EP3124130A1 - Meule de cylindre destinee a l'evitement cible de quarts d'onde - Google Patents

Meule de cylindre destinee a l'evitement cible de quarts d'onde Download PDF

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Publication number
EP3124130A1
EP3124130A1 EP15178612.6A EP15178612A EP3124130A1 EP 3124130 A1 EP3124130 A1 EP 3124130A1 EP 15178612 A EP15178612 A EP 15178612A EP 3124130 A1 EP3124130 A1 EP 3124130A1
Authority
EP
European Patent Office
Prior art keywords
rolls
function
rollers
work rolls
functions
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.)
Withdrawn
Application number
EP15178612.6A
Other languages
German (de)
English (en)
Inventor
Alois Seilinger
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Primetals Technologies Austria GmbH
Original Assignee
Primetals Technologies Austria GmbH
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Primetals Technologies Austria GmbH filed Critical Primetals Technologies Austria GmbH
Priority to EP15178612.6A priority Critical patent/EP3124130A1/fr
Priority to US15/744,158 priority patent/US10589328B2/en
Priority to PCT/EP2016/060724 priority patent/WO2017016695A1/fr
Priority to EP16721836.1A priority patent/EP3328565B1/fr
Priority to CN201680043955.2A priority patent/CN107921496B/zh
Priority to JP2018504231A priority patent/JP6585278B2/ja
Publication of EP3124130A1 publication Critical patent/EP3124130A1/fr
Withdrawn legal-status Critical Current

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Classifications

    • 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
    • B21B31/18—Adjusting or positioning rolls by moving rolls axially
    • 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
    • B21B13/14—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls
    • B21B13/142—Metal-rolling stands, i.e. an assembly composed of a stand frame, rolls, and accessories having counter-pressure devices acting on rolls to inhibit deflection of same under load; Back-up rolls by axially shifting the rolls, e.g. rolls with tapered ends or with a curved contour for continuously-variable crown CVC
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/18—Roll crown; roll profile
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2267/00—Roll parameters
    • B21B2267/18—Roll crown; roll profile
    • B21B2267/20—Ground camber or profile
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
    • B21B—ROLLING OF METAL
    • B21B2269/00—Roll bending or shifting
    • B21B2269/12—Axial shifting the rolls

Definitions

  • Such a rolling mill is for example from the WO 03/022 470 A1 known.
  • the contour of one of the two axially mutually displaceable rollers is formed by a first basic function, the contour of the other of the two axially mutually displaceable rollers by a second basic function.
  • the basis functions are functions of the place seen in the direction of the respective axis of rotation. They are further determined such that they complement each other in the unloaded state of the two axially mutually displaceable rollers in a certain relative axial position and complementary at an outgoing from this axial position displacement Shifting direction form a convex or a concave roll gap profile.
  • contour-influencing measures are the use of roll bending devices, by means of which the rolling force application to the rolling stock and the thickness distribution over the width of the rolling stock can be selectively influenced.
  • the superimposition of the basic function with the additional function serves the purpose of reducing the maximum pressure acting on the work roll and the backup roll or on the intermediate roll and the backup roll, thereby increasing roll life and avoiding roll breaks as far as possible.
  • the additional function is a quadratic function.
  • the object of the present invention is to provide a rolling mill, in which by axial displacement of rollers, the shape of the roll gap, ie the thickness profile of the roll gap over the bale length, is varied such that a highest quality standards fulfilling, flat and wave-free rolling is achieved.
  • the equivalent crown of the two axially against each other sliding rollers is provided with an offset.
  • the offset is positive, only negative in exceptional cases.
  • the equivalent crowning is the crowning conventionally (that is, symmetrically) ground Rollers which give the same nip profile in the unloaded or load-free state.
  • the specific relative axial position of the two axially mutually displaceable rollers in which the basic functions of the two axially mutually displaceable rollers complement each other, lies within the actually achievable displacement range of the two axially mutually displaceable rollers.
  • this axial position may be outside the actually reachable displacement range.
  • the two basic functions always form a convex or always a concave roll gap profile independently of the actual displacement. In this case, only in the mathematical sense, a sign reversal is possible.
  • the basis functions, relative to the center of the bale are antisymmetric to one another.
  • This embodiment facilitates both the mathematical description of the contours of the two axially mutually displaceable rollers and the production engineering production of the contours of the two axially mutually displaceable rollers.
  • the additional functions are preferably symmetrical, monotonous functions on both sides.
  • This configuration facilitates - in particular in combination with the antisymmetry of the basic functions to each other - both the mathematical description of the contours of the two axially mutually displaceable rollers and the production engineering production of the contours of the two axially mutually displaceable rollers.
  • the additional functions are symmetrical to one another.
  • the two rollers which can be displaced axially relative to one another can be ground in the same manner and only one of the two rollers must be installed in the rolling stand rotated by 180 ° relative to the other.
  • the first basis function is a polynomial function.
  • a typical example of a suitable polynomial function is a function that is a function of third degree, seen from the center of the bale and in the direction of the respective axis of rotation.
  • Another example is a function that has a 5th order share in addition to a 3rd order share.
  • the first basis function is a trigonometric function superimposed on a linear function.
  • the linear portion is preferably determined so as to (completely or at least substantially) achieve a minimization of the diameter differences of the bale contours along the bale contours.
  • the trigonometric function may in particular be a sine function.
  • the superposition of a sine function with a linear function to compensate for differences in diameter of the bale contours is known in the art as a tilted sine function.
  • the sum of the additional functions is a polynomial function.
  • a typical example of a suitable polynomial function is a function that is a 2nd order function, as seen from the center of the bale and in the direction of the respective axis of rotation. It is particularly preferred that the polynomial function also has a proportion of the fourth degree in addition to a second degree component.
  • the above statements apply not only to the sum of the additional functions, but also for each of the two additional functions considered individually.
  • the sum of the additional functions is a trigonometric function.
  • the trigonometric function may in particular be a cosine function.
  • the roll stand has no further rolls other than the work rolls.
  • the work rolls are supported directly or via intermediate rolls on support rolls.
  • the contours of the back-up rolls can be provided with an inverse additional contour, so that the back-up rolls complement each other in an uncompressed, unloaded state with the work rolls.
  • the contours of the support rollers differ from those of the work rolls in particular by a concave difference.
  • the contours of the intermediate rolls may be different from those of the work rolls and / or back-up rolls by such a concave difference.
  • maximum pressures acting between adjoining rollers can be minimized.
  • the rolling stock 2 can in particular Metal consist, for example, aluminum or steel. It can be a band or a heavy plate.
  • FIG. 1 and 2 has the rolling stand 1 rolling stand 3.
  • a first and a second work roll 4, 5 are mounted in the rolling mill stands 3 in the rolling mill stands 3 .
  • the work rolls 4, 5 are - as is common practice - stored in the rolling mill stands 3 such that the work rolls 4, 5 about a respective axis of rotation 6, 7 are rotatable.
  • the rotation is effected by means of a common drive assigned to the work rolls 4, 5 or by drives assigned to each of the work rolls 4, 5.
  • the drive is or the drives are not shown in the FIG.
  • the first work roll 4 is as shown in the FIG. 1 and 2 the upper work roll.
  • the second work roll 5 is the lower work roll.
  • the reverse assignment is also possible.
  • the roll stand 1 except the work rolls 4, 5 has no further rolls (Duogerüst). In general, however, support the work rolls 4, 5, as shown in the FIG. 1 and 2 on support rollers 8, 9 from. It is according to the illustration in FIG. 1 possible that the roll stand 1 except the work rolls 4, 5 and the support rollers 8, 9 has no further rolls (for example, in a Quartogerüst). In this case, the work rolls 4, 5 are supported directly on the support rollers 8, 9. Alternatively, it is - for example, in a Sextogerüst - as shown in FIG FIG. 2 possible that the roll stand 1 additionally intermediate rolls 10, 11 has. In this case, the work rolls 4, 5 are supported on the support rolls 8, 9 via the intermediate rolls 10, 11. The other rollers - that is, the support rollers 8, 9 and optionally also the intermediate rollers 10, 11 - are mounted in the rolling stand uprights 3, so that they are rotatable about a respective axis of rotation.
  • Two of the rollers 4, 5, 8, 9, 10, 11 are mounted in the rolling stand uprights 3 such that they are axially displaceable against each other are.
  • the two axially mutually displaceable rollers are the work rolls 4, 5.
  • the displacement thus takes place in the direction of the axis of rotation 6, 7.
  • the displaceability is in FIG. 1 indicated by corresponding double arrows at the work rolls 4, 5.
  • the two axially displaceable rollers are generally the intermediate rollers 10, 11.
  • the displaceability is in FIG. 2 indicated by corresponding double arrows in the intermediate rolls 10, 11.
  • the work rolls 4, 5 have in this case, as a rule, a relatively small diameter and are cylindrical or (symmetrically) slightly spherical. In individual cases, however, alternatively or in addition to the intermediate rolls 10, 11, in the case of a sexto scaffolding the work rolls 4, 5 can also be axially displaceable relative to one another. In this case, the work rolls 4, 5 - optionally in addition to the intermediate rolls 10, 11 - corresponding contours.
  • the two axially mutually displaceable rollers 4, 5 and 10, 11 - ie either the two work rolls 4, 5 or the two intermediate rollers 10, 11 - have according to FIG. 3 an effective bale length L on.
  • the corresponding rollers 4, 5 and 10, 11 furthermore have, as from in FIG. 3 above or below the respective roller 4, 5 and 10, 11 given equations for the radius R1, R2 of the respective roller 4, 5 and 10, 11 can be seen, each having a curved contour, which extends over the entire effective bale length L extends.
  • the radii R1, R2 as a function of the location x along the axes of rotation 6, 7 correspond to the contours of the rollers 4, 5 and 10, 11th
  • the two axially mutually displaceable rollers 4, 5 and 10, 11 have according to FIG. 3 first on a base radius R0.
  • the base radius R0 is constant, ie no function of the location x along the axis of rotation 6 of the first work roll 4 or the location x along the axis of rotation 7 of the second work roll 5 or the axes of rotation of the intermediate rolls 10, 11.
  • This base radius R0 is in the case of first work roll 4 (or the first work roll 4 adjacent intermediate roll 10) superimposed on a first basis function B1, in the case of the second work roll 5 (or the second work roll 5 adjacent intermediate roll 11) has a second basic function B2.
  • the basic functions B1, B2 are according to FIG. 3 Functions of the location x in the direction of the respective axis of rotation 6, 7.
  • the basic functions B1, B2 are preferably, with respect to the center of the bale, antisymmetric to one another. So these are odd functions in the mathematical sense.
  • the relation B1 (x) -B2 (-x) holds.
  • the basic functions B1, B2 are determined so that they complement each other in the unloaded state of the respective rollers 4, 5 and 10, 11 in a certain relative axial position of the respective rollers 4, 5 and 10, 11 complementary and at one of this axial position outgoing shift depending on the direction of displacement form a convex or a concave roll gap profile.
  • the meaning of these quantities is mentioned in the beginning WO 03/022 470 A1 explained.
  • the reference length L Ref may be identical to the ball length L. Alternatively, it can be a different value.
  • the basic functions B1, B2 are determined so that they complement each other in the unloaded state of the corresponding rollers 4, 5 and 10, 11 in a certain relative axial position of the corresponding rollers 4, 5 and 10, 11 complementary. This axial position is reached when the first work roll 4 (or the first work roll 4 adjacent intermediate roll 10) is displaced in the positive direction by the contour displacement c and the second work roll 5 (or the second work roll 5 adjacent intermediate roll 11) in negative Direction is shifted by the contour shift c.
  • the basic functions B1, B2 form a convex roll gap profile.
  • displacement of the first work roll 4 (or the intermediate work roll 10 adjacent to the first work roll 4) in the negative direction and, corresponding thereto, the second work roll 5 (or the intermediate work roll 11 adjacent to the second work roll 5) is positive Direction, the basic functions B1, B2 form a concave roll gap profile.
  • the basic functions B1, B2 relative to the center of the bale, antisymmetric to each other.
  • the first basic function B1 is additionally superimposed on an additional function Z1.
  • the second basic function B2 is additionally superimposed with an additional function Z2.
  • the additional functions Z1, Z2 are according to FIG. 3 - Analogous to the basic functions B1, B2 - functions of the place x in the direction of the respective axis of rotation 6, 7th
  • ⁇ and ⁇ are weighting factors, which typically have a value between 0 and 2.
  • the limits 0 and 2 can be assumed with. In individual cases even larger or even smaller values can be assumed.
  • the weighting factors ⁇ , ⁇ can be determined independently of each other. Preferably, both weighting factors ⁇ , ⁇ have the value 1. This has the advantage that the additional functions Z1, Z2 are symmetrical to one another.
  • C and D are proportional factors. As a rule, the proportion factor C has a value above zero. The proportion factor D may be 0, greater than zero, or less than zero as needed.
  • the first basis function B1 is a trigonometric function superimposed on a linear function.
  • the trigonometric function may in particular be a sine function.
  • the sum of the additional functions Z1, Z2, however, is a polynomial function.
  • the polynomial function as seen from the center of the bale and in the direction of the respective axis of rotation 6, 7, has at least a second degree component.
  • the proportion factor D has a value other than 0 - the polynomial function also has a fourth degree component.
  • d0 is a value which depends on the displacement s, but not on the location x in the direction of the axis of rotation 6, 7.
  • the resulting course of the roll gap g has on the one hand a convex or concave portion, which is dependent on the displacement s, namely the proportion 2 A ⁇ cos 2 ⁇ L Ref x ⁇ sin 2 ⁇ L Ref s - c
  • the resulting course of the roll gap g has a further convex or concave portion, which is not dependent on the displacement s, namely, in the case that the proportion factor D has the value 0, the proportion 2 C x 2
  • FIG. 4 shows a similar embodiment as FIG. 3 ,
  • the first basis function B1 is a polynomial function.
  • the sum of the additional functions Z1, Z2 a trigonometric function.
  • the trigonometric function according to FIG. 4 be a cosine function.
  • A is a well-chosen factor.
  • the additional functions Z1, Z2 can be selected independently of the basis functions B1, B2.
  • the additional functions Z1, Z2 are therefore not necessarily polynomial functions. It could also be trigonometric functions, in particular trigonometric functions according to FIG. 4 .
  • the additional functions Z1, Z2 are not necessarily trigonometric functions. It could also be polynomial functions, in particular polynomial functions according to FIG. 3 ,
  • FIG. 5 shows purely exemplary of the embodiment according to FIG. 3 the deviation of the resulting roll gap g from an average value.
  • FIG. 5 it can be seen that a very uniform profile can be achieved to a considerable extent as a result of the superimposition of the basic functions B1, B2 with the additional functions Z1, Z2.
  • the maxima 12 of the deviation can be further influenced both with regard to their position in the direction of the axis of rotation 6, 7 and with respect to their height.
  • the present invention has many advantages.
  • the adjustment range achievable by shifting the work rolls 4, 5 should be between-400 ⁇ m and -100 ⁇ m in crowning, this can be achieved by setting the adjustment range between +300 ⁇ m and +600 ⁇ m using only the basis functions B1, B2 would lie, by the additional functions Z1, Z2, however, in addition a parabolic crowning of -700 microns is superimposed.
  • the superimposition of the basic functions B1, B2 and the additional functions Z1, Z2 can be used to selectively suppress edge waves as well as center waves as well as quarter waves.
  • the suppression is particularly effective when not only the proportion factor C but also the proportion factor D has a value different from zero.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Reduction Rolling/Reduction Stand/Operation Of Reduction Machine (AREA)
  • Control Of Metal Rolling (AREA)
  • Casting Or Compression Moulding Of Plastics Or The Like (AREA)
  • Treatment Of Fiber Materials (AREA)
EP15178612.6A 2015-07-28 2015-07-28 Meule de cylindre destinee a l'evitement cible de quarts d'onde Withdrawn EP3124130A1 (fr)

Priority Applications (6)

Application Number Priority Date Filing Date Title
EP15178612.6A EP3124130A1 (fr) 2015-07-28 2015-07-28 Meule de cylindre destinee a l'evitement cible de quarts d'onde
US15/744,158 US10589328B2 (en) 2015-07-28 2016-05-12 Roll crown for the specific avoidance of quarter waves
PCT/EP2016/060724 WO2017016695A1 (fr) 2015-07-28 2016-05-12 Couronne de cylindre permettant d'éviter sélectivement les quarts d'ondes
EP16721836.1A EP3328565B1 (fr) 2015-07-28 2016-05-12 Meule de cylindre destinee a l'evitement cible de quarts d'onde
CN201680043955.2A CN107921496B (zh) 2015-07-28 2016-05-12 具有受控的四分之一波预防的辊式研磨
JP2018504231A JP6585278B2 (ja) 2015-07-28 2016-05-12 制御された四分の一波防止によるロール研磨

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15178612.6A EP3124130A1 (fr) 2015-07-28 2015-07-28 Meule de cylindre destinee a l'evitement cible de quarts d'onde

Publications (1)

Publication Number Publication Date
EP3124130A1 true EP3124130A1 (fr) 2017-02-01

Family

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Family Applications (2)

Application Number Title Priority Date Filing Date
EP15178612.6A Withdrawn EP3124130A1 (fr) 2015-07-28 2015-07-28 Meule de cylindre destinee a l'evitement cible de quarts d'onde
EP16721836.1A Active EP3328565B1 (fr) 2015-07-28 2016-05-12 Meule de cylindre destinee a l'evitement cible de quarts d'onde

Family Applications After (1)

Application Number Title Priority Date Filing Date
EP16721836.1A Active EP3328565B1 (fr) 2015-07-28 2016-05-12 Meule de cylindre destinee a l'evitement cible de quarts d'onde

Country Status (5)

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US (1) US10589328B2 (fr)
EP (2) EP3124130A1 (fr)
JP (1) JP6585278B2 (fr)
CN (1) CN107921496B (fr)
WO (1) WO2017016695A1 (fr)

Cited By (1)

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Publication number Priority date Publication date Assignee Title
CN112588838A (zh) * 2020-11-10 2021-04-02 北京科技大学 适用于短行程窜辊非对称自补偿轧制工作辊及其实现方法

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CN117483424B (zh) * 2023-11-17 2024-06-04 燕山大学 一种改善镁合金板边裂的可轴向移动异形轧辊及轧制方法

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WO2007144161A1 (fr) 2006-06-14 2007-12-21 Siemens Vai Metals Technologies Gmbh & Co Cage de laminoir pour la fabrication de bande laminée ou de tôle
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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112588838A (zh) * 2020-11-10 2021-04-02 北京科技大学 适用于短行程窜辊非对称自补偿轧制工作辊及其实现方法

Also Published As

Publication number Publication date
US10589328B2 (en) 2020-03-17
US20180200769A1 (en) 2018-07-19
WO2017016695A1 (fr) 2017-02-02
JP6585278B2 (ja) 2019-10-02
CN107921496B (zh) 2019-11-01
EP3328565B1 (fr) 2019-12-11
CN107921496A (zh) 2018-04-17
EP3328565A1 (fr) 2018-06-06
JP2018525228A (ja) 2018-09-06

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