexibility with regard to the pipe diameter to be manufactured in the same pilger rolling mill. Another object of the present invention is to enable shorter downtimes of the pilger rolling mill and faster swapping of the rollers of the pilger rolling mill.
  • At least one of these tasks is solved by a pilger rolling mill with the features of claim 1.
  • the rack holder according to the invention enables a pilger rolling mill to be made available which can be inexpensively adapted to the pipe diameter of the finished rolled pipe to be produced, so that it is possible to produce pipes with different diameters in the same pilger rolling mill.
  • the finished tubes also have improved accuracy and precision due to the adaptation of the roll stand to the requirements of the tube diameter of the finished tubes.
  • the term dimension of a roll stand encompasses the three spatial dimensions length, width and height and, moreover, also the dimensioning of the rolls and of the drive gearwheels, in particular with regard to their diameter.
  • the first roll stand has a different mass from the second roll stand.
  • the first and the second roll stand have mutually different widths (perpendicular to the direction of movement) and masses.
  • a material of the slug is selected from a group consisting of an unalloyed steel, a low-alloy steel and a high-alloy steel or a combination thereof.
  • the slug is made of stainless steel.
  • the rack holder according to the invention enables the roll stand to be exchanged in a simple manner for a second roll stand with a different dimension without any significant loss of time.
  • the breaks in operation due to the replacement of the roll stand can be significantly reduced and the system productivity can be increased considerably.
  • the pilger rolling mill is equipped with a rack holder which is designed in such a way that the rack can be received on the rack holder at at least two positions spaced apart in a direction parallel to the shafts of the rolls.
  • the rack holder according to the invention enables a drive gear of the roll stand to engage in the rack fastened to the rack holder at at least two spaced-apart positions in a direction parallel to the shafts of the rolls.
  • the width of the roll stand in the sense of the present application defining its extension in the direction parallel to the shafts of the rolls. This is important insofar as the rolling stand is also built to be more stable and solid as the diameter of the rolls increases, which in the end also goes hand in hand with an increase in the width of the rolling stand.
  • the pilger rolling mill is equipped with a rack holder, which is designed in such a way that the rack can be held on the rack holder at at least two positions spaced apart in a direction perpendicular to the shafts of the rolls and perpendicular to the direction of movement of the roll stand, the individual distance between the positions is at least 10 mm.
  • the distance between the positions is understood to mean the distance between the position of the tooth heads measured in a direction perpendicular to the shafts of the rolls and perpendicular to the direction of movement of the roll stand.
  • the rack can thus be adjusted in height at at least two positions spaced apart from one another, the individual distance between the positions being at least 10 mm, so that the Have axes of rotation of the rollers at least two mutually different distances.
  • a drive gear on the shaft of the upper or lower roller, preferably the lower roller, is adapted to the respective roller diameter, while the drive gear can nevertheless engage in the rack.
  • the individual distance between the positions is at least 20 mm. In a further embodiment, however, the individual distance between the positions is at most 100 mm. In a further embodiment, the individual distance between the positions is at most 40 mm.
  • the drive gear which is arranged on one shaft with one of the two rollers, transmits its rotational movement to the rollers, so that the roller diameters which can be used in various ways can each process a narrow range of tube diameters with high accuracy. This extends the value range of the diameter of the finished rolled pipes, which can be produced with the same pilger rolling mill, without any loss of quality being expected.
  • a further embodiment of the present invention is a pilger rolling mill which has two toothed rack holders with toothed racks attached to it, which are arranged mirror-symmetrically to a reference plane running perpendicular to the shafts of the rolls.
  • the shaft of one of the two rollers preferably the lower roller, carries a drive gear on both sides of the reference plane, the two drive gears each engaging in one of the toothed racks and with a cylinder axis of the slug to be accommodated between the rollers lying in the reference plane.
  • the mirror-symmetrical arrangement of the toothed racks attached to the rack holders reduces the occurrence of torques, which have a disruptive influence on the rolling process, since the torques that occur compensate one another through the mirror-symmetrical arrangement.
  • a mirror-symmetrical arrangement leads to significantly less wear on the individual components of the pilger rolling mill. This is reflected in reduced operating and repair costs, making the pilger rolling mill more economical.
  • the pilger rolling mill has a rack holder which extends away from the roll stand by a parallel to the direction of movement of the Rolling axis is pivotally arranged, so that a quick exchange of the roll stand is possible.
  • the pivoting of the rack holder away from the roll stand describes a folding mechanism for the rack holder. Unfolding the rack holder away from the roll stand releases the roll stand in such a way that when it is lifted, e.g. B. is not blocked by the rack holder by means of a crane.
  • the roll stand can thus be removed unhindered and in a simple manner from the pilger rolling mill in the direction perpendicular to the shafts of the rolls and perpendicular to the direction of movement of the roll stand.
  • the pilger rolling mill has a rack holder which is arranged so as to be pivotable about an axis running parallel to the direction of movement of the roll stand, the rack holder being hydraulically clampable in a direction perpendicular to the shafts of the rolls, so that the rack holder is in operation the pilger rolling mill absorbs the forces acting in a direction parallel to the reference plane.
  • the rack holder of the pilger rolling mill or parts thereof are interchangeable with a rack holder or parts thereof, so that the rack on the rack holder can be received at at least two positions spaced apart in a direction parallel to the shaft of the rolls.
  • the rack holder is constructed in two parts and comprises a base support and an adapter plate.
  • the base support is arranged so that it can pivot away from the roll stand about an axis running parallel to the direction of movement of the roll stand.
  • the adapter plate can be easily attached to the base support so that the rack attached to the rack holder can assume at least two spaced apart positions in a direction parallel to the shafts of the rollers.
  • the pilger rolling mill has a rolling stand which is movably mounted in a floating slide bearing, preferably on a hydraulically liftable slide.
  • the plain bearing is designed in such a way that it allows the play between the drive gear and the rack to be adjusted in a direction perpendicular to the shafts of the rolls and perpendicular to the direction of movement of the roll stand.
  • slide guides with maintenance-free, low-wear plain bearings are that they do not require any special lubrication.
  • the engagement of the drive gearwheel in the rack can thereby be determined very precisely, so that wear and tear that occurs over time can be reduced, which, in addition to saving material costs, also entails a cost advantage due to shorter downtimes of the pilger rolling mill.
  • the pilger rolling mill has two rolls arranged vertically one above the other, the shafts of the two rolls being connected to one another via two intermeshing gear wheels such that a rotary movement of one of the two rolls leads to a rotary movement of the other of the two rolls in the leads in the opposite direction.
  • the shafts of the rollers of the pilger rolling mill each have at least one bearing, at least one bearing of one of the two rollers and one bearing of the other of the two rollers being hydraulically braced against one another.
  • Such a hydraulic bracing of the bearings of the two rollers against each other makes it possible to set the roll gap very precisely. This has a positive effect on the quality of the tubes to be processed, which are given a very uniform shape during the rolling process due to the precise setting of the roll gap. Furthermore, the wear to which the rollers are subject during operation due to abrasion can be reduced by precisely adjusting the roller gap.
  • the stroke length of the roll stand which is determined by an eccentricity of a crank pin on which a push rod is accommodated, is set for the largest machinable pipe diameter and is constant for all machinable pipe diameters.
  • the increase in the diameter of the rolls is accompanied by an increase in the mass of the roll stand.
  • the rolling force also increases.
  • the feed length of a single stroke is consequently larger with a larger diameter of the rolls, so that the stroke length of the roll stand is also larger.
  • the stroke length of the roll stand is therefore determined by the largest pipe diameter to be processed in the pilger rolling mill. However, this stroke length represents a compromise for significantly smaller machinable pipe diameters.
  • the feed length of a single stroke is significantly smaller for smaller pipe diameters to be machined due to the smaller diameter of the rolls, so that a larger number of strokes is used in the rolling process.
  • this cannot be as high as desired, since from a certain speed of the rolling process the processing of the pipes becomes inaccurate and irregularities in the wall thickness occur, so that there is a loss of quality.
  • the stroke length of the roll stand which is determined by an eccentricity of a crank pin on which a push rod is received, can be set for different machinable pipe diameters.
  • the distance between the axis of rotation of the flywheel or the crank mechanism and the attachment point of the push rod on the flywheel is adjusted accordingly, i.e. the eccentricity of the crank pin is modified and selectively modified.
  • the crankshaft of the crank mechanism has a rotating balancing mass, the balancing mass being designed in such a way that it compensates for or almost compensates for the moments exerted by the first rolling mill taken up in the pilger rolling mill, the mass of the first rolling mill is smaller than the mass of the second roll stand. It is expedient if this balancing mass is offset from the crank pin by approximately 180 ° relative to the axis of rotation of the crankshaft.
  • crankshaft in the sense of the present application is understood to mean any type of shaft with a crank pin arranged concentrically thereon for receiving the push rod.
  • the rotating inertial forces occurring during the operation of the pilger rolling mill can be completely balanced with the aid of a compensating mass, which is arranged eccentrically to the axis of rotation of the crankshaft at 180 ° to the pivot point of the push rod on the crank mechanism.
  • This balancing mass leads to a mass distribution of the crankshaft with a push rod that is rotationally symmetrical with respect to the axis of rotation of the crankshaft and ensures first-order torque compensation.
  • the balancing mass is designed in such a way that it compensates for or almost compensates for the moments exerted by the first rolling stand received in the pilger rolling mill, the mass of the first rolling stand being smaller than the mass of the second rolling stand.
  • a second roll stand with a large mass is driven with a lower angular velocity of the crankshaft compared to a first roll stand with a lower mass.
  • the rotating mass forces increase quadratically with the angular velocity of the crankshaft, whereas they increase only linearly with the rotating mass.
  • the difference in mass between this and the first roll stand of lower mass can thus be at least partially reduced by the corresponding reduction in the angular velocity be balanced.
  • a balancing mass which is designed for the first roll stand, also compensates the rotating mass forces for the second roll stand with a larger mass.
  • An alternative to this embodiment is an embodiment of the balancing mass such that the balancing mass compensates as best as possible for the moments acting on the crank drive for a mass of the roll stand which results from the average of the masses of the first and the second roll stand.
  • the compensating mass is releasably attached to the crank mechanism, so that when the first rolling stand is replaced, it is adapted as precisely as possible to the mass of the second rolling stand accommodated in the pilger rolling mill, in order to enable the crank mechanism to run, which is free of free forces or moments, or where the free forces and moments are minimized.
  • the pilger rolling mill has a balancer shaft with a second rotating balancing mass, the crankshaft and the balancer shaft being so effectively connected to one another via a central control that the balancer shaft rotates at twice the angular speed of the crankshaft during operation of the cold pilger rolling mill and wherein the second balancing mass is designed in such a way that it compensates or almost compensates for the moments exerted by the first rolling stand received in the pilger rolling mill, the mass of the first rolling stand being smaller than the mass of the second rolling stand.
  • free mass forces of the second order are added when an pilger rolling mill is operated with an oscillating linear movement of the roll stand.
  • the free second order mass forces transmit second order moments via the push rod to the crankshaft and negatively influence the smooth running of the crankshaft.
  • the balancing mass is adapted in such a way that it enables the best possible balancing of the second-order moments for the first rolling stand, the first rolling stand having a smaller mass than the second rolling stand.
  • a compensating mass which is designed for the first roll stand, can also compensate the rotating mass forces for the second roll stand with a larger mass.
  • the second-order moments make a smaller contribution to the sum of the rotating mass forces than the first-order moments.
  • FIG 1 the construction of a pilger rolling mill according to the invention is shown in a schematic sectional side view, in which features which are not essential for understanding have been dispensed with.
  • the pilger rolling mill shown comprises a roll stand 1 with rolls 2, 3, two drive gears 6 arranged on the shaft of the lower roll 3, two toothed racks 5 fastened to a rack holder 4 each, a calibrated rolling mandrel 7 and a feed clamping slide 8.
  • the drive toothed wheels 6 are not shown here to see, since one of the two is covered by the lower roller 3 and the other has been omitted in the illustration for the sake of clarity.
  • the racks 5 and rack holder 4 are also not in Figure 1 pictured.
  • the pilger rolling mill has two toothed rack holders 4, which are arranged symmetrically with respect to a reference plane 11 running perpendicular to the shafts of the rolls, with fixed toothed racks 5 attached to them.
  • the rack holder 4 are away from the roll stand 1 to parallel to the Direction of movement of the roll stand 1 pivot axes 13 extending pivotally.
  • the slug 9 experiences a step-wise feed in the direction of the rolling mandrel 7 towards or over it, while the rollers 2, 3 are rotated horizontally back and forth over the mandrel 7 and thus over the slug 9.
  • the horizontal movement of the rollers 2, 3 is predetermined by a roll stand 1 on which the rollers 2, 3 are rotatably mounted.
  • the roll stand 1 is moved back and forth in a direction parallel to the rolling mandrel 7 with the aid of a crank drive, while the rolls 2, 3 themselves receive their rotary movement through the toothed racks 5, which are fixed relative to the roll stand 1, into the drive gearwheels 6 which are fixedly connected to the lower roll axes intervention.
  • a translational movement of the roll stand 1 is converted into a rotational movement of the drive gears 6.
  • the drive gears 6 are not on the right and left of one each Figure 1 shown lower gear wheel 14, so that the rotational movement of the drive gears 6 causes a rotational movement of the lower gear wheels 14.
  • the lower gearwheels 14 in turn do not mesh with one vertically one above the other Figure 1 shown upper gear gear 15 of the same diameter, which is arranged on the shaft of the upper roller 2.
  • the upper gearwheels 15 are set in rotation at the same angular velocity as the lower gearwheels 14, but in the opposite direction of rotation compared to the lower gearwheels 14.
  • the shafts of the upper and lower rollers 2, 3 each have a left and a right bearing, the left bearing of the upper roller against the left bearing of the lower roller 3 and the right bearing of the upper roller 2 against the right bearing of the lower one Roller 3 are hydraulically clamped.
  • the hydraulic bracing of the left and right bearings of the two rolls 2, 3 against one another enables the roll gap to be set precisely, as a result of which the pipes are given a very uniform shape during the rolling.
  • the advancement of the slug 9 over the mandrel 7 takes place with the aid of the advancement clamping slide 8, which enables a translational movement in a direction parallel to the axis of the rolling mandrel 7.
  • the conically calibrated rolls 2, 3 arranged vertically one above the other in the roll stand 1 roll against the feed direction of the feed clamping slide 8 on the lateral surface of the pipe to be machined in a direction parallel to the cylinder cylinder axis.
  • the so-called crawl's mouth which is formed by the rollers, detects the hole 9 and the rollers 2, 3 press one from the outside small material wave from which a smoothing caliber of the rolls 2, 3 and the mandrel 7 extends to the intended wall thickness until an idling caliber of the rolls 2, 3 releases the finished tube.
  • the roll stand 1 with the rollers 2, 3 attached to it moves counter to the direction of advance of the blank 9.
  • the base 9 is moved a further step onto the mandrel 7 after the idle caliber of the rollers 2, 3 has been reached pushed forward while the rollers 2, 3 return to their horizontal starting position with the roll stand 1.
  • the plate 9 is rotated about its axis in order to achieve a uniform shape of the finished tube.
  • the roll stand is in Figure 1 , if not recognizable, movably mounted in a floating slide bearing, implemented here by a hydraulically liftable slide.
  • the hydraulic mounting is characterized by its ease of installation, which in particular makes the replacement of the roll stand 1 much easier and faster. As a result, the operational downtime associated with replacing the roll stand can be significantly reduced.
  • such a mounting of the rollers 2, 3 does not require seals and pistons that are susceptible to wear, ie the hydraulic mounting is essentially maintenance-free and wear-free.
  • the stroke length of the in Figure 1 Pilger rolling mill shown is fixed for all machinable pipe diameters and by the largest pipe diameter to be machined in the pilger rolling mill. This enables a simplified operating sequence, since it is not necessary to change the eccentricity 21 of the crank pin, but the eccentricity 21 remains the same for all machining processes.
  • the stroke length of a pilger rolling mill adjustable for different machinable pipe diameters.
  • the distance between the axis of rotation of the flywheel of the crank mechanism and the attachment point of the push rod on the flywheel is adjusted accordingly, ie the eccentricity 21 of the crank pin is modified.
  • the stroke length can consequently be optimally adapted to the pipe diameter to be machined, so that the different machinable pipe diameters can be produced with better accuracy compared to a constant stroke length for the different machinable pipe diameters.
  • a complex change in the eccentricity 21 of the crank pin has to be accepted.
  • a central controller 20 is also provided, which is connected both to the drive motor of the balancer shaft 17 and to the drive motor of the crankshaft.
  • the controller 20 controls the motors in such a way that their drive shafts rotate in the same direction of rotation, the rotational frequency of the balancer shaft 17 being twice the rotational frequency of the crankshaft.
  • the controller 20 guarantees an angularly synchronous rotation of the two balancing masses 16, 18 of the crankshaft and balancing shaft 17. That is, the two balancing masses 16, 18 lie at the same angle after one revolution of the crankshaft, the balancing mass 18 of the balancing shaft 17 in the time that the Crankshaft needed for one revolution, made two full revolutions.
  • Figure 2a is a front view of a roll stand of the vocational rolling mill Figure 1 shown.
  • the roll stand 1 with a mass M 1 is designed for the processing of blanks with a diameter between 30 mm and 60 mm.
  • the maximum number of strokes of the roll stand ie the maximum number of back and forth movements of the roll stand per unit of time, is in Figure 2a present embodiment at 200 / min. Since the productivity of a cold pilger rolling mill is directly dependent on the number of strokes of the roll stand, the greatest possible number of working strokes per minute is aimed for reasons of economy.
  • the mill stand 1 in Figure 2a has a mirror-symmetrical arrangement of both the rollers 2, 3 and the drive gearwheels 6 with respect to a reference plane 11 running perpendicular to the shafts of the rolls 2, 3, a cylindrical axis of the plate 9 to be received between the rolls 2, 3 lying in the reference plane 11.
  • the drive gears 6 are firmly connected to the shaft of the lower rollers 3 and engage in the toothed racks 5, which are also attached to the toothed rack holders 4, which are also arranged in mirror symmetry.
  • the racks 5 are in Figure 2a not visible, since these are covered by the rack holders 4.
  • the rack holders 4 can be hydraulically clamped in a direction perpendicular to the shafts of the rolls.
  • the hydraulic bracing takes place here via a system of hydraulic nuts 12, which essentially consist of an annular piston and a cylinder.
  • a temporary pressurization creates a force in the direction perpendicular to the shafts of the rollers 2, 3. This can temporarily create clamping or pushing forces, so that the rolling stand 1 during the rolling process in a direction parallel to the shafts of the rollers 2, 3 on one is held in a fixed position and is thus prevented from sliding away due to torsional forces.
  • the in Figure 2a The rack holder 4 shown is also pivotably arranged away from the roll stand about a pivot axis 13 which runs parallel to the rack 5 and which consists of Figure 2a is not recognizable due to its orientation into the image plane.
  • the drive gear wheels 6 lose contact with the rack 5, so that the roll stand 1 is not blocked by the rack holder 4 when it is lifted by a crane.
  • the rolling stand 1 can thus be exchanged freely and in a simple and quick manner. This brings with it greater flexibility in the machining process with regard to an expanded range of machinable tube diameters.
  • FIG 2b shows an oblique view from above of the rolling stand Figure 2a , but with the rack holder 4 in an open position such that the rack holder 4 has been pivoted about its pivot axis 13 in accordance with the direction of the arrow shown away from the roll stand and as a result the rack 5 attached to the rack holder 4 has no contact with the drive gear 6.
  • the roll stand 1 is thus no longer blocked by the rack holder 4 and can be removed simply and quickly by lifting it out of the pilger rolling mill and replaced by a second roll stand 1 'with different dimensions by means of a crane.
  • Figure 3a is a front view of a second roll stand 1 'of the pilger rolling mill Figure 1 shown.
  • a roll stand 1 ' With larger dimensions with regard to the three spatial dimensions and the diameter of the rolls 2', 3 'and drive gears 6', which, however, in the same pilger rolling mill Figure 1 can be installed.
  • the larger dimensions of the in Figure 3a The rolling stand 1 'shown is also reflected in one in comparison to the rolling stand 1 Figure 2a and 2 B increased mass.
  • the mass of the second roll stand in the present embodiment is 2.5 times the mass M 1 of the roll stand 1 Figure 2a and 2 B .
  • Roll stand 1 ' shown designed for the processing of billets with a diameter between 40 mm and 88 mm and thus for larger diameters compared to the roll stand 1 Figure 2a and 2 B .
  • the maximum number of strokes of the roll stand 1 ' is 150 / min with a correspondingly lower value.
  • the rack holder 4 ' is located in Figure 3a at a position further away from the reference plane 11 'perpendicular to the reference plane 11' compared to that in FIG Figure 2a rack holder shown 4.
  • the rack holder 4, 4 ' is constructed in two parts.
  • it includes a base support and on the other hand an adapter plate which can be attached to the base support in such a way that the respective drive gear 6, 6 'of the roll stand 1, 1' at at least two positions spaced apart from one another in a direction perpendicular to the reference plane 11 into that on the respective rack holder 4, 4 'fixed rack 5, 5' can engage.
  • this adapter plate is built larger in a direction parallel to the shafts of the rollers 2, 3 than in the case of Figure 3a , so that the rack 5 has a smaller distance from the reference plane 11 in the direction of the normal to the reference plane 11.
  • FIG 3b shows an oblique view from above of the roll stand 1 ' Figure 3a .
  • the rack holder 4 ' has been pivoted away from the roll stand 1' about a pivot axis 13 'running parallel to the direction of movement of the roll stand 1' and is located accordingly Figure 2b in an open position such that the rack 5 'fastened to the rack holder 4' no longer has any contact with the drive gear 6 'of the roll stand 1'.
  • a roll stand 1 ' with larger dimensions compared to that in FIG Figures 2a and 2 B
  • the illustrated dimensions of the roll stand 1 ' can be removed from the pilger rolling mill in a simple and quick manner with the aid of the pivoting device which releases the roll stand 1'.

Landscapes

  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Metal Rolling (AREA)
EP16813355.1A 2015-12-23 2016-12-20 Kaltpilgerwalzanlage Active EP3393689B1 (de)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102015122701.0A DE102015122701A1 (de) 2015-12-23 2015-12-23 Kaltpilgerwalzanlage
PCT/EP2016/081913 WO2017108784A1 (de) 2015-12-23 2016-12-20 Kaltpilgerwalzanlage

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EP3393689A1 EP3393689A1 (de) 2018-10-31
EP3393689B1 true EP3393689B1 (de) 2020-06-10

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US (1) US11045848B2 (zh)
EP (1) EP3393689B1 (zh)
JP (1) JP6875402B2 (zh)
KR (1) KR102589419B1 (zh)
CN (1) CN108430660B (zh)
DE (1) DE102015122701A1 (zh)
ES (1) ES2819310T3 (zh)
WO (1) WO2017108784A1 (zh)

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CN107497863A (zh) * 2017-09-20 2017-12-22 张家港市圣鼎源制管有限公司 一种冷轧管机
DE102017221126A1 (de) * 2017-11-27 2019-05-29 Sms Group Gmbh Walzgerüst
CN109317519A (zh) * 2018-10-22 2019-02-12 中国重型机械研究院股份公司 一种两辊热轧管机的机架装置及使用方法
CN111195653A (zh) * 2020-01-07 2020-05-26 宁波凯力精密机械有限公司 恒纯滚动的轧制结构及方法
CN112808775A (zh) * 2020-12-19 2021-05-18 常熟市和新不锈钢管制造有限公司 一种提高钢管质量的冷轧机
CN113578971A (zh) * 2021-07-01 2021-11-02 广东科莱博科技有限公司 一种往复式轧机工作机架的传动结构
CN115090679A (zh) * 2022-07-05 2022-09-23 中国重型机械研究院股份公司 一种单齿条驱动的高速冷轧管机
CN117463887B (zh) * 2023-12-26 2024-04-09 成都正西液压设备制造有限公司 双轨自由移动成型生产线

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Also Published As

Publication number Publication date
US20190084020A1 (en) 2019-03-21
CN108430660A (zh) 2018-08-21
EP3393689A1 (de) 2018-10-31
KR102589419B1 (ko) 2023-10-13
CN108430660B (zh) 2020-07-28
WO2017108784A1 (de) 2017-06-29
ES2819310T3 (es) 2021-04-15
US11045848B2 (en) 2021-06-29
JP6875402B2 (ja) 2021-05-26
JP2019503871A (ja) 2019-02-14
DE102015122701A1 (de) 2017-06-29
KR20180096752A (ko) 2018-08-29

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