EP3525946B1 - Multi-stand rolling mill for rod-shaped bodies comprising mill stands with four motorized rolls - Google Patents
Multi-stand rolling mill for rod-shaped bodies comprising mill stands with four motorized rolls Download PDFInfo
- Publication number
- EP3525946B1 EP3525946B1 EP17797186.8A EP17797186A EP3525946B1 EP 3525946 B1 EP3525946 B1 EP 3525946B1 EP 17797186 A EP17797186 A EP 17797186A EP 3525946 B1 EP3525946 B1 EP 3525946B1
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- European Patent Office
- Prior art keywords
- rolling mill
- mill
- drive shaft
- rolling
- stand
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- 238000005096 rolling process Methods 0.000 title claims description 122
- 230000002441 reversible effect Effects 0.000 claims description 5
- 230000004913 activation Effects 0.000 claims 2
- 238000003801 milling Methods 0.000 claims 2
- 238000011144 upstream manufacturing Methods 0.000 claims 2
- 230000000694 effects Effects 0.000 description 10
- 230000033001 locomotion Effects 0.000 description 5
- 230000005540 biological transmission Effects 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 238000006073 displacement reaction Methods 0.000 description 2
- 238000004513 sizing Methods 0.000 description 2
- 230000003213 activating effect Effects 0.000 description 1
- 230000000712 assembly Effects 0.000 description 1
- 238000000429 assembly Methods 0.000 description 1
- 230000008859 change Effects 0.000 description 1
- 239000003638 chemical reducing agent Substances 0.000 description 1
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- 238000010438 heat treatment Methods 0.000 description 1
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- 238000012423 maintenance Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 230000009467 reduction Effects 0.000 description 1
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Classifications
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
- B21B35/02—Drives for metal-rolling mills, e.g. hydraulic drives for continuously-operating mills
- B21B35/04—Drives for metal-rolling mills, e.g. hydraulic drives for continuously-operating mills each stand having its own motor or motors
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B17/00—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling
- B21B17/02—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling with mandrel, i.e. the mandrel rod contacts the rolled tube over the rod length
- B21B17/04—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling with mandrel, i.e. the mandrel rod contacts the rolled tube over the rod length in a continuous process
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B17/00—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling
- B21B17/14—Tube-rolling by rollers of which the axes are arranged essentially perpendicular to the axis of the work, e.g. "axial" tube-rolling without mandrel, e.g. stretch-reducing mills
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B13/00—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories
- B21B13/02—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories with axes of rolls arranged horizontally
- B21B2013/025—Quarto, four-high stands
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B23/00—Tube-rolling not restricted to methods provided for in only one of groups B21B17/00, B21B19/00, B21B21/00, e.g. combined processes planetary tube rolling, auxiliary arrangements, e.g. lubricating, special tube blanks, continuous casting combined with tube rolling
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B31/00—Rolling stand structures; Mounting, adjusting, or interchanging rolls, roll mountings, or stand frames
- B21B31/16—Adjusting or positioning rolls
- B21B31/20—Adjusting or positioning rolls by moving rolls perpendicularly to roll axis
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21B—ROLLING OF METAL
- B21B35/00—Drives for metal-rolling mills, e.g. hydraulic drives
- B21B35/02—Drives for metal-rolling mills, e.g. hydraulic drives for continuously-operating mills
- B21B35/025—Drives for metal-rolling mills, e.g. hydraulic drives for continuously-operating mills for stretch-reducing of tubes
Definitions
- the present invention relates to the field of rolling systems of tubular bodies. More precisely, the invention relates to a multi-stand rolling mill comprising mill stands with four rolls motorized by means of control drive shafts.
- the rolling mill described in patent EP 2391460 has various drawbacks, the first of which is related to the complicated configuration of the mechanical system used for rotating the mill stand rolls.
- the rolls are motorized by means of retractable drive shafts actuated by external controls.
- the external controls comprise two motors. Each motor is connected to a split ratio motor with two outputs, a first output controls a first drive shaft which engages/disengages a first half-joint integral with a first roll to be actuated.
- a second output of the motor comprises a second drive shaft, with axis parallel to the first drive shaft, which actuates, via a transmission, a third drive shaft having an axis orthogonal to the first and to the second drive shaft.
- the drive shafts 31, 32, 33, 34 are operatively released from the corresponding roll 11, 12, 13, 14.
- the first drive shaft 31 and the third drive shaft 33 are orientable drive shafts according to the definition provided above. More precisely, these two drive shafts 31, 33 are inclinable between the first reference position, in which the rotation axis 311, 333 of each orientable drive shaft 31, 33 is parallel to the rotation axis of the corresponding roll 11, 13, and a second reference position, in which the drive shafts 31, 33 themselves assume a position, which is entirely outside the space comprised between the support plane 101 and the reference plane 102. Specifically, the third drive shaft 33 is completely under the support plane 101, while the first drive shaft 31 is completely over the reference plane 102.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Metal Rolling (AREA)
Description
- The present invention relates to the field of rolling systems of tubular bodies. More precisely, the invention relates to a multi-stand rolling mill comprising mill stands with four rolls motorized by means of control drive shafts.
- The use of multi-stand rolling mills with motorized rolls, in which each mill stand is provided with four rolls, is known for rolling rod-shaped bodies, in particular tubes or bars. The use of four-roll mill stands, in which the axes of the two adjacent, or contiguous, rolls are arranged by 90°, allows a more uniform peripheral speed with respect to what can be obtained with three-roll mill stands in which the rotation axes of two adjacent rolls are arranged at 120°. Substantially, the four-roll mill stands allow a greater feed effect, the number of mill stands being equal. At the same time, with respect to a three-roll mill stand, the presence of four rolls advantageously reduces the pinching (crushing) effect of the edges of the rolls of on the rod-shaped body. This translates into a higher end quality of the rolled product.
- Patent
EP 2391460 to the Applicant relates to such a rolling mill comprising a central body, which defines a space in which a plurality of mill stands is accommodated, each of which having four motorized rolls. Each mill stand has a conformation obtained by rotating a previous or successive mill stand by 180 degrees with respect to the vertical axis. For each mill stand, the rotation axis of two non-contiguous rolls is inclined by 22,5° with respect to a horizontal plane, while the rotation angle of the other two non-contiguous rolls is inclined by 67,5°, again with respect to the same horizontal plane. - The rolling mill described in patent
EP 2391460 has various drawbacks, the first of which is related to the complicated configuration of the mechanical system used for rotating the mill stand rolls. For each mill stand, the rolls are motorized by means of retractable drive shafts actuated by external controls. The external controls comprise two motors. Each motor is connected to a split ratio motor with two outputs, a first output controls a first drive shaft which engages/disengages a first half-joint integral with a first roll to be actuated. A second output of the motor comprises a second drive shaft, with axis parallel to the first drive shaft, which actuates, via a transmission, a third drive shaft having an axis orthogonal to the first and to the second drive shaft. Such third drive shaft engages/disengages a second half-joint, which is integral with a second roller to be moved contiguous to the first. The engagement/disengagement of the first drive shaft and the third drive shaft and the third drive shaft in/from the respective half-joint is achieved by means of a corresponding hydraulic thrust device. - The complex configuration of the system of drive shafts described above is one of the main drawbacks of the rolling mill described in
EP 2391460 . In this regard, the presence of the split ratio motor which actuates the first and the second drive shaft, like the presence of the 90° transmission necessary to transmit the motion of the second and third drive shaft, appear critical. The presence of these transmission assemblies strongly weighs on the overall size of the supporting structure of the rolling mill in both vertical and transversal terms. In this regard, it is worth emphasizing the considerable length of the two drive shafts (first and second) inclined by 22,5° with respect to the horizontal. Such length strongly weighs on the transversal extension of the rolling mill. - In the solution described in
EP 2391460 , the radial position of the rolls can be adjusted by means of an eccentric adjustment system. In this regard, each roll is provided with bearings mounted inside eccentric bushings, one on the control system (drive shaft side), the other on the opposite side. The two bushings are connected by a bridge which connects them rigidly. An eccentric adjustment device, which controls the eccentric rotation by exploiting a connection tube, which is integral with the control side eccentric bushing, is arranged on the control side of the roll. The adjustment device is integral with the supporting structure of the rolling mill and rotates between a working position, in which it is connected to the tube, and a resting position, in which it is disconnected from the tube itself. The adjustment device comprises a reducer, e.g. formed by a worm screw, which imposes the eccentric rotation. The complexity of the eccentricity adjustment device is another technical limit of the rolling mill described inEP 2391460 . In particular, the adjustment device is critical also in terms of reliability. In this regard, it is worth noting that in the concerned solution, the adjustment device is also configured to interact with the structure of the mill stand which supports the rolls to define a retainer for the mill stand itself in the working position. This further function performed by the device contributes to its complexity. - From these considerations, the need arises to improve the rolling mill described above, particularly in terms of transversal and vertical dimensions. Therefore, it is a main task of the present invention to provide a rolling mill for four-roll mill stands which allows solving the drawbacks indicated above. In the scope of this task, it is a first object of the present invention to provide a rolling mill in which the rolls are actuated by means of a less complicated system than the one used in the known solutions. It is another object of the present invention to provide a rolling mill, in which the radial position of the rolls is adjusted by means of less complicated technical solutions than those used in the known solutions. A not last object of the present invention is to provide a rolling mill which is reliable and easy to implement at competitive costs.
- These and other objects, which will be more apparent in light of the description which follows, are achieved by a rolling mill for tubular bodies, comprising:
- a structure defining a housing for at least one mill stand with four rolls, wherein each roll is operatively connectable to a drive shaft, said housing being vertically delimited between a horizontal support plane and a reference plane parallel to said support plane;
- four drive shafts, each of which can rotate a respective roll of said mill stand, wherein each drive shaft can axially extend and retract in reversible manner, passing from a retracted configuration, in which it is operatively disconnected from the respective roll, to an extended configuration, in which it is operatively connected to the respective roll, and vice versa,
- Objects and advantages of the present invention will be apparent from the following detailed description of an embodiment of the same and from the accompanying drawings provided by way of non-limiting example only, in which:
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Figure 1 is a cross section view of a rolling mill according to the invention; -
Figure 2 is a section view of a mill stand of a rolling mill according to the present invention; -
Figures 3 and4 are views related to a group of components of the rolling mill ofFigure 1 in a first and a second operative configuration, respectively; -
Figure 5 is a view of the rolling mill inFigure 1 during a mill stand replacement operation; -
Figures 6, 7 and 7A are views of a drive shaft of a rolling mill according to the present invention; -
Figures 8 and 9 are views of another drive shaft of a rolling mill according to the present invention; -
Figures 10 and 11 are views related to an actuating device of the drive shaft ofFigures 8 and 9 ; - Figures from 12 to 16 show the drive shaft in
Figures 8 and 9 during the rotation from a first reference position to a second reference position; -
Figure 17 is a view related to a possible embodiment of a rolling mill according to the present invention; -
Figures 18 and 18A are respectively a side view and a front view of mill stands of a rolling mill according to the present invention; -
Figures 19, 19A are respectively a side view and a front view of a mandrel-holder stand of a rolling mill according to the present invention. - The same reference numbers and letters in the figures refer to the same elements or components.
- The present invention thus relates to a rolling mill for tubular bodies, generically indicated by reference numeral 1 in the figures. The rolling mill 1 according to the invention comprises a
structure 3 defining ahousing 4 for one or more rolling mill stands 10 defining arolling axis 100.Figure 1 is a view of the rolling mill taken along a cross section with respect to therolling axis 100. - The mill stands 10 of the rolling mill 1 comprise four
rolls Figure 2 ) of eachroll -
Figure 2 shows in detail amill stand 10, which has a configuration known in itself. In particular, the mill stand 10 comprises a first pair of non-contiguous rolls 11, 13 having a rotation axis which is inclined by an angle α1 of 22,5° with respect to thesupport plane 101 of themill stand 10, while the rotation angle of the other non-contiguous pair ofrolls support plane 101 itself. Eachroll bushing first side sleeve control drive shaft bushing second side sleeve first sleeve longitudinal pin bushing rolls - Furthermore, with the removable roller solution, a standard type lathe may be used to restore the surface of the worn rolls, the use of a special lathe for turning the rolls without removing them from the mill stand being no longer necessary.
- The position of the
rolls axis 100 can be adjusted by means of an eccentric adjustment system which may be, for example, of the type described in patent applicationEP2391460 mentioned above. In particular, eachroll longitudinal pin eccentric bushings 371, 372 at its sides, one on the control side (drive shaft side) and one on the opposite side, the twobushings 371, 372 are connected by arigid bridge 373 which transmits the rotation from one bushing to another. Theeccentric bushing 372 of the control side can rotate by means of acontrol device 60 of the eccentric rotation described below. - Again according to a solution known in itself, the eccentric systems related to two contiguous, or adjacent, rolls are connected by means of
conical tooth sectors 79 configured so as to transmit the rotation of an eccentric system, controlled from the outside, to an eccentric bushing driven by an eccentric system of an adjacent roll, in which such driven bushing is connected on the side opposite to the control side. In this manner, for example, in the configuration of the mill stand 10 shown inFigure 2 , the rotation of the eccentric system associated with the roll with reference to 14 is transmitted to the eccentric system associated with the roll indicated byreference numeral 11. - The
housing 4 in which the mill stands 10 are accommodated is vertically delimited between thehorizontal support plane 101, on which the mill stands 10 rest, and areference plane 102, which is parallel to thesupport plane 101. The distance between the mentionedplanes height 5 of the mill stands 10 (seeFigure 2 ) measured according to the same direction. In this manner, the mill stands 10 can be introduced in thehousing 4 and removed from it according to atransversal displacement direction 105 substantially orthogonal to the rollingdirection 100. In this regard, the replacement of the mill stands 10 may be achieved by means of the system and according to the principles described in patentEP 2391460 . - For each mill stand 10, each
roll corresponding drive shaft actuating motor shaft corresponding motor drive shafts EP 2391460 , in which the four drive shafts are actuated by only two motors. - Each
drive shaft corresponding roll roll corresponding roll side sleeve - The rolling mill 1 according to the present invention comprises at least one
inclinable drive shaft rotation axis drive shaft corresponding roll rotation axis corresponding roll inclinable drive shaft drive shaft support plane 101 and thereference plane 102. In this manner, in the rotated position, said at least onedrive shaft mill stand 10, i.e. the transversal movement of the mill stand along thetransversal direction 105. For the purposes of the present invention, the expression "rotation axis of the drive shaft" means the rotation axis of the portion of the drive shaft which connects/couples to thecorresponding side sleeve roll - In the operative configuration shown in
Figures 1 and3 , thedrive shafts corresponding side sleeve first drive shaft 31 and thethird drive shaft 33 respectively actuate the twonon-contiguous rolls support plane 101. Thesecond drive shaft 32 and thefourth drive shaft 34 actuate the other tworolls support plane 101 itself. - In the configuration shown in
Figure 4 , thedrive shafts roll figures 3 and4 , it is worth noting that thefirst drive shaft 31 and thethird drive shaft 33 are orientable drive shafts according to the definition provided above. More precisely, these twodrive shafts rotation axis orientable drive shaft corresponding roll drive shafts support plane 101 and thereference plane 102. Specifically, thethird drive shaft 33 is completely under thesupport plane 101, while thefirst drive shaft 31 is completely over thereference plane 102. - Again with reference to
Figures 3 and4 , thesecond drive shaft 32 and thefourth drive shaft 34 are not orientable drive shafts, but may be extended or retracted according to a direction parallel to that of thecorresponding roll Figure 4 , the twodrive shafts 32, 34 (not orientable) are shown in the retracted configuration, in which they are completely outside the space comprised between thesupport plane 101 and thereference plane 102. In such retracted configuration, thesecond drive shaft 32 is completely under thesupport plane 101, while thefourth drive shaft 34 is completely over thereference plane 102. - As a whole, it is worth noting that in the configuration of
Figure 4 , all thedrive shafts support plane 101 and thereference plane 102, space which is useful for displacing the mill stand transversally. In this regard,Figure 5 is a transversal view of the rolling mill inFigure 1 in a configuration corresponding to that ofFigure 4 . It is worth noting that the mill stand 10 can be displaced transversally (direction 105) to anunloading platform 801 to be replaced by a new mill stand (indicated by reference numeral 10') previously located on aloading platform 802. In particular, the new mill stand 10' is introduced transversally and pushes the mill stand 10 towards the unloadingplatform 801, according to the principles described inEP 2391460 .Figures 6 and 7 show a possible embodiment of the second drive shaft 32 (also valid for the fourth drive shaft 34) respectively in the retracted configuration and in the extended configuration.Figure 7A is an axial view of the drive shaft inFigure 7 . As shown, thesecond drive shaft 32 comprises afirst portion 32A operatively connected tomotor 42, which actuates, i.e. rotates, the drive shaft itself. Thesecond drive shaft 32 also comprises asecond portion 32B which is movable with respect to thefirst portion 32A. Suchsecond portion 32B comprises an end which operatively couples to theside sleeve 702 associated with thesecond roll 12. Thesecond portion 32B is movable with respect to thefirst portion 32A by effect of aninner spring 39. The latter acts so as to move thesecond portion 32B away from thefirst portion 32A. The twoportions portion 32B is defined by a tube which is axially movable, rotating and inclinable between the toothings to compensate for the eccentric movement which is imposed between the axis of thesecond portion 32B and that of thefirst portion 32A by effect of theeccentric control device 60 described below. - To vary the configuration of the
second drive shaft 32, the use of thrust means is envisaged. Such means vary the position of thefirst portion 32A with respect to thesecond portion 32B. Preferably, the thrust means comprise ahydrodynamic actuator 81 stably fixed tostructure 3 of the rolling mill 1, the rod of which is integral with aslide 720 which is movable with respect tostructure 3 and also with respect to thedrive shaft 32.Such slide 720 supports the control device mentioned above. - Again with reference to
figures 6 and 7 , thefirst portion 32A of thedrive shaft 32 does not vary its position during the change of configuration because it remains stably connected to thecorresponding motor 42 fixed in turn to structure 3 (see for exampleFigure 1 ). Theslide 720 is moved in axial sense by theactuator 81 and moves independently from thedrive shaft 32. This means a condition in which the parts of thedrive shaft slide 720 translates without rotating. Thespring 39 shown above pushes thesecond portion 32B in the coupling configuration offigure 7 . In such configuration, the rod of theactuator 81 is extended and keeps theslide 720 in advanced position and more precisely so that theend part 720B of theslide 720 assumes a more advanced position (towards the roll 12) with respect to acollar 32C integral with thesecond portion 32B ofdrive shaft 32. The variation of configuration from extended (Figure 7 ) to retracted (Figure 6 ) occurs by activating theactuator 81.Slide 720 is retracted byactuator 81 towardsmotor 42. During such displacement, theend part 720B ofslide 720 intercepts thecollar 32C of thesecond portion 32B, feeding the latter towardsmotor 42, in opposition tospring 39. Such feeding determines the operative release of thedrive shaft 32 of thecorresponding roll 12. -
Figures 8 and 9 show a possible embodiment of the first drive shaft 31 (also valid for the third drive shaft 33) respectively in the retracted configuration and in the extended configuration. Also thefirst drive shaft 31 comprises afirst portion 31A connected to the correspondingactuating motor 41 and asecond portion 31B, movable with respect to thefirst portion 31A, and provided with an end which operatively couples to thefirst roll 11. Thefirst portion 31A is connected to the correspondingactuating motor 41 by means of a Cardan joint 48 which defines a rotation axis about which thedrive shaft 31 is rotated between the reference positions defined above. From the mechanical point of view, the twoportions first drive shaft 31 are connected in manner substantially corresponding to that envisaged for theportions second drive shaft 32. - The
first drive shaft 31 is rotated by an actuating device which rotates and guides the drive shaft itself between the two positions defined above. Figures from 10 to 16 show a possible embodiment of such device which comprises alever body 8 hinged to structure 3 so as to rotate about an axis 7.Body 8 comprises afirst part 8A, connected to ahydraulic actuator 82, and asecond part 8B which configures a "fork" provided with twotines 88B. Suchsecond part 8B develops from a side opposite to thefirst part 8A with respect to the rotation axis 7 of thelever body 8. Thesecond portion 31B of thefirst drive shaft 31 comprises pairs ofwheels 36 diametrically opposite (see alsofigures 8 and 9 ) and configured to slide inside twoguides 85 fixed tostructure 3.Such guides 85 develop on substantially oppositevertical planes 185 between which thedrive shaft 31 is operatively arranged.Wheels 36 are moved alongguides 85 by means oftines 88B which intervene on them following the rotation of thelever body 8 about the mentioned axis 7. In this regard, Figures from 12 to 16 show the steps of the rotation, induced by the actuating device, between the first and the second reference position. In such figures, for description purposes only, thereference plane 102 is inclined by 22,5° with respect to ahorizontal reference line 106. In the actual configuration (seefigures 1 ,3 and4 ) thereference plane 102 is horizontal. - In
Figure 12 , thefirst drive shaft 31 is shown in the extended configuration, in which it is operatively connected to thecorresponding roll 11. In the condition inFigure 12 ,wheels 36 integral with thedrive shaft 31 are outside guides 85 because thedrive shaft 31 must be free to rotate the corresponding roll. In the condition inFigure 13 , thefirst drive shaft 31 is shown in the retracted (releasing) configuration, in which it is free to rotate about the axis configured by theCardan joint 48. In particular, before releasing thefirst drive shaft 31,wheels 36 are aligned withguides 85, preferably by means of a motor encoder which controls the rotation of thefirst drive shaft 31 to the required condition. In the condition ofFigure 13 ,wheels 36 of thedrive shaft 31 are arranged substantially at the inlet of the corresponding guides 85. The rotation of thefirst drive shaft 31 is determined by the thrust of thehydraulic actuator 82 on thefirst part 8A of thelever body 8 so as to rotate thesecond part 8B in a sense such thattines 88B act onwheels 36. More precisely, following such rotation,wheels 36 are pushed bytines 88B along guides 85 which are shaped so as to cause a lifting of thefirst drive shaft 31 and a concurrent sliding of thesecond portion 31B with respect to thefirst portion 31A (see in sequencefigures 13 ,14 and 15 ). Such sliding occurs towards the rotation axis of thedrive shaft 31 configured by theCardan joint 48. The final position (second reference position) of thedrive shaft 31 is established by the reaching of the end of travel in guides 85 (condition inFigure 16 ). In particular, thedrive shaft 31 is held in the second reference position bytines 88B. - It is apparent that the reverse rotation of the
drive shaft 31, from the second to the first reference position, is obtained by means of a rotation of thelever body 8 in the opposite side. Such inverse rotation materializes in a lowering oftines 88B which determines a consequent lowering of thefirst extension 31. - For the rotation of the
third drive shaft 33, an actuation device equivalent to the new just described above may be used. - According to a preferred embodiment of the invention, the actuation device is configured also to vary the configuration of the
first drive shaft 31 from the retracted condition to the extended condition. In this regard, the translation movement of thesecond part 31B, at the end of which thefirst drive shaft 31 is operatively released from the correspondingroll 11, may also be obtained by effect of the rotation of thelever body 8 and thus by the thrust oftines 88B. The latter, by acting onwheels 36, move thesecond portion 31B of thedrive shaft 31 towards the rotation axis configured by the Cardan joint 48, until the rotation of the drive shaft itself starts according to what has been described above. In other words, the actuating device described above is advantageously configured to vary the configuration of thefirst drive shaft 31 and to rotate it between the two reference positions. In other words, both operations are advantageously performed with only one device. - With reference again to
Figures 1 and3 , according to another aspect of the invention, thesecond drive shaft 32 and thefourth drive shaft 34 comprise acontrol device 60 to adjust the eccentric system by means of which the radial position of the rotation axis of the rolls may be varied with respect to the rollingaxis 100. For ease of description, reference will be made hereinafter to thesecond drive shaft 32, but the conditions remain valid also for thefourth drive shaft 34. In general, unlike the solutions known in the prior art, in particular the solution described in patentEP 2391460 , thecontrol device 60 is advantageously installed on the slide 720 (indicated above), moved through theactuator 81, and not on the fixed structure. This solution thus allows simplifyingstructure 3 and thus eliminating, for example, the tipping control device described inEP 2391460 . At the same time, when the second drive shaft takes the coupling configuration, thecontrol device 60 is arranged in the correct operative position to intervene on the eccentric adjustment system. In other words, the control device operatively connects to the eccentric system when thedrive shaft 32 reaches the coupling configuration. - With reference to
figures 6, 7 and 7A , thecontrol device 60 is in all cases integral with theslide 720, which translates axially by effect of the action of the thrust means 81 described above. Thecontrol device 60 comprises aratio motor 61 which acts on aneccentric sleeve 27 with respect to thehollow shaft 322 of thesecond part 32B connected to, and rotated by, thefirst portion 32A of the drive shaft integral withmotor 42. When thehollow shaft 322 is coupled to theside sleeve 702 of the corresponding roll 12 (extended configuration),sleeve 27 engages in the eccentric system associated with thesecond roll 12 so that a rotation of theeccentric sleeve 27 corresponds to a rotation of said eccentric system. The rotation of the eccentric system translates into a variation of the radial position of the roll and thus of the set of elements 602-502-702 which allows the rotation thereof. At the same time, by effect of the connection withsleeve 702, the corresponding radial position of thesecond portion 32B of thedrive shaft 32 is varied. The rotation of theeccentric sleeve 27 is adjusted by theratio motor 61 which acts on a crown gear externally associated with the sameeccentric sleeve 27. By effect of the conicaltoothed sectors 79 envisaged in themill stand 10, the rotation of the eccentric system associated with thesecond roll 12 is also transferred to the eccentric systems associated with thethird roll 13. - The
control device 60 described above is envisaged also for thefirst drive shaft 34, as clearly visible inFigures 3 and4 , for example. By effect of the transmission ensured by theconical tooth sectors 79, no control device is associated with thefirst drive shaft 31 and with thethird drive shaft 33. - According to a further aspect of the present invention, shown in
Figures 3 and4 , the rolling mill 1 comprises a retainingdevice 80 to lock the mill stand 10 in thehousing 4 in a predetermined position. The latter is defined so that therolls axis 100. In particular, the retainingdevice 80 is installed underneath thesupport plane 101 and comprises aretainer 880 configured to assume at least one locking position and at least one unlocking position. In the unlocking position, theretainer 880 intercepts a housing of thebase 10C of the mill stand 10 fixing the position of the latter in thehousing 4 of the rolling mill. In the releasing position, theretainer 880 is under or on the level of thesupport plane 101, thus allowing the translation of the mill stand 10 in the movement space defined between the twoplanes device 80 is entirely independent from the adjustment device of the eccentric, contrary to what has been envisaged, for example in the solution described inEP 2391460 . - The rolling mill 1 according to the invention may be advantageously used as sizer rolling mill for making tubular bodies. In particular, the sizing is performed by means of a plurality of four-roll mill stands having the peculiarities described above.
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Figure 17 is a side view of a rolling mill 1 according to the invention in a preferred embodiment, in which thehousing 4 of the rolling mill 1 defines a first rolling section 410 and asecond rolling section 420. The latter is defined downstream of the first sector 410 with respect to the feeding sense (indicated with reference 2) of the perforated bodies along theroll 100. In the first section 410, a first plurality of rolling mill stands 10A,10B (hereinafter also indicated with the expression first mill stands 10A,10B) is arranged in succession along the rollingaxis 100 starting from aninlet section 4A of thehousing 4. In particular, the mill stands 10A, 10B implement rolling on mandrel. In thesecond section 420, instead, a second plurality of rolling mill stands 15A, 15, 15B (hereinafter also indicated with the expression second mill stands 15A, 15, 15B) is arranged, which implement rolling without an internal tool. Such second mill stands 15A, 15, 15B, perforated bodies are thus arranged immediately downstream of the first mill stands 10A, 10B along the rollingaxis 100 with respect to the sense ofadvancement 2. In other words, the second mill stands 15A, 15, 15B are arranged immediately in succession with the first mill stands 10A, 10B. So, as a whole, the rolling mill 1 appears as a single machine, defined in the scope of thesame structure 3, which implements two rolling processes in series: the first on mandrel, the second without an internal tool. In particular, the first mill stands 10A, 10B and the second mill stands 15A, 15, 15B are four-roll mill stands having the features described above. It is worth noting that inFigure 17 , the motors which actuate the drive shafts of the rolling mill stands are generically indicated byreference numeral 40. - Again with reference to
Figure 17 , the rolling mill 1 comprises a first mandrel-holder stand 112, arranged between theinlet section 4A of thehousing 4 and the first plurality of mill stands 10A, 10B, and a second mandrel-holder stand, 113 arranged instead between the first mill stands 10A, 10B of the first section 410 and the second rolling mill stands 15A, 15, 15B of thesecond section 420. The mandrel-holder stands 112, 113 support the mandrel 7 when the perforated body is pulled out from the mandrel itself to be rolled without an internal tool in thesecond section 420. - Figures from 19 to 19A relate to a possible embodiment of a mandrel-holder stand which can be used in the rolling mill 1 according to the invention. Such embodiment is known in itself and will not be described in greater detail.
- It is worth noting that from the operative point of view, the first mandrel rolling section 410 and the
second section 420 for rolling without an internal tool may replace a REELER machine and a SIZER machine, respectively. In other words, the first section 410 can perform the thickness reeling function, while thesecond section 420 can perform the sizing of the perforated body. Therefore, the rolling mill 1 according to the invention may be advantageously used instead of these two machines (REELER-SIZER), at the same time allowing eliminating the heating furnace envisaged in traditional systems between the machines themselves. In particular, according to another advantageous aspect, it is worth noting that the first section 410 allows a reeling of the thickness of the "longitudinal" and not of the "helicoidal" type as in the traditional REELER machines. This possibility translates into a reduction of the number of faults with respect to the case of helicoidal reeling, which can be achieved by means of a traditional type REELER machine. As a result, the rolling mill 1 shown inFigure 17 may be advantageously used in a rolling system comprising, as main station or machine, an oblique type thickness-finishing rolling mill, such as for example an EXPANDER rolling mill, an ASSEL, DIESCHER or PLANETARY rolling mill. A possible use is envisaged also in a system in which a HOT WALKING BEAM type rolling mill or a PLUG MILL rolling mill is provided to define the thickness of the perforated bodies. The rolling mill types described above are well known to a person skilled in the art and for this reason are not described in detail. In general, the rolling mill 1 infigure 17 may be advantageously used instead of the REELER and SIZER machines normally envisaged in the rolling system indicated above. -
Figures 18 and 18A relate to a possible embodiment of the first mill stand 10A,10B and/or of the second mill stands 15A,15,15B of the rolling mill 1. As shown, the rolling mill 1 comprises an aligning and locking system of the mill stands in thehousing 4. In a preferred embodiment, shown in the figures, the mill stands 10A, 10B, 112, 113 accommodated in the first section 410 and those accommodated in thesecond section 420 are provided with at least one pair of floatingpins horizontal plane 300 passing through the rollingaxis 100. The alignment system comprises at least one first pair ofhydraulic cylinders 181 and one second pair ofhydraulic cylinders 182 fixed tostructure 3 at anoutlet section 4B of thehousing 4 and of theinlet section 4A of thehousing 4, respectively. Thecylinders 181 of the first pair act on a corresponding floatingpin 71 of thelast mill stand 15B of thesecond section 420, while thecylinders 181 of the second pair act on a floatingpin 71A of the first mill stand housed in the first section 410, i.e. the mandrel-holder stand 112. Thecylinders 181 of the first pair push the floating pins 71 of the mill stand 15B from thesecond section 420 so that they are inserted in the corresponding female housings defined in the adjacent mill stand 15 pushing at the same time the floating pins already present in such housings. Such action repeats up to the first mandrel-holder stand 112 adjacent to theinlet section 4A of thehousing 4. In particular, thepins 71A of the first mandrel-holder stand 112 are inserted in corresponding housings instructure 3. In this manner, all the mill stands are constrained and axially locked. Thecylinders 182 are fixed to structure 3 at theinlet section 4A and act on the floatingpins 71A of the mandrel-holder stand 112 so as to push them in opposite sense, i.e. towards theoutlet section 4B. In this manner, the floating pins 71, 71A are released from the housings in which they were previously engaged so as to allow the successive removal of one or more mill stands of the rolling mill 1. - According to a preferred embodiment, the mill stands 112, 10A, 10B, 113, 15A, 15, 15B of the rolling mill 1 are provided with a further pair of thrust points 73, 73A arranged on opposite sides of the mill stand, at a substantially
vertical plane 312 passing through the rollingaxis 100. In this configuration, the rolling mill 1 comprises further thrustcylinders 91 fixed tostructure 3 as theoutlet section 4B of thehousing 4. Such further pairs ofcylinders 91 act on thrust points 73, 73A arranged on thevertical plane 312 in manner similar to that described above for the cylinders which act on the floating pins arranged on the horizontal plane. The actions exchanged betweencylinders 91 and the mill stands 112, 10A, 10B, 113, 15A, 15, 15B are of compression only. - The present invention thus further relates to a rolling system comprising at least one rolling mill having the peculiarities described above. As mentioned above, the rolling mill 1 may be used as sizer rolling mill or alternatively for rolling on mandrel and a rolling without an internal tool on perforated bodies, the thickness of which was already defined by means of a thickness-finishing rolling mill. The latter may be of the oblique type, e.g. of the EXPANDER, ASSEL, DIESCHER or PLANETARY type. Alternatively, the finishing rolling mill may be of the HOT WALKING BEAM or also of the PLUG MILL type.
- The rolling mill according to the invention allows fully fulfilling the predetermined tasks and objects. In particular, the structure of the rolling mill appears simpler and with smaller dimensions than the structures currently envisaged in rolling mills with four-roll mill stands. In particular, the structure is simplified by effect of the independent actuation of the drive shafts combined with the use of the orientable drive shafts. At the same time, the installation position envisaged for the eccentric control device also contributes to simplifying the structure, at least in terms of transversal dimensions.
and in that two first of said drive shafts rotate two respective first non-contiguous and reciprocally opposite rolls of the mill stand, and can be inclined angularly between a first reference position and a second reference position, so that they are outside the space comprised between said support plane and said reference plane when they are in the retracted configuration,
and in that two second of said drive shafts rotate two respective second non-contiguous and reciprocally opposite rolls of the mill stand, and wherein, when the second drive shafts are in the retracted configuration, they are outside the space comprised between said support plane and said reference plane.
Claims (15)
- A rolling mill (1) for tubular bodies comprising:- a structure (3) defining a housing (4) for at least one mill stand (10) with four rolls (11, 12, 13, 14), wherein each roll is operatively connectable to a drive shaft (31, 32, 33, 34), said housing (4) being vertically delimited between a horizontal support plane (101) and a reference plane (102) parallel to said support plane (101);- four drive shafts (31, 32, 33, 34), each of which can rotate a respective roll (11, 12, 13, 14) of said mill stand (10), wherein each drive shaft (31, 32, 33, 34) can axially extend and retract in reversible manner, passing from a retracted configuration, in which it is operatively disconnected from the respective roll (11, 12, 13, 14), to an extended configuration, in which it is operatively connected to the respective roll (11, 12, 13, 14) and vice versa,characterized in that each drive shaft (31,32,33,34) is actuated independently from the other drive shafts which can rotate the other rolls of the same mill stand (10) by means of a respective drive motor (41, 42, 43, 44), installed in a different position from that of the motors which actuate the other drive shafts,
and in that two first (31, 33) of said drive shafts can rotate two respective non-contiguous and reciprocally opposite first rolls (11, 13) of the mill stand (10), and are angularly inclinable between a first reference position and a second reference position, such that they are outside the space comprised between the support plane (101) and said reference plane (102) when they are in the retracted configuration,
and in that two second (32, 34) of said drive shafts can rotate two respective non-contiguous and reciprocally opposite second rolls (12, 14) of the mill stand (10) and wherein, when the second drive shafts (32, 34) are in the retracted configuration, they are outside the space comprised between said support plane (101) and said reference plane (102). - A rolling mill (1) according to claim 1, wherein the two second drive shafts (31, 32) have a telescopic configuration comprising a first portion (31A, 32A) connected to the related actuating motor (42, 44) and a second portion (31B, 32B) which slides telescopically with respect to the first portion (32A, 34A).
- A rolling mill (1) according to claim 1 or 2, wherein the two inclinable drive shafts (31, 33) also have a telescopic configuration, wherein a respective first portion (31A, 33A) is connected to the respective actuating motor (41) and a respective second portion (31B, 33B) can slide telescopically with respect to the first portion (31A, 33A), wherein said respective first portion (31A, 33A) is connected to the respective actuating motor (41, 43) by means of a Cardan joint (48) which defines a rotation axis about which said inclinable drive shafts (31, 33) are inclined between the first reference position and the second reference position.
- A rolling mill (1) according to claim 3, wherein the two telescopic drive shafts (32, 34) comprise thrust means (81) to vary the position of said second portion (32B, 34B) with respect to said first portion (32A, 34A) so as to vary the configuration of the two drive shafts (32, 34).
- A rolling mill (1) according to claim 3 or 4, comprising an actuating device for rotating and guiding the two inclinable drive shafts (31, 33) between the first reference position and the second reference position.
- A rolling mill (1) according to any one of the claims from 1 to 5, wherein the rotation axis of the two first non-contiguous rolls (11, 13) of the mill stand (10) is inclined by a 22,5° angle with respect to said support plane (101).
- A rolling mill (1) according to claim 6, wherein the rotation axis of the two second non-contiguous rolls (14) of the mill stand (10) is inclined by a 67,5° angle with respect to said support plane (101).
- A rolling mill (1) according to claim 7, wherein said actuating device comprises a lever body (8) hinged to said structure (3) to rotate about an axis (7), said body (8) comprising a first part (8A) connected to an actuator (82), and a second part (8B) provided with two tines (88B), said second part (8B) developing from a side opposite to that of the first part (8A) with respect to the axis (7), said second part (31B) of said drive shaft (31) comprising pairs of diametrically opposite wheels (36) sliding within two opposite guides (85) fixed to said structure (3), said guides (85) developing on opposite vertical planes (185) between which the drive shaft (31) is operatively arranged, wherein said tines (88B), after the activation of said actuator (82), act on said wheels (36) moving them along said guides (85) and causing the rotation of said drive shaft (31).
- A rolling mill (1) according to any one of claims from 1 to 8, wherein said rolling mill (1) comprises:- an adjustment system for adjusting the radial position of a respective roll (12, 14) with respect to said rolling axis (100), and- at least one control device (60) which is connected to said adjustment system to control the activation thereof,wherein said control device (60) is connected to said adjustment system when the drive shaft (32, 34) of said respective roll (12, 14) takes said extended configuration.
- A rolling mill (1) according to any one of claims from 1 to 9, wherein said rolling mill (1) comprises a retaining device (80) to lock said mill stand (10) in said housing (4) in a predetermined position, wherein said retaining device (80) is installed in a position under said support plane (101), said retaining device comprising a retainer (880) configured to take at least one locking position in which said mill stand (1) is locked in said predetermined position, and a releasing position in which said mill stand (1) may translate in said housing (4).
- A rolling mill (1) according to any one of claims from 1 to 10, wherein said mill stand (10) comprises a monoblock body which sustains said rolls (11, 12, 13, 14) within an operative cavity, said rolls (11, 12, 13, 14) being removable from said monoblock body through said operative cavity.
- A rolling mill (1) according to any one of claims from 1 to 11, wherein said housing (4) comprises:- a first section (410) for milling on mandrel, in which a first plurality of rolling mill stands (10A, 10B) is arranged in sequence along said rolling axis (100) from an inlet section (4A) of said housing (4);- a second section (420) for milling without an internal tool, downstream of said first section (41), with respect to the advancement direction of said tubular bodies, said second section (420) comprising a second plurality of rolling mill stands (15A, 15, 15B) arranged in sequence along said rolling mill (100),wherein said rolling mill (1) comprises a first mandrel-holder stand (112) and a second mandrel-holder stand (113) arranged in said first section (410) upstream and downstream of said first plurality of rolling mill stands (10A, 10B), respectively, with respect to said advancement direction of said tubular bodies.
- A rolling mill (1) according to claim 12, comprising a system for aligning and locking said rolling mill stands in said housing (4).
- A rolling system characterized in that it comprises a rolling mill according to any one of claims from 1 to 13.
- A rolling system according to claim 14, wherein said system comprises a thickness-finishing rolling mill upstream of said rolling mill according to any one of claims from 1 to 13, wherein said thickness-finishing rolling mill is of the oblique or of the HOT WALKING BEAM or HOT PILGER MILL type.
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
IT102016000103504A IT201600103504A1 (en) | 2016-10-14 | 2016-10-14 | MULTI-CASE SHEET FOR ASTIFORM BODIES INCLUDING FOUR ROLLER CAGES |
PCT/IB2017/056347 WO2018069876A1 (en) | 2016-10-14 | 2017-10-13 | Multi-stand rolling mill for rod-shaped bodies comprising mill stands with four motorized rolls |
Publications (2)
Publication Number | Publication Date |
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EP3525946A1 EP3525946A1 (en) | 2019-08-21 |
EP3525946B1 true EP3525946B1 (en) | 2020-11-25 |
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Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
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EP17797186.8A Active EP3525946B1 (en) | 2016-10-14 | 2017-10-13 | Multi-stand rolling mill for rod-shaped bodies comprising mill stands with four motorized rolls |
Country Status (3)
Country | Link |
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EP (1) | EP3525946B1 (en) |
IT (1) | IT201600103504A1 (en) |
WO (1) | WO2018069876A1 (en) |
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Publication number | Priority date | Publication date | Assignee | Title |
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IT201900014925A1 (en) * | 2019-08-22 | 2021-02-22 | Danieli Off Mecc | GUIDING DEVICE FOR DRIVING A SPINDLE THRUST BAR OR FOR DRIVING A SPINDLE IN A TUBULAR BODY LAMINATION PROCESS |
Family Cites Families (4)
Publication number | Priority date | Publication date | Assignee | Title |
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DE3236892A1 (en) * | 1982-10-01 | 1984-04-05 | Mannesmann AG, 4000 Düsseldorf | ROLLING MILL FOR THE PRODUCTION OF THIN-WALLED SEAMLESS TUBES |
IT1392497B1 (en) * | 2008-12-30 | 2012-03-09 | Danieli Off Mecc | MULTI-CHAMBER MILL, OF THE LONGITUDINAL EXTENSION TYPE, FOR ASTIFORM BODIES, INCLUDING FOUR ROLLER CAGES, AND PROCEDURE FOR CAGE CHANGE |
IT1399629B1 (en) * | 2010-04-20 | 2013-04-26 | Sms Innse Spa | LAMINATE FOR EXTENDED ARTICLES. |
JP5459457B1 (en) * | 2012-07-24 | 2014-04-02 | 新日鐵住金株式会社 | Manufacturing method and apparatus for seamless metal pipe |
-
2016
- 2016-10-14 IT IT102016000103504A patent/IT201600103504A1/en unknown
-
2017
- 2017-10-13 WO PCT/IB2017/056347 patent/WO2018069876A1/en unknown
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IT201600103504A1 (en) | 2018-04-14 |
WO2018069876A1 (en) | 2018-04-19 |
EP3525946A1 (en) | 2019-08-21 |
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