WO1993000180A1

WO1993000180A1 - Shape control device of multi-stage rolling mill and method of controlling same

Info

Publication number: WO1993000180A1
Application number: PCT/JP1992/000782
Authority: WO
Inventors: Kenichi Uesugi; Tatsuhiko Takeshima
Original assignee: Kabushiki Kaisha Kobeseikosho
Priority date: 1991-06-20
Filing date: 1992-06-18
Publication date: 1993-01-07
Also published as: DE4292012T1

Abstract

An object of the present invention is to lower the stress peaks given by shoulders of bearing rolls of backup rolls. The shape control device according to the present invention is provided to a multi-stage rolling mill which is provided in a housing (21) thereof with a pair of work rolls (11), intermediate rolls (12, 13) for supporting the work rolls and a backup roll (14) for supporting the intermediate roll (13). The backup roll (14) is constituted by a plurality of bearings (18) rotatably fitted over roll shafts (17) in the axial direction at predetermined intervals. The shape control device according to the present invention has a support roll eccentric device incorporated in at least one of the backup rolls (14). Said support roll eccentric device is constituted by: eccentric rings (23) fitted over and fixed to the roll shafts (17) at opposite sides of the bearings (18) in the axial direction of the bearings (18) and having a center eccentric to the axes of the roll shafts (17); saddles (19) rotatably fitted over the eccentric rings (23) and detachably supported by the housing (21); and a rotating means (29) for rotating the roll shafts (17).

Description

Specification

TECHNICAL FIELD The present invention relates to a shape control device for a multi-high rolling mill and a control method therefor.

The present invention relates to a shape control device in a multi-high rolling mill and a control method thereof.

[Background Art]

In a multi-stage cluster rolling mill used for rolling thin sheets, etc., a small-diameter work roll sandwiching a material to be rolled from above and below is supported by a back-up roll through an intermediate roll, and a plurality of work rolls are axially mounted on a roll shaft. Rollers are fitted to form a back-up profile.

Since the work roll has a small diameter, it tends to bend in the axial direction during the rolling operation, and as a result, there is a problem that the shape of the rolled material is impaired, such as a wave or a warp in the width direction of the rolled material.

Therefore, in order to improve this shape, conventionally, as shown in FIG. 18, a roller fitting portion 3 having an independent eccentric amount is provided in a portion corresponding to each roller 2 of the backup roll 1 in a predetermined eccentric direction. The roller 2 is eccentrically provided on the shaft 4, and each roller 2 is rotatably fitted to each roller fitting portion 3, and the roll shaft 4 is rotated around the axis so that the intermediate roll 5 is rotated. The shape of the crown of the work roll, that is, the radius of the work roll, is changed through the method (Japanese Patent Publication No. 59-48683).

Further, as shown in FIG. 19, there is a roller shaft 4 in which each roller fitting portion 3 is angled (the same publication).

In the former eccentric bag-up roll 1, a stress peak occurs at the shoulder a of each roller 2, the surface pressure of the intermediate roll 5 in contact with the peak increases locally, and the surface separation of the intermediate roll 5 decreases. Easy to occur.

Also, the shoulder mark of the backup roll 1 is likely to occur on the intermediate roll 5, and when this is transferred to the work roll, the material (product) becomes glossy. Spots develop.

Further, at the time of rolling, the material to be rolled may be stretched only at the roller 2 portion of the backup roll 1, particularly at the portion corresponding to the summer portion a of each roller 2, and the intermediate portion between the rollers 2 may not be stretched. As a result, a wave is generated in the material to be rolled in the radial direction of the sheet.

In the latter case, the former problem can be improved to some extent. However, although the radius curve of the intermediate roll 5 is not uniform due to the rolling conditions, the angle of the roller fitting portion 3 is a constant value, so that a peak occurs at the shoulder portion of the roller 2 as in the former case. There is.

DISCLOSURE OF THE INVENTION

The present invention has been made in view of the above-described conventional problems, and has as its object to reduce stress peaks caused by shoulders of respective rollers.

The shape control device of the present invention is provided in a multi-high rolling mill having a pair of black crawls, an intermediate roll supporting the work roll, and a backup roll supporting the intermediate roll in a housing. The back-up roll is composed of a plurality of bearings which are externally fitted to the roll shaft at a predetermined distance from the roll shaft in the axial direction.

The shape control device of the present invention has a support roll eccentric device.

The support roll eccentric device is incorporated in at least one of the plurality of backup rolls.

The support roll eccentric device is an eccentric ring that is externally fitted and fixed to the roll shaft on both sides in the axial direction of each of the bearings, and has a center that is eccentric with respect to the axis of the roll shaft. A saddle is rotatably fitted to the ring and supported by the housing so as to be in contact with and separate from the housing. The saddle is configured to rotate the roll shaft. According to the present invention, the roll shaft is rotated by the rotation means to the axial center. To adjust the shape.

That is, when the roll shaft is turned, each eccentric ring turns integrally therewith. When rolling starts, the reaction force from the material to be rolled is transmitted to each bearing roller of the back-up profile via the work roll and intermediate roll, and each saddle is pressed against the housing, causing the roll axis to bend. .

Therefore, since each bearing roller is pressed through the bending of the roll shaft, the stress peak due to the shoulder of each bearing roller can be suppressed to a small value.

Further, by rotating the roll shaft by the rotating means, the radius curve of the roll shaft can be adjusted arbitrarily.

Further, in the present invention, it is expedient to employ the following configuration to arbitrarily obtain a deflection curve of the roll shaft.

That is, an arcuate shoe portion is formed on the outer peripheral surface of the saddle of the support roll eccentric device, and an arcuate bearing surface for supporting a part of the shoe is formed on the housing. In the free state where the rolling load does not act on the backup roll, the one roll described above such that the gap between the part of the shoe and the bearing surface sequentially increases or decreases from both ends to the center of the roll shaft. Set the amount of eccentricity of a plurality of eccentric rings provided on the shaft.

In order to set the amount of eccentricity of the eccentric ring, a plurality of eccentric rings provided on the one roll shaft are formed in the same shape, and the mounting angle of the eccentric ring to the roll shaft is sequentially shifted. Good.

The setting of the gap between the part of the shoe and the bearing surface is performed by rotating the roll shaft by a rotating means.

If the material to be rolled is convex at the center, the gap between the part of the shoe and the bearing surface decreases gradually from both ends of the roll shaft to the center. Set to The setting of the gap amount is performed by rotating the roll shaft in one direction by a rotating means.

When the shape of the material to be rolled is concave at the center, the gap between the part of the shoe and the bearing surface is set to increase gradually from both ends of the roll shaft to the center. The setting of the gap size is performed by rotating the roll shaft in a direction opposite to the above by a rotating means.

As described above, by operating the support roll eccentric device, the shape of the material to be rolled whose central portion has the uneven shape can be corrected to a flat shape. -By providing a needle bearing between the saddle and the eccentric ring, rotation of the roll shaft becomes smooth.

It is preferable that retainers are fixed to both sides of the eccentric ring or the saddle in the axial direction to prevent the eccentric ring and the saddle from moving in the axial direction.

The surface moving means can be composed of a gear fixed to one end of the roll shaft and a motor for driving the gear, but is not limited thereto.

When the multi-high rolling mill is a 20-high rolling mill, it is expedient to incorporate the support roll eccentric device into at least two back-up rolls at the center of at least the four upper backup rolls.

In this case, it is preferable to incorporate the support roll eccentric device into at least the center two of the four back-up rolls on the lower side.

When the multi-high rolling mill is a 12-high rolling mill, it is preferable to incorporate the supporting roll eccentric device into at least two backers and nap rolls on both sides of at least three lower backup π-rolls.

In the shape control device of the present invention, in addition to the support roll eccentric device, In addition, a crown control device can be incorporated.

The crown Control device, with one less in embedded les of the backup roll the support roll eccentric device is not incorporated set <S> ₀

The crown control device includes: a saddle that supports the roll shafts on both sides in the axial direction of each of the bearing rolls; and an extruder that individually extrudes the saddles in the radial direction of the roll shaft. When the multi-high rolling mill is a 20-high rolling mill, the crown control device is incorporated into two backup rolls on both sides of the four backup rolls on the upper side, and the above-mentioned support is provided on two central backup σ-rolls. It is expedient to incorporate a port eccentric device and to install the support port eccentric device in the center two back-up ports of the four lower backup rolls.

When the multi-high rolling mill is a 1-high rolling mill, the crown control device is incorporated into two backup rolls on both sides of the three backup rolls on the upper side, and two on both sides of the three backup rolls on the lower side The backup roll eccentricity device is preferably incorporated into the backup roll.

In the present invention, the bearing rolls of the adjacent back-up rolls are arranged so as to be shifted from each other in the axial direction, thereby preventing the occurrence of bearing marks and the uneven wear of the bearing rolls.

Further, in the present invention, when the support roll eccentric device and the crown control device are used in combination, the crown control device is used to take charge of shape control of a portion that cannot be controlled by the support roll eccentric device. Is good. [Brief description of drawings]

FIG. 1 (A) is a cross-sectional view of a pack-up roll, and (B) is a cross-sectional view of a saddle portion thereof.

FIG. 2 is a schematic view of a 20-high cluster rolling mill.

FIG. 3 is a front view of the support roll eccentric device.

FIG. 4 is a view taken in the direction of arrows C—C in FIG.

FIG. 5 is an explanatory diagram when the convex crown is adjusted. .

FIG. 6 is an explanatory diagram of a convex crown state.

FIG. 7 is an explanatory view when the concave crown is adjusted.

FIG. 8 is an explanatory diagram of a concave crown state.

FIG. 9 is a roll layout diagram of a 12-high rolling mill.

FIG. 10 is a cross-sectional view of a crown control device in a 12-high rolling mill.

FIG. 11 is a longitudinal sectional view of the crown control device.

FIG. 12 is a sectional view taken along line AA of FIG.

FIG. 13 is an explanatory diagram showing plate shape control characteristics.

FIG. 14 is a layout view when a support port eccentric device and a crown control device are incorporated in a 20-high rolling mill.

FIG. 15 is an explanatory diagram of the riding effect of the supporting roll eccentric device and the roll bending device.

FIG. 16 is an explanatory diagram illustrating the operation of the roll bending device when the supporting roll eccentric device is not provided.

FIG. 17 is an arrangement diagram when the support roll eccentric device and the crown control device are incorporated in a 12-high rolling mill.

FIG. 18 is a partially cutaway front view showing a conventional backup roll.

FIG. 19 is a front view showing a conventional backup roll. BEST MODE FOR CARRYING OUT THE INVENTION

Hereinafter, an embodiment of the present invention will be described in detail with reference to the drawings.

FIG. 2 shows a 20-high cluster rolling mill.

In FIG. 2, reference numeral 10 denotes a material to be rolled. The material to be rolled 10 is sandwiched between a pair of upper and lower work rolls 11. Each work roll 11 is supported by four backup rolls 14 via two first intermediate rolls 12 and three second intermediate rolls 13. In FIG. 2, the upper back-up roll is not shown.

Of each back-up roll 14, two back-up rolls 14 on the center side of the rolling mill are provided with support roll eccentric devices.

As shown in FIG. 3, the support roll eccentric device has a roll shaft 17 whose both ends are rotatably supported by bearing stands 15 and 16, and is rotatable at equal intervals in the axial direction of the roll shaft 17. And five saddles 19 rotatably fitted on a roll shaft 17 on both axial sides of each roller 18.

Each roller 18 is formed by a bearing.

Each saddle 19 has an arcuate shroud portion 20 below it. A bearing surface 22 that supports a part of the shoe 20 is formed in an arc shape in the housing 21.

When the rolling force is not applied to the bearing roller 18, a slight gap is provided between the part 20 and the bearing surface 22. This gap is closed when a rolling force acts on the bearing roller 18 from the second intermediate roll 13 side.

That is, a slight gap is provided between the part of the shoe 20 and the bearing surface 22 so that the part of the shoe 20 comes into contact with the bearing surface 22 due to the reaction force from the second intermediate roll 13 during rolling.

As shown in FIG. 1 (A) and (B), each saddle An eccentric ring 23 is fitted over a portion corresponding to the screw 19 and connected by a key 31. Each eccentric ring 23 is provided such that a center Y is eccentric by an eccentric amount L with respect to a center X of the π-axis 17. The two eccentric rings 23 have the same phase at the center, and are set so that the phase shifts symmetrically by the same angle in order as they move toward the rain end side in the axial direction.

Accordingly, the gap between the bush portion 20 and the bearing surface 22 increases or decreases sequentially from the center to both sides in the axial direction.

A saddle 19 is rotatably fitted around the outer periphery of each eccentric ring 23 via a needle bearing 24. The saddle 19 is sandwiched between a pair of retainers 26 uru fixed on both sides of the eccentric ring 23 with rivets 25.

At one end of each roll shaft 17 of the two back-approaches 14 on the center side, as shown in FIGS. 3 and 4, a sector gear 26a that meshes with each other is provided. One sector-one gear 26a is operatively connected to a hydraulic motor 29 via a gear 27 and a shaft 28. The hydraulic motor 29 has a speed reducer, a brake and a position detector, and the hydraulic motor 29 constitutes a rotating means.

Note that, of the four backup rolls 14, the two backup rolls 14 at both ends are not provided with a support roll eccentricity device. That is, in the backup rolls on both sides, a concentric ring is provided between the roll shaft and the saddle instead of the eccentric ring.

In the above configuration, during rolling, the roll shafts 17 of the two backup rolls U on the center side are rotated by the hydraulic motor 29 through the gear 27 and the pair of sector gears 26a in the opposite directions by the same angle. Then, the roll shaft 17 is adjusted so that a predetermined curve is added to each roll shaft 17. For example, when the roll shaft 17 is rotated in the direction indicated by the arrow a shown in FIG. However, since the amount of eccentricity in the vertical direction changes according to the phase difference of each eccentric ring 23, as shown in Fig. 5, the two saddles 19 at the center are lowest, and the saddles are shifted toward both sides in the axial direction. The position of 19 goes higher. Therefore, if rolling is started in this state, the reaction force from the material to be rolled 10 acts on each roller 18 of the backup roll 14 via the work roll 11, the intermediate rolls 12, 13, and pushes each saddle 19 downward. Therefore, a part 20 of each saddle 19 comes into contact with the bearing surface 22 of the housing 21. As a result, the roll shaft 17 bends in a convex crown shape as shown in FIG. 6, and this bend causes each roller 18 to be pressed against the intermediate roll 13, and the stress peak at the shoulder portion of each roller 18 is conventionally reduced. It can be kept smaller than this.

Also, if the roll shaft 17 is rotated in the direction indicated by the arrow b shown in FIG. 1A, the saddle 19 at the center becomes higher than the saddles 19 at both ends as shown in FIG. Therefore, at the time of rolling, the roll shaft 17 is bent in a concave crown shape as shown in FIG.

Therefore, the bending curve of the roll shaft 17 can be adjusted arbitrarily by changing the rotation direction and the rotation angle of the roll shaft 17, and the bending state of the work roll 11 can be changed effectively. Further, since the roll shaft 17 is rotated by the hydraulic motor 29, the rotation means can be configured simply and in a small space.

The adjustment of the deflection curve by the hydraulic motor 29 can be performed not only before rolling, but also when the shape is defective during rolling. That is, since the hydraulic motor 29 is of a high torque type, and the needle bearing 24 is interposed between each saddle 19 and the eccentric ring 23 to reduce the friction coefficient for the rotation, the hydraulic motor 29 is in the middle of rolling. Even so, the deflection curve can be changed.

The hydraulic motor 29 is not limited to the high torque type, and may be a low torque type. A hydraulic motor 29 may be provided for each of the two roll shafts 17. The rotating means may be an electric motor in addition to the hydraulic motor 29, or may be of a type that is manually rotated using a hand gear mechanism or the like.

The one shown in Fig. 9 is a 12-high cluster rolling mill. This rolling mill includes a pair of upper and lower work rolls 101, 102, and a pair of upper and lower churou rolls 103, left and right (the rolling pass direction is the left and right direction) located on the upper left and upper right of the work rolls 1D1, 102. 104 and the lower left and right lower rolls 105 and 106 located on the lower left and lower right of the work rolls 101 and 102, and the upper and lower intermediate rolls 10S to 106 each have three upper and lower backup rolls 107, Backed up by 10 8, 109, 110, 111, 112.

As shown in FIG. 10, the upper backup rolls 107, 108, and 109 each include bearings 113, 114, and 115 rotatably fitted on one roll shaft 116, 117, and 118, respectively. Roll 107 has seven bearings 113, left backup roll 108 has six bearings 114, and right back-up roll 109 has five bearings 115. Saddle 119 arranged between bearings 113 of the central back-up roll. , 119A are fixedly attached to the mill housing 126. Crown control devices are provided on the back-up rolls 108, 109 on both the left and right sides.

The crown control device has fixed saddles 120A and 121A on the rain side and movable saddles 120 and 121 disposed between the bearings 114 and 115.

The number of left movable saddles 120 is five, and the number of right movable saddles 121 is four. The left and right saddles 120, 121 are shifted axially by about half the bearing pitch (center-to-center distance). The central service The dollar 119 and the saddle 121 on the right are almost the same. The saddles 120A, 121A at both ends of the left and right backup α-bars 108, 109 are fixed to the mill housing 126 by clampers 127, 128.

The movable saddles 120, 121 are supported by individual saddle supports 122, 123, respectively. Eccentric shafts 124, 125 orthogonal to the π-axis 117, 118 are respectively rotatable on the saddle supports 122, 123. The movable saddles 120 and 121 are supported by a mill housing 126 via saddle receivers 122 and 123 by eccentric shafts 124 and 125 so as to be slidable in a direction orthogonal to the roll shafts 117 and 118.

The eccentric shafts 124 and 125 of the movable saddles 120 and 121 have the same structure on both the left and right sides as shown in FIGS. 10 to 12, and are rotatably supported on the mill housing 126 by bearings 129, 130 and 131. The shaft upper ends 124Α and 125Α protrude upward from the mill housing 126 and have sector gears 132 fixed thereto. Each sector gear 132 is driven by a servomotor 136 via an intermediate gear 133, a drive gear 134 and a cycle reducer 135. As shown in FIG. 12, the center C of the eccentric shaft portions 124Β and 125Β of the eccentric shafts 124 and 125 is eccentric by S with respect to the center C1 of the bearings 129 and 130.

In the above embodiment, when the shape control of the plate to be rolled すなわち, that is, the backup roll position control, is performed, the eccentric shafts 124 and 125 are individually driven by the servomotor 136, and the bearings 114 and 115 are connected to the roll shafts 117 and 118. By reciprocating in the orthogonal direction and controlling the position, the roll shafts 117 and 118 are deformed (curved), and the work roll 101 is deformed via the intermediate rolls 103 and 104, and the thickness of the rolled plate の in the width direction is obtained. It is possible to control the shape of the rolled sheet によって generated by the distribution and the thickness distribution. The plate shape control characteristics of the 12-high rolling mill shown in FIG. 10 become dense as shown in FIG. That is, the center position of the nine right and left eccentric shafts 124 and 125 Since the rolls 101 are alternately arranged in the axial direction, the ability to control the elongation rate is subdivided, and the uncontrollable portion is reduced as shown by hatching in FIG. Therefore, plate shape control can be performed with accuracy o

The 20-high rolling mill shown in FIG. 14 incorporates both the support roll eccentricity device and the crown control device.

That is, the support roll eccentric device is incorporated in the two backup rolls 201 and 202 at the upper and lower central portions. The crown control device is incorporated in the backup rolls 203 on the left and right sides on the upper side. The backup rolls 204 on the left and right sides on the lower side incorporate a hydraulic pressure reduction device.

The upper and lower first intermediate rolls 205 are lateral adjust rolls that can move in the axial direction. Further, the first intermediate roll 205 is provided with a roll bending device for moving both end portions in the axial direction in the radial direction. Of the upper and lower second intermediate rolls 206, those on the left and right sides are drive rolls. Reference numeral 207 indicates a work roll.

The reason why the supporting roll eccentric device is provided for the two center back-up rolls 201 and 202 and the crown control device is provided for the left and right back-up rolls 203 is as follows.

The operating force may be small because the saddle control only needs to be pushed one saddle at a time, but the eccentricity of the supporting roll rotates one roll shaft, so the operating force increases.

Therefore, in the case of a 20-high rolling mill, the supporting roll eccentric device was incorporated in the backup rolls 201 and 202 at the center where the acting load was small.

Since the crown control can move each saddle individually and independently, the deflection curve of any pattern can be obtained. In the eccentric device, since the amount of eccentricity is fixed, only one pattern of deflection curve can be obtained.

Therefore, by combining the crown control device and the support roll eccentric device, various radius curves can be obtained over a wide range, and the shape correcting ability is improved.

In this combination, it is preferable to control the portion whose shape cannot be controlled only by the support roll eccentric device by the crown control device. That is, the flatness of the material to be rolled is controlled by the support roll eccentric device, and the control of a shape that cannot be handled by the support roll eccentric device is controlled by the crown control device.

Further, by combining the supporting roll eccentric device and the roll bender device, the shape correcting ability is further improved.

That is, as shown in FIG. 15, when a large convex pressing is performed by the support roll eccentric device, a portion where a load is hardly applied to the roll end is generated. In such a state, when a force in the direction of the backup roll 201 is applied to both ends of the first intermediate roll 205 by a bending device, the bending force reaches the center of the first intermediate roll 205, and the work port rolls. 207 can be made flat, and the material to be rolled P becomes flat.

On the other hand, as shown in Fig. 16, when the amount of eccentricity of the supporting roll is set to 0, the crown shape of the material P to be rolled affects the intermediate roll 205 and the center of the roll becomes concave, so that the first intermediate Even when the bending force is applied to the end of the roll 205, the bending force does not work to the center of the roll, and the flat material cannot be obtained.

Therefore, in the comparison between FIG. 15 and FIG. 16, it can be clearly understood that the shape control ability of the vendor is improved by the synergistic effect of the combination of the support roll device and the vendor device.

In the 12-high rolling mill shown in FIG. 17, the support roll eccentric device is also used. And the crown control π-control device are both incorporated.

That is, the crown control device is incorporated in the backup rolls 301 on both the upper left and right sides. A backup roll eccentric device is incorporated in the backup rolls 302 on the lower left and right sides. The hydraulic roll-down device is incorporated in the lower central backup roll 303.

The upper and lower intermediate rolls 304 are lateral adjust rolls that can move in the axial direction. Further, the intermediate roll 304 is provided with a roll bending device that moves both ends in the axial direction in the radial direction. Further, the intermediate roll 304 is a driving roll.

The reason why the support roll eccentricity is provided on the left and right pack-up rolls 302 is as follows: (1) In the two-high rolling mill, there is only one central backup roll, so if you have a support roll eccentricity In this case, when the roll shaft is moved sideways, the deflection curve of the roll shaft is not symmetrical with respect to the center of the rolling mill.

The embodiments described in this specification are illustrative and not restrictive. The scope of the invention is indicated by the appended claims, and all modifications that fall within the meaning of those claims are included in the present invention.

[Industrial applicability]

The present invention is incorporated in a multi-high rolling mill for rolling a sheet material,

Claims

The scope of the claims

A housing has a pair of primary crawls, an intermediate roll supporting the primary crawls, and a backup roll supporting the central crawls, wherein the back-up rolls extend in the axial direction with respect to the roll axis. The shape control device in a multi-high rolling mill composed of a plurality of bearings rotatably fitted at predetermined intervals is

A support roll eccentric device incorporated in at least one of the plurality of backup rolls,

The support roll eccentric device,

An eccentric ring that is externally fitted and fixed to the roll shaft on both sides in the axial direction of each of the bearings, and has a center eccentric with respect to the axis of the roll shaft;

A saddle that is rotatably fitted to each of the eccentric rings, and is supported so as to be able to freely contact and separate from the housing;

Rotating means for rotating the roll shaft;

It is composed of The shape control device for a multi-high rolling mill according to claim 1,

An arcuate shroud portion is formed on the outer peripheral surface of the saddle, and an arcuate bearing surface for supporting the shroud portion is formed on the housing,

In a free state in which a rolling load does not act on the backup roll, the gap between the part of the shoe and the bearing surface gradually increases or decreases from both ends of the roll shaft to the center thereof. The amount of eccentricity of multiple eccentric rings provided on the roll shaft is set

3. In the shape control device for a multi-high rolling mill according to claim 2, when the shape of the material to be rolled is convex at the central portion, the gap between the part of the shoe and the bearing surface is located from the rain end of the roll shaft to the center. Section, it is set to decrease sequentially,

When the material to be rolled is concave at the center, the gap between the part of the shoe and the bearing surface is set so as to increase gradually from both ends of the roll shaft to the center.

4. The shape control device for a multi-high rolling mill according to claim 2,

The plurality of eccentric rings provided on the one roll shaft are formed in the same shape,

The mounting angles of the eccentric ring to the roll shaft are sequentially shifted. 5. The shape control device for a multi-high rolling mill according to claim 1,

A 21-dollar bearing is provided between the saddle and the eccentric ring.

6. The shape control device for a multi-high rolling mill according to claim 1,

The shape control device of a multi-high rolling mill according to claim 1, wherein retainers are fixed to both sides of the eccentric ring or the saddle in the axial direction to prevent relative movement of the eccentric ring and the saddle in the axial direction.

The rotating means includes a gear fixed to one end of the roll shaft.

And a motor for driving the gear.

8. The shape control device for a multi-high rolling mill according to claim 1, wherein the multi-high rolling mill is a 20-high rolling mill, and at least two backup rolls at the center among at least four upper backup rolls. The support roll eccentric device is incorporated in the device.

9. The shape control device for a multi-high rolling mill according to claim 1,

The multi-high rolling mill is a 20-high rolling mill, and the support roll eccentric device is incorporated in at least two of the lower four back-up rolls, namely, the center two rolls and the Nukuatsu roll. 10. In the shape control device of the multi-high rolling mill according to claim 1,

The multi-high rolling mill is a 12-high rolling mill, and the support roll eccentric device is incorporated in at least two back-up rolls on both sides of at least three lower backup rolls. 11. The shape control device for a multi-high rolling mill according to claim 1,

The bearing rolls of the adjacent backup rolls are offset from each other in the axial direction.

12. The shape control device for a multi-high rolling mill according to claim 1,

The shape control device further includes a crown control device.

The crown control device is incorporated in at least one of the back-up rolls in which the supporting π-roll eccentric device is not incorporated. 13. The shape control device for a multi-high rolling mill according to claim 12,

The crown control device comprises: a saddle that supports the π-axis on both sides in the axial direction of each bearing; And an extruding device for individually extruding in the radial direction of the screw shaft.

14. The shape control device for a multi-high rolling mill according to claim 12,

The multi-high rolling mill is a 20-high rolling mill, and the crown control device is incorporated into two back-up rolls on both sides of the four upper-side rolls,

The support roll eccentric device is incorporated in two central back-up profiles.

15. The shape control device for a multi-high rolling mill according to claim 14,

The support roll eccentric device is incorporated in the center two knock-up rolls of the four lower backup rolls.

16. The shape control device for a multi-high rolling mill according to claim 12,

The multi-high rolling mill is a 12-high rolling mill, in which the crown control device is incorporated into two of the upper three backup rolls and two of the backup rolls on both sides.

The support roll eccentric device is incorporated in the lower three back-up rolls, the two sides of the back-up roll, and the tuck-up roll.

17. The shape control device for a multi-high rolling mill according to claim 12,

The bearing rolls of the adjacent back-up rolls are offset from each other in the axial direction.

18. —A pair of work rolls, a middle roulette roll that supports the single crawl, and a rotatable outer shaft that is rotatably mounted on the roll shaft at a predetermined interval in the axial direction to support the roll. With multiple bearings The shape of a multi-stage rolling machine comprising a backup roll formed and a support roll eccentric device that is incorporated into at least one of the plurality of backup rolls and imparts a predetermined bending curve to the roll shaft. A control method of a control device,

The control method includes:

When the shape of the material to be rolled is convex at the center, the rotating means is operated so that the arrangement of the bearings of the backup port is convex at the center,

When the shape of the material to be rolled is concave at the center, the rotating means is operated so that the arrangement of the bearings of the backup port is concave at the center.

19. A pair of work σ-rolls, an intermediate roll supporting the work π-rolls, and rotatably fitted to the roll shaft at a predetermined interval in the axial direction to support the intermediate rolls. A backup roll constituted by a plurality of bearings, a support roll eccentric device incorporated into at least one of the plurality of backup rolls, and imparting a predetermined radius curve to the roll shaft; Control of the shape control device of the multi-high rolling mill, which is comprised of at least one of the other back-up rolls that do not incorporate the roll eccentric device and a crown control device that pushes each bearing individually. The method

The control method is

In the case where the shape of the material to be rolled is convex at the center or concave at the center, the support roll eccentric device is operated so that the shape of the material to be rolled becomes flat,

Control of a shape that cannot be handled by the support roll eccentric device Controlled by a round control device