EP3393689A1 - Kaltpilgerwalzanlage - Google Patents
KaltpilgerwalzanlageInfo
- Publication number
- EP3393689A1 EP3393689A1 EP16813355.1A EP16813355A EP3393689A1 EP 3393689 A1 EP3393689 A1 EP 3393689A1 EP 16813355 A EP16813355 A EP 16813355A EP 3393689 A1 EP3393689 A1 EP 3393689A1
- Authority
- EP
- European Patent Office
- Prior art keywords
- rollers
- rolling
- rolling mill
- stand
- rack
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000005096 rolling process Methods 0.000 title claims abstract description 220
- 230000033001 locomotion Effects 0.000 claims abstract description 52
- 230000007246 mechanism Effects 0.000 claims description 16
- 238000004519 manufacturing process Methods 0.000 abstract description 8
- 238000007493 shaping process Methods 0.000 abstract 2
- 238000003754 machining Methods 0.000 description 5
- 239000000463 material Substances 0.000 description 4
- 230000008901 benefit Effects 0.000 description 3
- 150000001875 compounds Chemical class 0.000 description 3
- 238000009499 grossing Methods 0.000 description 3
- 229910000851 Alloy steel Inorganic materials 0.000 description 2
- 229910000831 Steel Inorganic materials 0.000 description 2
- 230000006978 adaptation Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000009467 reduction Effects 0.000 description 2
- 239000010959 steel Substances 0.000 description 2
- 241000237858 Gastropoda Species 0.000 description 1
- 238000005299 abrasion Methods 0.000 description 1
- 230000001133 acceleration Effects 0.000 description 1
- 230000002411 adverse Effects 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 238000007796 conventional method Methods 0.000 description 1
- 230000001419 dependent effect Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 238000012423 maintenance Methods 0.000 description 1
- 239000002184 metal Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000008092 positive effect Effects 0.000 description 1
- 230000008439 repair process Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000010935 stainless steel Substances 0.000 description 1
- 229910001220 stainless steel Inorganic materials 0.000 description 1
- 230000001360 synchronised effect Effects 0.000 description 1
Classifications
-
- 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 converting a billet into a tube with a linearly movably mounted in a first rolling stand, wherein on the rolling stand, two rollers for forming the billet to the tube are rotatably mounted on shafts, wherein one of the rollers with a drive gear is arranged on a shaft and wherein the drive gear engages a fixed rack which is fixed to a rack holder, that a translational movement of the rolling mill causes a rotational movement of the drive gear and the roller, and connected to the rolling stand crank mechanism, the operation of the pilger rolling mill a rotational movement of a drive motor via a push rod in an oscillating translational movement of the rolling mill transferred.
- an extended hollow cylindrical blank is reduced by compressive stresses.
- the blank is formed into a tube with a defined reduced outer diameter and a defined wall thickness.
- the most common tube reduction method is known as cold pilgering, the blank being called a billet.
- the billet is pushed over a calibrated rolling mandrel defining the inside diameter of the finished pipe, while from the outside it comprises two likewise calibrated rolls defining the outside diameter of the finished pipe and rolled longitudinally over the rolling dome.
- the billet undergoes incremental advancement in the direction of the rolling dome to and beyond it, while the rolls are rotationally reciprocated over the mandrel and thus the billet horizontally.
- the horizontal movement of the rollers is predetermined by a rolling stand on which the rollers are rotatably mounted.
- the roll stand is reciprocated in known Kaltpilgerwalzanlagen by means of a crank mechanism in a direction parallel to the rolling mandrel.
- the crank mechanism is connected to a torque and mass balance system which stores the kinetic energy released at the reversal points during the reciprocation of the roll stand and this for the subsequent acceleration the rolling mill used after reversing the direction of movement.
- the rollers themselves, however, receive their rotational movement through a fixed relative to the mill rack, engage firmly with the roller axes connected gears.
- the feed tension slide with the billet is moved in the so-called feed direction over the rolling mandrel.
- the conically calibrated rollers arranged vertically one above the other in the rolling stand rotate opposite to one another at the same angular velocity while the feed tensioning carriage holds the billet. In this case, the two rollers each roll in the same direction parallel to the cylinder axis of the billet and counter to the feed direction on the outer surface of the billet.
- the caliber shape of the substantially circularly calibrated rolls always decreases until the diameter of the finished tube is reached in the last cross section of the caliber.
- the cross-section of the caliber mold consists of a working caliber comprising a conical crawl mouth, a uniform circular calender and a subsequent slightly larger spout, and an open-gauge caliber with a larger opening.
- the vocational jaw formed by the rollers engages the billet and the rollers press from the outside a small material shaft, 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 rolls attached thereto moves counter to the feeding direction of the billet.
- the billet is advanced by a further step onto the rolling dome, while the rolls with the rolling stand return to their horizontal starting position. At the same time, the billet undergoes a rotation about its axis in order to achieve a uniform shape of the finished tube in the circumferential direction.
- a domestic rolling mill according to the prior art is limited to the production of finished pipes with a narrow Wertebe rich of inner andnostien pressmessem the finished pipes, since the rolling mill used in the respective pilger rolling mill always only for a narrow range of inner and outer diameters of the pipe to be machined is designed.
- the rolling stands for the respective requirements must be selected to the diameter of the pipes to be machined.
- larger rolling stands are also required in view of the width of the rolling stand and the diameter of the rolls used therein. As the size of the rolling stand increases, so does the mass of the rolling stand.
- a rolling mill of a certain size is designed for a specific parameter range of the diameter of the pipes to be produced, in which the billet best possible, d. H. as evenly as possible, is processed. It is possible to roll billets outside this parameter range, but the rolls are out of their optimum range. Consequently, the precision of the machining process decreases and the finished pipes have a poorer quality compared to the finished pipes which have been machined in the optimum parameter range.
- the caliber shape of the rolls of the second stand has a circumferential configuration of the rolls other than the caliber shape of the rolls of the first stand, thereby capturing lands of slightly different diameter from the second pair of pillows, forming them in the smoothing caliber and passing them through the exit Leeriaufkaliber can be handed over to release the finished pipe.
- the outer diameter of the finished tube can thus be changed in a narrow range of values.
- the present invention has the object to provide a pilger rolling mill, which allows in the same pilger rolling mill production of tubes of a range of inner and outer diameters, which extends the narrow range of values according to the prior art.
- Another object of the present invention is to allow shorter downtime of the pilger rolling mill as well as a faster exchange of the rollers of the pilger rolling mill.
- a pilger rolling mill for forming a billet into a tube with a linearly movably mounted first mill stand, wherein two rolls are rotatably mounted on the mill stand for forming the billet to the tube, one of the rollers having a drive gear is arranged on a shaft and wherein the drive gear engages a fixed rack which is fixed to a rack holder, that a translational movement of the rolling mill causes a rotational movement of the drive gear and the roller, and connected to the rolling stand crank mechanism, the operation of the pilger rolling mill a rotary motion of a drive motor via a push rod in an oscillating translational movement of the rolling stand, wherein the rack holder is configured such that the first rolling stand against a second rolling mill with a different from the first dimension two dimension is interchangeable.
- the rack holder according to the invention makes it possible to provide a pilger rolling system which can be inexpensively adapted to the pipe diameter of the finished rolled tubes so that the production of tubes with different diameters in the same pilger rolling mill is possible.
- the finished tubes also have improved accuracy and precision by adapting the rolling stand to the pipe diameter requirements of the finished rolled tubes.
- dimension of a rolling stand in the sense of the present invention encompasses the three dimensions of space length, width and height and beyond that also the dimensioning of the rollers and the drive gears, in particular with respect to their diameter.
- the first stand has a different mass from the second stand.
- the first and second stands have different widths (perpendicular to the direction of movement) and masses.
- a material of the billet is selected from a group consisting of an unalloyed steel, a low alloy steel and a high alloy steel or a combination thereof.
- the billet is made of stainless steel.
- the rack holder according to the invention makes it possible to replace the roll stand in a simple manner against a second rolling stand with a different dimension without appreciable loss of time.
- the interruptions due to the replacement of the roll stand can be significantly reduced and the productivity of the plant can be greatly increased.
- the pilger rolling mill is provided with a rack holder which is configured such that the rack is receivable on the rack holder at at least two positions spaced from each other in a direction parallel to the shafts of the rollers.
- the rack holder according to the invention enables a drive gear of the rolling stand to engage at least two spaced-apart positions in a direction parallel to the shafts of the rollers in the rack mounted on the rack holder.
- at least two rolling stands with two different widths can be installed on the same pilger rolling mill, wherein the width of the rolling mill in the context of the present application defines its extension in the direction parallel to the shafts of the rolls. This is of importance insofar as the roll stand is built more stable and solid as the diameter of the rolls increases, which ultimately leads to an increase in the width of the roll stand.
- the pilger rolling mill is provided with a rack holder which is configured such that the rack is receivable on the rack holder at at least two positions spaced from each other in a direction perpendicular to the shafts of the rollers and perpendicular to the direction of movement of the rolling mill, wherein the individual distance between the positions is at least 10 mm.
- the rack is receivable on the rack holder at at least two positions spaced from each other in a direction perpendicular to the shafts of the rollers and perpendicular to the direction of movement of the rolling mill, wherein the individual distance between the positions is at least 10 mm.
- the rack is thus adjustable in height at at least two spaced-apart positions, wherein the individual distance of the positions is at least 10 mm, so that the Rotary axes of the rollers have at least two mutually differing distances from one another.
- This makes it possible to install two rolling stands with differing roll diameters in the same pilger rolling mill.
- the individual distance of the positions is at least 20 mm. In a further embodiment, however, the individual spacing of the positions is at most 100 mm. In a further embodiment, the individual spacing of the positions is at most 40 mm.
- a further embodiment of the present invention is a pilgrim rolling system, which has two rack-symmetrically arranged to a perpendicular to the waves of the rollers extending reference plane rack holder with racks attached thereto.
- the shaft of one of the two rollers preferably the lower roller, carries a drive gearwheel on both sides of the reference plane, wherein the two drive gearwheels each engage in one of the racks and a cylinder axis of the pulley to be received between the rollers lies in the reference plane.
- the reference mirror-symmetrical arrangement of the racks attached to the rack holders reduces the occurrence of torques, which exert a disturbing influence on the rolling process, since the torques occurring compensate each other by the mirror-symmetrical arrangement.
- a mirror-symmetrical arrangement leads to a significantly lower wear of 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 moves away from the rolling mill one parallel to the direction of movement of the rack Roll stand extending axis is arranged pivotably, so that a quick replacement of the roll stand is possible.
- the pivoting of the rack holder away from the rolling stand describes a folding mechanism for the rack holder.
- the unfolding of the rack holder away from the mill stand releases the mill stand so that it can be lifted when lifting z. 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 pivotally mounted about an axis parallel to the direction of movement of the rolling stand, wherein the rack holder is hydraulically clamped in a direction perpendicular to the shafts of the rollers, so that the rack holder in operation the pilger rolling mill receives the forces acting in a direction parallel to the reference plane.
- the rack mount of the pilger rolling mill or parts thereof are interchangeable with a rack holder or parts thereof such that the rack is receivable on the rack holder at at least two positions spaced apart in a direction parallel to the shaft of the rollers.
- the rack holder is constructed in two parts and comprises a base support and an adapter plate.
- the base support is in this case arranged away from the rolling mill stand about a parallel to the direction of movement of the roll stand extending axis.
- the adapter plate can be easily attached to the base support so that the rack mounted on the rack support can assume at least two spaced apart positions in a direction parallel to the shafts of the rollers.
- the pilger rolling mill on a rolling stand, which is movably mounted in a floating slide bearing, preferably on a hydraulically liftable carriage.
- the sliding bearing is designed so that it allows adjusting the clearance between the drive gear and the rack in a direction perpendicular to the shafts of the rollers and perpendicular to the direction of movement of the rolling stand.
- the pilger rolling mill on two vertically stacked rollers, wherein the shafts of the two rollers are connected to each other via two meshing gears such that a rotational movement of one of the two rollers to a rotational movement of the other of the two rollers in the opposite direction leads.
- the shafts of the rolls of the vocational rolling mill each have at least one bearing, wherein at least one bearing of one of the two rolls and a bearing of the other of the two rolls are braced hydraulically against each other.
- the stroke length of the rolling stand which is determined by an eccentricity of a crank pin, on which a push rod is received, set for the largest machinable pipe diameter and is consistent for all machinable pipe diameter.
- 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 size of the area being rolled increases as the rolling force increases. Consequently, the feed length of a single stroke is greater with a larger diameter of the rolls, so that the stroke length of the roll stand is also greater.
- the stroke length of the rolling stand is therefore determined by the largest pipe diameter to be machined in the pilger rolling mill. However, this stroke length is 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 in the rolling process comes into play.
- this can not be arbitrarily high, as from a certain speed of the rolling process, the processing of the tubes becomes inaccurate and more irregularities occur in the wall thickness, so that a loss of quality occurs.
- the stroke length of the roll stand which is determined by an eccentricity of a crank pin on which a push rod is received, adjustable for different machinable pipe diameter.
- the distance between the axis of rotation of the flywheel or the crank mechanism and the point of attachment of the push rod on the flywheel is adapted accordingly, i. the eccentricity of the crank pin is selectably modified modified.
- the crankshaft of the crank mechanism has a co-rotating balancing mass, wherein the balancing mass is designed such that it compensates or virtually compensates for the moments exerted by the first rolling mill received in the pilger rolling mill in the first order, wherein the mass of the first roll stand smaller than the mass of the second rolling stand. It is expedient if this balancing mass is offset from the crank pin by about 180 relative to the axis of rotation of the crankshaft. Under a crankshaft in the context of the present application, each type of shaft is understood with a concentrically arranged crank pin for receiving the push rod.
- the rotating inertial forces occurring during operation of the pilger rolling mill can be completely compensated by means of a balancing mass, which is arranged eccentrically to the axis of rotation of the crankshaft by 180 3 to the articulation point of the push rod offset on the crank mechanism.
- This balancing mass leads to a rotationally symmetrical mass distribution of the crankshaft with push rod with respect to the axis of rotation of the crankshaft and ensures a first order torque compensation.
- the balancing mass is configured such that it compensates or virtually compensates for the moments exerted by the first rolling stand received in the pilger rolling mill in the first order, wherein the mass of the first rolling stand is smaller than the mass of the second rolling stand.
- a second large-mass rolling mill is driven at a smaller angular speed of the crankshaft compared to a first smaller-mass rolling mill.
- the rotating mass forces increase quadratically with the angular velocity of the crankshaft, whereas with the rotating mass they increase only linearly.
- the mass difference between it and the first rolling mill of lesser mass can thus be at least partially due to the corresponding reduction in the rotational speed be compensated.
- a balancing mass which is designed for the first roll stand, the rotating mass forces well compensated well for the second rolling mill 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 mechanism for a mass of the rolling mill, which results from the average value of the masses of the first and the second roll stand.
- the balancing mass is detachably fastened to the crank mechanism, so that it is adapted as precisely as possible to the mass of the second rolling stand accommodated in the pilger rolling mill when replacing the first rolling stand, in order to allow the crank mechanism to run. which is free of free forces or moments, or in which the free forces and moments are minimized.
- the pilger rolling mill on a balancing shaft with a second rotating balancing mass wherein the crankshaft and the compensation swivel are so effectively interconnected via a central control that rotates the balancer shaft at twice the angular speed of the crankshaft during operation of the cold pilger rolling mill and wherein the second balancing mass is configured such that it compensates for or almost compensates for the moments exerted by the first rolling stand received in the pilger rolling mill in second order, the mass of the first rolling mill being smaller than the mass of the second rolling mill.
- free mass forces of the second order are added when operating a pilger rolling mill with an oscillating linear movement of the rolling stand.
- the second-order free inertial forces transmit second order moments via the push rod to the crankshaft and adversely affect the smooth running of the crankshaft.
- the second-order free mass forces oscillate in time at twice the angular velocity of the crankshaft. Therefore, the inertial forces of the second order can be minimized or compensated by means of the balancing shaft according to the invention, which is operatively connected to the crankshaft via a central control and together with the balancing weight attached thereto at twice the crankshaft speed.
- the balancing mass is adjusted so that it allows the best possible compensation of the second-order moments for the first rolling stand, wherein the first roll stand has a smaller mass than the second roll stand.
- a leveling compound which is designed for the first roll stand can well compensate the rotating mass forces also for the second rolling 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.
- Figure 1 shows a schematic sectional side view of the structure of a pilger rolling mill according to an embodiment of the present invention.
- FIG. 2 a shows a front view of a first rolling stand of the pilger rolling mill from FIG. 1.
- FIG. 2b shows an oblique view from above of the rolling stand from FIG. 2a with the rack holder in the open position.
- FIG. 3 a shows a front view of a second rolling stand of the pilger rolling mill from FIG. 1.
- Figure 3b shows an oblique view from above of the rolling stand of Figure 3a with the rack holder in the open position.
- FIG. 1 shows the structure of a pilger rolling mill according to the invention in a schematic lateral sectional view, in which features which are unimportant for the understanding have been dispensed with.
- the illustrated pilger rolling mill comprises a rolling stand 1 with rollers 2, 3, two arranged on the shaft of the lower roller 3 drive gears 6, two attached to each rack holder 4 racks 5, a calibrated rolling mandrel 7 and a feed clamping slide 8.
- the drive gears 6 are not to be seen here, since one of the two is covered by the lower roller 3 and the other has been omitted for clarity in the illustration.
- the racks 5 and rack 4 are also not shown in Figure 1.
- the pilgrim rolling mill has two mirror-symmetrically arranged to a perpendicular to the waves of the rollers extending reference plane 1 1 arranged rack holder 4 with attached fixed racks 5.
- the rack holder 4 are in this case from the rolling stand 1 away from parallel to the Movement direction of the roll stand 1 extending pivot axes 13 pivotally mounted.
- the billet 9 undergoes a step-by-step advance in the direction of the rolling mandrel 7 towards or beyond it, while the rolls 2, 3 rotate over the mandrel 7 and thus horizontally over the billet 9 be moved back and forth.
- 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 reciprocated in a direction parallel to the rolling dome 7 by means of a crank drive, while the rolls 2, 3 themselves receive their rotary motion through the racks 5 fixed relative to the roll stand 1, into which are fixedly connected to the lower roll axes Drive gears 6 engage.
- a translational movement of the rolling stand 1 is converted into a rotational movement of the drive gears 6.
- the drive gears 6 are respectively arranged on the right and left of a lower gear not shown in Figure 1 14, so that the rotational movement of the drive gears 6 causes a rotational movement of the lower gear wheels 14.
- the lower gear wheels 14 in turn mesh with a vertically superposed not shown in Figure 1 upper gear 15 of the same diameter, which is arranged on the shaft of the upper roller 2.
- the upper gear wheels 15 are rotated at the same rotational speed as the lower gear wheels 14, but compared with the lower gear wheels 14 in the opposite direction of rotation.
- the shafts of the upper and lower rollers 2, 3 each have a left and a right bearing, wherein 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 Roller 3 are hydraulically braced.
- the hydraulic clamping of the left and right bearings of the two rollers 2, 3 against each other allows a precise adjustment of the roll gap, whereby a very uniform shape of the tubes is obtained during rolling.
- the advance of the billet 9 via the mandrel 7 takes place with the aid of the feed clamping slide 8, which allows a translational movement in a direction parallel to the axis of the rolling mandrel 7.
- the rollers 2, 3 arranged vertically one above the other in the rolling 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 axis of the pipe.
- the so-called Pilgrim mouth formed by the rollers detects the billet 9 and the rollers 2, 3 press from the outside one small material shaft, which is stretched by a smoothing caliber of the rollers 2, 3 and the rolling mandrel 7 to the intended wall thickness until an idling caliber of the rollers 2, 3, the finished tube releases.
- the roll stand 1 with the rolls 2, 3 attached thereto moves counter to the feed direction of the billet 9.
- the billet 9 is, after reaching the idling caliber of the rolls 2, 3, by a further step on the rolling mandrel 7 advanced, while the rollers 2, 3 return to the rolling stand 1 in its horizontal starting position.
- the billet 9 undergoes a rotation about its axis to achieve a uniform shape of the finished pipe.
- the rolling mill stand in Figure 1 For precise adjustment of the clearance between the drive gear 6 and the rack 5 in a direction perpendicular to the shafts of the rollers 2, 3 and perpendicular to the direction of movement of the rolling stand 1, the rolling mill stand in Figure 1, although not visible, in a floating sliding bearing , implemented here by a hydraulically liftable carriage, movably mounted.
- the hydraulic bearing is characterized in addition to the precise adjustment possibility between drive gear 6 and rack 5 by their ease of assembly, which in particular significantly facilitates and accelerates replacement of the rolling stand 1. As a result, the downtime associated with replacement of the mill stand can be significantly reduced.
- such a bearing of the rollers 2, 3 comes out without wear-prone seals and pistons, i.
- the hydraulic bearing is essentially maintenance and wear-free.
- the stroke length of the pilger rolling mill shown in Figure 1 is set constant for all machinable pipe diameter and by the largest to be machined in the pilger rolling mill pipe diameter. This allows a simplified operation, since no costly changing of the eccentricity 21 of the crank pin is required, but the eccentricity 21 remains the same for all machining processes.
- the stroke length can therefore 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 must be accepted.
- a central control 20 is further provided which is connected both to the drive motor of the balance shaft 17 and to the drive motor of the crankshaft. The controller 20 controls the motors so that their drive shafts rotate in the same direction of rotation, wherein the rotational frequency of the balance shaft 17 is twice as large as the rotational frequency of the crankshaft.
- the controller 20 guarantees an angularly synchronous rotation of the two balancing weights 16, 18 of the crankshaft and balance shaft 17. That is, the two balancing weights 16, 18 are angularly equal after one revolution of the crankshaft, wherein the balancing mass 18 of the balancer shaft 17 in the time that the Crankshaft needed for one revolution, has made two full turns.
- FIG. 2 a shows a front view of a rolling stand of the pilger rolling mill from FIG. 1.
- the roll stand 1 with a mass Mi is designed for the machining of slugs with a diameter between 30 mm and 60 mm.
- the maximum number of strokes of the mill stand, d. H. the maximum number of reciprocating movements of the roll stand per unit time, is in the present embodiment in Figure 2a at 200 / min. Since the productivity of a cold pilgering mill is directly dependent on the number of strokes of the roll stand, for efficiency reasons, a possible largest number of work strokes per minute is sought.
- the roll stand 1 in FIG. 2 a has a mirror-symmetrical arrangement of both the rolls 2, 3 and the drive gears 6 with respect to a reference plane 11 extending perpendicularly to the shafts of the rolls 2, 3, a cylinder axis of the rolls to be received between the rolls 2, 3. the lump 9 is in the reference plane 1 1.
- the drive gears 6 are fixedly connected to the shaft of the lower rollers 3 and engage in the attached to the mirror-symmetrically arranged rack holders 4 racks 5 a.
- the racks 5 are not apparent in Figure 2a, since they are covered by the rack 4 stops.
- the rack holders 4 are hydraulically clamped in a direction perpendicular to the shafts of the rolls.
- the hydraulic clamping takes place via a system of hydraulic nuts 12, which consist essentially of an annular piston and a cylinder.
- a force build-up takes place in the direction perpendicular to the shafts of the rollers 2, 3.
- clamping or pushing forces can be built up temporarily, so that the rolling stand 1 during the rolling process in the direction parallel to the shafts of the rollers 2, 3 at a fixed position is thus prevented from sliding away due to the resulting torsional forces.
- the rack holder 4 shown in Figure 2a is also pivotally away from the mill stand about a parallel to the rack 5 extending pivot axis 13 pivotally mounted, which is not apparent from Figure 2a due to their orientation in the image plane.
- the drive gears 6 lose contact with the racks 5, so that the rolling stand 1 is not blocked by the rack holder 4 when lifting by means of a crane.
- the rolling stand 1 can be replaced unhindered and in a simple and fast way. This entails greater flexibility of the machining process with regard to an expanded range of machinable pipe diameters.
- FIG. 2b shows an oblique view from above of the rolling mill stand from FIG. 2a, but with the toothed rack holder 4 in an open position such that the toothed rack holder 4 has been pivoted away from the rolling stand about its pivot axis 13 in accordance with the arrow direction shown and consequently attached to the rack holder 4 Rack 5 has no contact with the drive gear 6 again.
- the roll stand 1 is thus no longer blocked by the rack holder 4 and can be removed by means of a crane in a simple and fast way by lifting out of the pilger rolling mill and replaced by a second rolling stand V with other dimensions.
- FIG. 3 a shows a front view of a second rolling stand V of the pilger rolling mill from FIG. 1.
- this is a rolling stand V with larger dimensions with regard to the three spatial dimensions and the diameter of the rollers 2 ', 3' and drive gears 6 ', which, however, can be installed in the same pilger rolling mill from FIG.
- the larger dimensions of the roll stand 1 'shown in FIG. 3a are also reflected in a mass which is increased in comparison to the roll stand 1 from FIGS. 2a and 2b.
- the mass of the second stand is in the present embodiment at 2.5 times the mass Mi of the rolling mill 1 of Figure 2a and 2b.
- 3a is designed for the machining of bales with a diameter of between 40 mm and 88 mm and thus for larger diameters compared to the roll stand 1 from FIGS. 2a and 2b.
- the maximum stroke rate of the roll stand V is 150 / min at a correspondingly lower value.
- the toothed rack holder 4 ' according to the invention is located in FIG. 3a at a position farther from the reference plane 11' perpendicular to the reference plane 11 'as compared to the toothed rack holder 4 shown in FIG. 2a.
- this is achieved allows the rack holder 4, 4 'is constructed in two parts. It includes one hand a base support and on the other hand an adapter plate which is attachable to the base support such that the respective drive gear 6, 6 'of the roll stand 1, 1' at at least two spaced-apart positions in a direction perpendicular to the reference plane 1 1 in the respective rack holder 4th , 4 'fixed rack 5, 5' can engage.
- this adapter plate is built in a direction parallel to the waves of the rollers 2, 3 larger than in the case of Figure 3a, so that the rack 5 a smaller distance from the reference plane 1 1 in the direction of the normal of the reference plane 1 first having.
- FIG. 3b shows an oblique view from above of the rolling stand 1 'from FIG. 3a.
- the rack holder 4 ! in this case has been pivoted away from the roll stand 1 'about a pivot axis 13' extending parallel to the direction of movement of the roll stand 1 'and is corresponding to Figure 2b in an open position such that the rack 5' attached to the rack holder 4 'no longer contact to the drive gear 6 'of the roll stand 1'.
- the rolling stand 1 ' can be removed from the pilger rolling mill in a simple and fast manner with the aid of the pivoting device releasing the rolling stand V.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
- Metal Rolling (AREA)
Abstract
Description
Claims
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 |
Publications (2)
Publication Number | Publication Date |
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EP3393689A1 true EP3393689A1 (de) | 2018-10-31 |
EP3393689B1 EP3393689B1 (de) | 2020-06-10 |
Family
ID=57570761
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP16813355.1A Active EP3393689B1 (de) | 2015-12-23 | 2016-12-20 | Kaltpilgerwalzanlage |
Country Status (8)
Country | Link |
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US (1) | US11045848B2 (de) |
EP (1) | EP3393689B1 (de) |
JP (1) | JP6875402B2 (de) |
KR (1) | KR102589419B1 (de) |
CN (1) | CN108430660B (de) |
DE (1) | DE102015122701A1 (de) |
ES (1) | ES2819310T3 (de) |
WO (1) | WO2017108784A1 (de) |
Families Citing this family (8)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
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 |
CN109317519B (zh) * | 2018-10-22 | 2024-06-18 | 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 |
Family Cites Families (23)
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US2387515A (en) * | 1942-05-13 | 1945-10-23 | Rockrite Processes Inc | Reducing mill |
US2537356A (en) * | 1942-11-28 | 1951-01-09 | See Fabriks Aktiebolag | Rolling mill for the production of conical tubes |
US2738682A (en) * | 1952-12-30 | 1956-03-20 | Skardal Karl Arvid | Wire guide |
GB786675A (en) * | 1955-08-05 | 1957-11-20 | W H A Robertson & Company Ltd | Rolling mills |
US3369383A (en) * | 1965-07-16 | 1968-02-20 | Gen Dynamics Corp | Rolling mill system |
FR1502302A (fr) | 1966-11-25 | 1967-11-18 | Vni I Kt I Trubnoi Promy | Mécanisme d'actionnement de la cage d'un laminoir à froid pour tubes |
DE6752062U (de) | 1968-04-09 | 1969-02-20 | Mannesmann Meer Ag | Zahnstangenanstellung an kaltpilgerwalzwerken |
US3600913A (en) * | 1968-09-04 | 1971-08-24 | Wean Ind Inc | Pilger mill die adjustment |
FR2510913A1 (fr) | 1981-08-06 | 1983-02-11 | Vallourec | Dispositif de changement d'outillage de laminoir a froid a pas de pelerin |
US4660400A (en) | 1983-12-21 | 1987-04-28 | Moskovsky Institut Stali I Splavov | Pilger mill stand |
DE3674781D1 (de) | 1986-03-04 | 1990-11-08 | Mannesmann Ag | Walzgeruest. |
JPS6384707A (ja) * | 1986-09-26 | 1988-04-15 | Kobe Steel Ltd | 圧延機の軸受装置 |
IT1220852B (it) * | 1988-03-01 | 1990-06-21 | Danieli Off Mecc | Dispositivo di sostituzione cilindri di gabbie di laminazione |
US4993251A (en) | 1989-07-07 | 1991-02-19 | Sandvik Special Metals Corporation | Rollstand having easily replaceable roll dies |
DE4124691C1 (de) * | 1991-07-22 | 1992-02-27 | Mannesmann Ag, 4000 Duesseldorf, De | |
RU2086319C1 (ru) | 1994-05-18 | 1997-08-10 | Акционерное общество "Электростальский завод тяжелого машиностроения" | Рабочая клеть стана холодной прокатки труб |
UA65925A (en) * | 2003-07-03 | 2004-04-15 | Novokramatorsk Machine Works Cjsc | Method for adjustment of value of forced rolling radius and cold-rolling pilger mill for tubes for its embodiment |
CN2663041Y (zh) | 2003-11-05 | 2004-12-15 | 上海兴森特殊钢有限公司 | 具有双平衡块的周期式双管冷轧管机用曲柄连杆机构 |
US20090113975A1 (en) * | 2007-11-05 | 2009-05-07 | Fletcher Calvin Eddens | Roll die assemblies for pilger mills |
DE102011052739B4 (de) * | 2011-08-16 | 2017-03-02 | Sandvik Materials Technology Deutschland Gmbh | Pilgerwalzanlage |
DE102012112398B4 (de) | 2012-12-17 | 2018-05-30 | Sandvik Materials Technology Deutschland Gmbh | Pilgerwalzanlage mit einem Kurbeltrieb |
DE102013112371A1 (de) | 2013-11-11 | 2015-05-13 | Sandvik Materials Technology Deutschland Gmbh | Kaltpilgerwalzanlage sowie Verfahren zum Umformen einer Luppe zu einem Rohr |
KR101552514B1 (ko) * | 2014-04-25 | 2015-09-14 | 한전원자력연료 주식회사 | 냉간 필거 압연기의 필거 다이 조립체의 갭 조절장치 |
-
2015
- 2015-12-23 DE DE102015122701.0A patent/DE102015122701A1/de not_active Withdrawn
-
2016
- 2016-12-20 WO PCT/EP2016/081913 patent/WO2017108784A1/de active Application Filing
- 2016-12-20 EP EP16813355.1A patent/EP3393689B1/de active Active
- 2016-12-20 CN CN201680076154.6A patent/CN108430660B/zh active Active
- 2016-12-20 US US16/064,493 patent/US11045848B2/en active Active
- 2016-12-20 JP JP2018533657A patent/JP6875402B2/ja active Active
- 2016-12-20 KR KR1020187020894A patent/KR102589419B1/ko active IP Right Grant
- 2016-12-20 ES ES16813355T patent/ES2819310T3/es active Active
Also Published As
Publication number | Publication date |
---|---|
DE102015122701A1 (de) | 2017-06-29 |
KR102589419B1 (ko) | 2023-10-13 |
US20190084020A1 (en) | 2019-03-21 |
JP6875402B2 (ja) | 2021-05-26 |
CN108430660B (zh) | 2020-07-28 |
EP3393689B1 (de) | 2020-06-10 |
ES2819310T3 (es) | 2021-04-15 |
CN108430660A (zh) | 2018-08-21 |
WO2017108784A1 (de) | 2017-06-29 |
JP2019503871A (ja) | 2019-02-14 |
KR20180096752A (ko) | 2018-08-29 |
US11045848B2 (en) | 2021-06-29 |
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