JP6992032B2 - Rolling machine - Google Patents

Description

The present invention relates to a rolling mill.

Patent Document 1 describes a rolling mill capable of removing the backlash of a roll bearing box of a rolling mill without enlarging the equipment, a rattling device for the roll bearing box, a rolling method, a method of modifying the rolling mill, and a method of modifying the rolling mill. As an example of hot-finishing tandem rolling equipment, a roll bearing box that rotatably supports a rolling roll in a housing and a first pressing device that imparts a vertical balance force or bender force to the rolling roll via the roll bearing box. And a second pressing device that applies a pressing force in the direction perpendicular to the rolling roll axis in the horizontal plane to the roll bearing box, and the first pressing device and the second pressing device are displaced in the rolling roll axis direction. It is described that the second pressing device is arranged between the plurality of first pressing devices in the rolling roll axis direction.

Further, as an example of a rolling mill that can prevent the generation of an extremely unbalanced load on a bearing, prolong the service life of the bearing, increase the roll shift amount, and improve the shape correction ability of the rolled material, Patent Documents In 2, the pressure of each of a plurality of bending cylinders arranged along the roll axis direction can be adjusted so that the resultant force of the bending force acting on the bearing of the rolling roll always acts on the center position in the longitudinal direction of the bearing. That is, for example, the hydraulic pressure of the cylinder near the center of the longitudinal direction of the bearing is set to be large, and the hydraulic pressure of the cylinder not close to the longitudinal direction of the bearing is set to be small, so that the position where the bending force acts is set. Even if they are different, it is described that the resultant force of the bending force is applied to the center of the bearing in the longitudinal direction.

WO2001 / 064360 Special Publication No. 63-055369

It has a shift function that moves the rolled roll in the roll axis direction and a bending function that applies a pressing force in the direction perpendicular to the axis to the roll bearing, and the horizontal rattling (gap) of the roll bearing box generated during rolling. A technique for eliminating the problem by using a rattling cylinder is known (see, for example, Patent Document 1).

In this rolling mill, a plurality of rattling cylinders are installed in the axial direction of the roll to prevent the rattling cylinders from coming off the roll bearing box and being pressed horizontally when the roll is shifted.

In addition, as a technology to suppress the eccentric load acting on the bearing and prolong the life of the bearing, the pressure of each cylinder is adjusted so that the resultant force of the bending force acting on the bearing acts on the central part in the roll axial direction of the bearing. A rolling mill configured to be capable of this is known (see, for example, Patent Document 2).

Here, in order for the bending force to act appropriately on the bearing, it is desirable that the center of the bearing in the roll axial direction be located in a range narrower than the distance between the plurality of bending cylinders arranged in the axial direction, and the roll is within this range. It is considered to be the maximum shift amount of the axial shift amount.

Further, in order to establish the function of the rattling cylinder, the rattling cylinder must be in a state where the bearing box is pushed.

Therefore, in a rolling mill that uses both a bending cylinder and a rattling cylinder, the rattling cylinder is arranged so that the range in which the pressing force of the rattling cylinder acts extends to the outside rather than the range in which the bending force acts. If this is the case, the bearing box needs to have a length equal to or greater than the total of the peeling cylinder spacing and the shift amount, which leads to an increase in the size of the structure around the bearing.

The present invention provides a rolling mill capable of appropriately applying a bending force and a pressing force of a rattling cylinder as compared with the conventional case to suppress an increase in the size of the apparatus.

The present invention includes a plurality of means for solving the above problems, for example, a roll for rolling a rolled material, a bearing receiving a load from the roll, and an entry side and an exit side in the rolling direction. One or more first cylinders that are arranged in any of the above and apply a bending force to the bearing in the vertical direction to bend the roll, and the bearing on either the entry side or the exit side in the rolling direction. A second cylinder that applies a pressing force to the rolling direction or the side opposite to the rolling direction, and all the first cylinders arranged on either the entry side or the exit side in the rolling direction. Are arranged so as to be offset in the axial direction of the roll when viewed from the rolling direction, and the second cylinder on the drive side is an entry side in the rolling direction on the drive side and the second cylinder on the drive side when viewed from the rolling direction. Of all the first cylinders arranged on any of the exit sides, the axial position of the first cylinder arranged closest to the rolled material and the first arranged farthest from the rolled material . Located at or between the axial positions of the cylinders, the second cylinder on the operating side is on the entry and exit sides of the rolling direction on the operating side when viewed from the rolling direction. Of all the first cylinders arranged in any of the above, the axial position of the first cylinder arranged closest to the rolled material and the shaft of the first cylinder arranged farthest from the rolled material. It is characterized by being located at or between them in the same direction .

According to the present invention, it is possible to appropriately act the bending force and the pressing force of the rattling cylinder as compared with the conventional case, and to suppress the increase in size of the apparatus. Issues, configurations and effects other than those mentioned above will be clarified by the description of the following examples.

It is a figure which shows the outline of the rolling equipment which provided the rolling mill of Example 1 or 2 of this invention. It is a front view explaining the outline of the rolling mill of Example 1 or 2. It is a figure which shows a part of the cross section of AA' in FIG. It is a figure which shows a part of the cross section of BB' in FIG. It is a top view explaining the detail of the intermediate roll part in the rolling mill of Example 1. FIG. It is a top view which explains the detail of the other outline of the intermediate roll part in the rolling mill of Example 1. FIG. It is a figure explaining the pressing force of the 2nd cylinder in the case of driving only the upper intermediate roll bearing box take-off cylinder inside the axial direction on the drive side of the rolling mill of Example 1. FIG. It is a figure explaining the pressing force of the 2nd cylinder in the rolling mill of Example 1, when only the upper intermediate roll bearing box outside the drive side in the axial direction is driven. It is a figure which shows a part of the cross section of the BB'-arrow view of FIG. 2 in the rolling mill of Example 2. FIG. It is a top view explaining the details of the work roll part in the rolling mill of Example 2. FIG.

<Example 1>
Example 1 of the rolling mill of the present invention will be described with reference to FIGS. 1 to 8. FIG. 1 is a view showing an outline of a rolling mill equipped with the rolling mill of the present embodiment 1 or 2, FIG. 2 is a front view explaining an outline of the rolling mill, and FIG. 3 is a cross section taken along the line AA'of FIG. FIG. 4 is a view showing a part, FIG. 4 is a view showing a part of the cross section taken along the line BB'of FIG. 2, and FIGS. 5 and 6 are plan views illustrating the details of the intermediate roll portion.

First, the outline of the rolling equipment provided with the rolling mill of the first embodiment will be described with reference to FIG.

As shown in FIG. 1, the rolling equipment 1 is provided with a plurality of rolling mills for hot rolling the rolled material 5 onto strips, and the first stand 10, the second stand 20, and the third stand are located from the entry side of the rolled material 5. It has 7 stands of a stand 30, a 4th stand 40, a 5th stand 50, a 6th stand 60, and a 7th stand 70, and a control device 80. Of the first stand 10, the second stand 20, the third stand 30, the fourth stand 40, the fifth stand 50, the sixth stand 60, the seventh stand 70, and the control device 80, the portion that controls each stand. Corresponds to the rolling mill in the present invention.

The rolling equipment 1 is not limited to the 7 stands as shown in FIG. 1, and may consist of at least 2 stands or more.

Next, a part of the outline of the rolling mill of the present invention will be described with reference to FIG. Although the seventh stand 70 shown in FIG. 1 will be described as an example in FIG. 2, the rolling mill of the present invention has the first stand 10, the second stand 20, the third stand 30, and the fourth stand 40 shown in FIG. , 5th stand 50 and 6th stand 60 can be applied to any of the stands.

In FIG. 2, the seventh stand 70, which is the rolling mill of the present embodiment, is a six-stage rolling mill that rolls the rolled material 5, and includes a housing 700, a control device 80, and a hydraulic device (not shown). Have.

The housing 700 includes an upper working roll 710 and a lower working roll 711, an upper intermediate roll 720 and a lower intermediate roll 721 that are supported by contacting the upper working roll 710 and the lower working roll 711, respectively. Further, it is provided with an upper reinforcing roll 730 and a lower reinforcing roll 731 that are supported by contacting the upper intermediate roll 720 and the lower intermediate roll 721, respectively.

Of these rolls, at the axial end of the upper work roll 710, a bearing (omitted for convenience of illustration) that shifts in the axial direction of the roll together with the upper work roll 710 and receives the load from the roll is on the drive side. It is provided on both the operation side and the operation side, and these bearings are supported by the upper working roll bearing box 712. Similarly, the lower work roll 711 is also provided with bearings (not shown) at the axial ends on both the drive side and the operation side, and these bearings are supported by the lower work roll bearing box 713. ..

In this embodiment, the upper work roll 710 is configured to be shiftable in the roll axial direction by the shift cylinder 715 as shown in FIG. 3 via the upper work roll bearing box 712 on the operation side. Similarly, the lower work roll 711 is also configured to be shiftable in the roll axis direction by the shift cylinder 716 as shown in FIG. 3 via the lower work roll bearing box 713 on the operation side.

The upper intermediate roll 720 is provided with bearings 790 (see FIG. 5) at its axial end on both the drive side and the operation side, and these bearings 790 are provided by the upper intermediate roll bearing boxes 722A and 722, respectively. I support it. The lower intermediate roll 721 also has bearings (not shown) at the ends in the axial direction on both the drive side and the operation side, and these bearings are supported by the lower intermediate roll bearing boxes 723A and 723, respectively. ..

Further, the upper intermediate roll 720 is configured to be shiftable in the roll axis direction by a shift cylinder 725 as shown in FIG. 3 via the upper intermediate roll bearing box 722A on the drive side. Similarly, the lower intermediate roll 721 is also configured to be shiftable in the roll axial direction by the shift cylinder 726 as shown in FIG. 3 via the lower intermediate roll bearing box 723A on the drive side.

Returning to FIG. 2, the entry-side fixing member 702 is fixed to the entrance-side housing 700 of the rolled material 5, and the outside of the rolled material 5 is attached to the exit-side housing 700 facing the entry-side fixing member 702. The exit side fixing member 703 is fixed.

In the seventh stand 70, as shown in FIGS. 2 and 4, the upper work roll bending cylinder 740 and the upper work roll bending cylinder 740 provided in the work roll bending block portion 714 of the entry side fixing member 702 are on both the operation side and the drive side. The upper work roll bearing box 712 is supported by the upper work roll bending cylinder 742 provided in the intermediate roll bending block portion 727 and the upper work roll bending cylinders 741 and 743 provided in the output side fixing member 703. By appropriately driving these cylinders, a bending force is applied to the bearing of the upper work roll 710 in the vertical direction so that the upper work roll 710 can be bent.

Similarly, as shown in FIGS. 2 and 4, both the operation side and the drive side are provided on the lower work roll bending cylinder 744 and the lower intermediate roll bending block portion 728 provided on the entry side fixing member 702. The lower work roll bearing box 713 is supported by the lower work roll bending cylinder 746 and the lower work roll bending cylinders 745 and 747 provided on the output side fixing member 703, and these cylinders are appropriately driven. A bending force is applied to the bearing of the lower work roll 711 in the vertical direction so that the lower work roll 711 can be bent.

The upper intermediate roll 720 has an upper intermediate roll bending cylinder 750 and an outer intermediate roll bending cylinder 750 provided on the upper intermediate roll bending block portion 727 of the entry side fixing member 702 on both the operation side and the drive side. The upper intermediate roll bearing boxes 722 and 722A are supported by the upper intermediate roll bending cylinder 751 provided in the block portion 727, and bending force is applied to the bearing 790 in the vertical direction by appropriately driving these cylinders. The upper middle roll 720 can be bent. Further, the upper intermediate roll bending block portion 727 is provided with upper work roll bending cylinders 742 and 743 on the entry side and the exit side so that the upper work roll 710 can be bent by appropriately driving these cylinders. It has become.

The lower intermediate roll 721 also has the lower intermediate roll bending cylinder 752 and the lower intermediate roll bending of the exit side fixing member 703 provided in the lower intermediate roll bending block portion 728 of the entry side fixing member 702 on both the operation side and the drive side. The lower intermediate roll bearing boxes 723 and 723A are supported by the lower intermediate roll bending cylinder 753 provided in the block portion 728, and bending force is applied to the bearing 790 in the vertical direction by appropriately driving these cylinders. The lower middle roll 721 can be bent. Further, the lower intermediate roll bending block portion 728 is provided with lower work roll bending cylinders 746 and 747 on the entry side and the exit side so that the lower work roll 711 can be bent by appropriately driving these cylinders. It has become.

Of these cylinders, the upper work roll bending cylinders 740 and 741 apply bending force to the bearing of the upper work roll 710 in contact with the rolled material 5 in the vertical direction to the increase side (anti-roll material side) to apply the bending force to the upper work roll 710. Is arranged so as to bend (first cylinder). Further, the upper work roll bending cylinders 742 and 743 apply a bending force on the vertical decree side (rolled material side direction) opposite to the upper work roll bending cylinders 740 and 741 to the bearings to bend the upper work roll 710. It is arranged like this.

Similarly, the lower work roll bending cylinders 744 and 745 are arranged so as to apply a bending force to the bearing of the lower work roll 711 in contact with the rolled material 5 on the vertical oil lease side to bend the lower work roll 711 (. 1st cylinder). Further, the lower work roll bending cylinders 746 and 747 are arranged so as to apply a bending force on the decree side in the direction opposite to the lower work roll bending cylinders 744 and 745 to the bearings to bend the lower work roll 711.

The upper intermediate roll bending cylinders 750 and 751 are arranged so as to apply a bending force to the bearing 790 of the upper intermediate roll 720 on the vertical oil lease side to bend the roll (first cylinder).

The lower intermediate roll bending cylinders 752 and 753 are arranged so as to apply a bending force to the bearing 790 of the lower intermediate roll 721 on the vertical oil lease side to bend the lower intermediate roll 721 (first cylinder).

As shown in FIGS. 2 and 4, for the purpose of removing rattling, the upper work roll 710 is attached to the inner side fixing member 702 on the inner side of the rolled material 5 via a liner (not shown) of the upper work roll bearing box 712. The upper working roll bearing box is provided with a take-off cylinder 760 so as to apply a force in the horizontal direction, specifically, a pressing force in the rolling direction (second cylinder). Similarly, the entry side fixing member 702 is provided with a lower work roll bearing box removal cylinder 762 so as to apply a pressing force to the lower work roll 711 in the rolling direction via the liner of the lower work roll bearing box 713. (2nd cylinder). As a result, a desired force can be applied to the working roll or the like in a direction orthogonal to the roll axis direction.

Further, as shown in FIGS. 2 and 3, for the purpose of removing rattling, the upper intermediate roll 720 is attached to the outer side fixing member 703 on the outer side of the rolled material 5 via the liners of the upper intermediate roll bearing boxes 722A and 722. The upper intermediate roll bearing box is provided with a take-off cylinder 771 so as to apply a force in the horizontal direction, that is, a pressing force on the side opposite to the rolling direction (second cylinder). Similarly, the lower intermediate roll bearing box is attached to the output side fixing member 703 so as to apply a pressing force to the lower intermediate roll 721 via the liners of the lower intermediate roll bearing boxes 723A and 723 in the direction opposite to the rolling direction. A taking cylinder 773 is provided (second cylinder).

Returning to FIG. 2, bearings (not shown) are provided at the axial ends of the upper reinforcing roll 730 on both the drive side and the operation side, and these bearings are supported by the upper reinforcing roll bearing box 732. There is. Similarly, the lower reinforcing roll 731 is provided with bearings (not shown) at the axial ends on both the drive side and the operation side, and these bearings are supported by the lower reinforcing roll bearing box 733. ..

Further, as shown in FIG. 2, the housing 700 on the entry side is provided with a cylinder 780 for removing the upper reinforcing roll bearing box so as to apply a horizontal force to the upper reinforcing roll 730 via the upper reinforcing roll bearing box 732. Has been done. Similarly, the housing 700 on the entry side is provided with a lower reinforcing roll bearing box removing cylinder 782 so as to apply a horizontal force to the lower reinforcing roll 731 via the lower reinforcing roll bearing box 733.

The hydraulic device includes each of the above-mentioned bending cylinders, rattling cylinders, shift cylinders, and reduction cylinders (not shown) that apply a reduction force for rolling the rolled material 5 to the upper work roll 710 and the lower work roll 711. It is connected to a hydraulic cylinder, and this hydraulic device is connected to the control device 80.

The control device 80 controls the operation of the hydraulic device and drives and controls each of the above-mentioned bending cylinders and the like by supplying and discharging pressure oil to each of the bending cylinders and the like.

Next, among the rolls, the configuration related to the upper intermediate roll 720 will be described with reference to FIG. The upper work roll 710, the lower work roll 711, and the lower intermediate roll 721 can also have the same configuration as the upper intermediate roll 720. Since the detailed configuration thereof is substantially the same as that of the upper intermediate roll 720, the description thereof will be omitted.

The present invention is preferably applied to the upper intermediate roll 720 or the lower intermediate roll 721 as shown in FIG.

As shown in FIG. 5, in this embodiment, two upper intermediate roll bending cylinders 750 are provided in the axial direction of the roll on the entry side of the rolled material 5 on each of the drive side and the operation side of the upper intermediate roll 720. Has been done. Further, two upper intermediate roll bending cylinders 751 are provided on the exit side of the rolled material 5, and the same number of first cylinders are arranged in the axial direction on each of the entry side and the exit side in the rolling direction. There are two. The two upper intermediate roll bending cylinders 750 provided on the entry side of the rolled material 5 and the two upper intermediate roll bending cylinders 751 provided on the exit side of the rolled material 5 overlap each other when viewed from the rolling direction. Is arranged. Here, in FIG. 5, the expressions of the work roll bending cylinders 742 and 743 described in FIGS. 2 and 4 are omitted.

Further, in the present embodiment, the upper intermediate roll bearing box removing cylinder 771 arranged on the outlet side of the rolled material 5 is located on the opposite side of the side where the second cylinder is located when viewed from the rolling direction. Of the first cylinders, the axial direction is arranged inward in the axial direction from the position of the outermost first cylinder. Further, among the first cylinders located on the opposite side of the side where the second cylinder is located when viewed from the rolling direction, the axial direction is arranged outside the position of the innermost first cylinder in the axial direction. More specifically, it is arranged at an intermediate position in the axial direction of the upper intermediate roll bending cylinder 751 provided on the same exit side.

When viewed from the rolling direction, the two first cylinders on the side where the second cylinder is located are the outermost cylinders in the axial direction among the first cylinders located on the opposite sides on the side where the second cylinder is located. It can be assumed that it is arranged at the same position as the position of the first cylinder and is arranged at the same position as the position of the innermost first cylinder in the axial direction.

That is, when viewed from the rolling direction, the first cylinders on the entry side are arranged apart from each other in the axial direction, and the first cylinders on the exit side are also arranged apart from each other in the axial direction. Of these, a second cylinder is provided between the outermost and innermost first cylinders in the axial direction or at the same position.

Further, of the two upper intermediate roll bending cylinders 750 provided on the entry side, the upper intermediate roll bending cylinder 750 on the outer side in the axial direction on both the drive side and the operation side is provided by the shift cylinder 725 via the shift mechanism 725A. It is desirable that the center of the bearing 790 is arranged outside the shift range when the upper intermediate roll 720 is shifted in the axial direction.

In this embodiment, the position where the output of one upper intermediate roll bearing box take-off cylinder 771 acts is set between the axial positions of the two upper intermediate roll bending cylinders 750 arranged on the entry side. It is desirable that it is arranged and the output is controlled.

Next, the details of the drive control of the upper intermediate roll bending cylinders 750 and 751 and the upper intermediate roll bearing box removing cylinder 771 of this embodiment will be described with reference to FIGS. 5 and 1. These drive controls are executed by the control device 80 that drives and controls the hydraulic device.

In this embodiment, when the rolls are bent, the output working positions of the four upper intermediate roll bending cylinders 750 and 751 and the output working positions of the one upper intermediate roll bearing box picking cylinder 771 are bearings, respectively. When the axial length of the ₇₉₀ is LB, within LB / 4 axially outward from the axial center of the bearing 790, and within _LB / 4 axially _inward from the axial center of the bearing 790. That is, it is configured to fit in the _LB / 2 at the axial center of the bearing 790.

In this case, the outputs of the upper and middle roll bending cylinders 750 and 751 can be adjusted more finely and separately so that the bending force is accurately applied to the axial center of the bearing 790.

For example, when the intermediate roll shifts L _s , depending on the position of the bearing of the intermediate roll, the acting force of the positions e1 and e2 on the drive side and the entry side of the operation side is multiplied by the coefficients αe1 and αe2 on the bending force Pbe on the entry side, respectively. The Pbe is driven as the output of the upper intermediate roll bending cylinder 750. On the output side, the acting force at the positions d1 and d2 is set to the value obtained by multiplying the bending force Pbd on the output side by the coefficients αd1 and αd2, respectively, and the Pbd is driven as the output of the upper intermediate roll bending cylinder 751.

The total of Pbe and Pbd is the total output on the drive side or the total output on the operation side, and is the bending force per bearing box of the intermediate roll. The action position of the resultant force of Pbe and Pbd is set so as to be substantially on the roll axis in the rolling direction, and is set to be the center of the bearing that shifts in the roll axis direction. The resultant force of Pbe and Pbd is a bending force required under the rolling conditions.

The position of the intermediate roll bearing box removal cylinder 771 is fixed to g1, and the pressing force thereof is Pg1. The position of the g1 is set so that it fits in the axial center _LB / 2 of the bearing 790 even when the intermediate roll shifts between L _s .

The values of αe1, αe2, αd1, and αd2 do not necessarily have to be the same, and the values are appropriately different so that the action positions of the outputs of the four upper and intermediate roll bending cylinders 750 and 751 substantially coincide with the center positions of the bearing 790. Can be. Of course, the same value can be set depending on the position of the upper intermediate roll 720.

Further, it is not limited to driving all four cylinders in total, and it is possible to drive three out of four cylinders or two out of four cylinders.

In this case, only one or two of αe1, αe2, αd1 and αd2 becomes 0, and the remaining three or two variables are appropriately set.

Next, other arrangement examples such as the upper intermediate roll bending cylinder and its output control will be described with reference to FIGS. 6 and 2 .

In the form shown in FIG. 6, two upper intermediate roll bending cylinders 750A are provided on the inlet side of the rolled material 5 in the axial direction of the roll. Further, one upper intermediate roll bending cylinder 751A is provided on the outlet side of the rolled material 5.

Of these, the upper intermediate roll bending cylinder 751A provided on the exit side of the rolled material 5 is located between the two upper intermediate roll bending cylinders 750A provided on the opposite entry side when viewed from the rolling direction. Arranged to do.

Further, of the two upper intermediate roll bending cylinders 750A provided on the entry side, the upper intermediate roll bending cylinder 750A on the outer side in the axial direction on both the drive side and the operation side is provided by the shift cylinder 725 via the shift mechanism 725A. The center of the bearing 790 is arranged outside the shift range when the upper intermediate roll 720 is shifted in the axial direction.

Further, the upper intermediate roll bearing box take-off cylinder 771A arranged on the protruding side of the rolled material 5 is a shaft of the upper intermediate roll bending cylinder 751A provided on the same protruding side when viewed from the rolling direction. It is placed on both sides of the direction.

Further, in the upper intermediate roll bearing box take-off cylinder 771A, the axial position of the cylinder on the outer side in the axial direction is the cylinder on the outer side in the axial direction among the two upper intermediate roll bending cylinders 750A provided on the opposite entrance side. It is placed at the same position as or inside the position. The axial position of the upper intermediate roll bearing box backing cylinder 771A on the inner side in the axial direction is the same as or higher than the cylinder on the inner side in the axial direction among the two upper intermediate roll bending cylinders 750A provided on the opposite entrance side. It is placed in the inner position.

Further, also in this embodiment, the position where the output of the two upper intermediate roll bearing box take-off cylinders 771A acts is settled between the axial positions of the two upper intermediate roll bending cylinders 750A arranged on the entry side. It is desirable that they are arranged in such a manner and that the output is controlled.

Next, the details of the drive control of the upper intermediate roll bending cylinders 750A and 751A and the upper intermediate roll bearing box removing cylinder 771A of this embodiment will be described. These drive controls are also executed by the control device 80 that drives and controls the hydraulic device.

First, at the time of bending the roll, the difference between the total output of the two first cylinders and the output of the first cylinder provided on the opposite side is configured to be within a predetermined range. Further, when the center of the bearing 790 is arranged between the two upper intermediate roll bending cylinders 750A arranged on the entry side, and when the roll is bent, one of the two first cylinders and the opposite side. It is configured to drive the first cylinder provided in.

Here, the shift amount of the upper intermediate roll 720, that is, the shift amount at the center of the bearing 790 in the axial direction is _LS (the shift amount on the drive direction side is positive). L _S is divided into sections A, B, and C. Table 2 shows the relationship between the bearing center position and the driving state of each cylinder. The intersection position of the line connecting e1 and d1 and the roll axis is the boundary between section C and section B, and the intersection position of the line connecting e2 and d1 and the roll axis is the boundary between section B and section A.

When the axial center of the bearing exists in the section C, on the drive side, a predetermined coefficient αe1 is applied to the bending force Pbe on the entry side, which requires the outputs of the upper and middle roll bending cylinders 750A, e1 and e2 on the entry side. The output obtained by multiplying and αe2, respectively, and the upper and middle roll bending cylinders 751A and d1 on the output side are driven. In the section C, by setting αe1 to 1 and selecting αe2 to 0, the bending force can be applied closer to the center of the bearing.

On the operation side, the output of the input side bending force Pbe that requires the output of the input side upper intermediate roll bending cylinders 750A, e1 and e2 multiplied by the predetermined coefficients αe1 and αe2, and the output of the output side upper intermediate roll bending. Drives the cylinders 751A and d1. In the section C, by setting αe1 to 1 and selecting αe2 to 0, the bending force can be applied closer to the center of the bearing.

Similarly to the section C, when the axial center of the bearing exists in the section A, the drive side drives the upper intermediate roll bending cylinder 750A on the entry side and the upper intermediate roll bending cylinder 751A on the exit side. In the section A, by setting αe1 to 0 and selecting αe2 to 1, a bending force can be applied closer to the center of the bearing.

On the operation side, the upper intermediate roll bending cylinder 750A on the entry side and the upper intermediate roll bending cylinder 751A on the exit side are driven in the same manner as in the section C. In the section A, by setting αe1 to 0 and selecting αe2 to 1, a bending force can be applied closer to the center of the bearing.

Even when the axial center of the bearing exists in the section B, as in the section C, the upper intermediate roll bending cylinder 750A on the entry side and the upper intermediate roll bending cylinder 751A on the exit side are provided on both the drive side and the operation side. Drive. The values of αe1 and αe2 in the section B are set so that the resultant force of the upper intermediate roll bending cylinder 750A on the entry side and the upper intermediate roll bending cylinder 751A on the exit side acts near the center of the bearing.

For the upper intermediate roll bearing box take-off cylinder 771A, the value is set to be the value obtained by multiplying the output Pg requiring the output at the positions g1 and g2 by γ1 and γ2, respectively, in the sections A, B, and C. The coefficients γ1 and γ2 in the sections A, B, and C are such that the pressing force of the upper intermediate roll bearing box removing cylinder 771A acts on the center of the shifting bearing.

Next, the effect of this embodiment will be described.

The rolling mill of the present embodiment described above has a roll for rolling a rolled material, a bearing 790 that receives a load from the roll, and a bending force in the vertical direction with respect to the bearing 790 on each of the entry side or the exit side in the rolling direction. To apply a pressing force to the bearing 790 in the rolling direction or on the side opposite to the rolling direction on either the entry side or the exit side in the rolling direction with one or more first cylinders that bend the roll. It is equipped with two cylinders. Of these, in the first cylinder, when viewed from the rolling direction, at least one first cylinder on the entry side or the exit side in the rolling direction is arranged so as to be separated from each other in the axial direction of the roll, and the second cylinder is arranged. When viewed from the rolling direction, of all the first cylinders arranged on the entry side or the exit side in the rolling direction, the axial direction is the same as or between the positions of the outermost and innermost first cylinders. Is located in.

As a result, the other second cylinder (rattle cylinder) on the entry side or the exit side is installed in the installation range of the first cylinder (bending cylinder) on the entry side or the exit side. For this reason, it is possible to prevent the range of action of the pressing force of the second cylinder from significantly exceeding the range in which the bending force is applied so as not to generate an eccentric load on the bearing, so that the bending force and the pressing force can be appropriately applied to the bearing. It is possible to suppress the increase in size of the device while acting on the surface.

The effects produced by the pressing force of the second cylinder acting near the central portion in the longitudinal direction of the bearing are as follows.

FIG. 7 shows a case where only the upper intermediate roll bearing box on the inner side in the drive side is driven by the take-off cylinder 771, and the pressing force of the second cylinder acts on the vicinity of the central portion in the longitudinal direction of the bearing. The rolling direction force Fd acting on the bearing from the roll, the pressing force Fg2 of the second cylinder, the outer reaction force F1 generated in the liner of the upper intermediate roll bearing box 722A and the upper intermediate roll bending block portion 727, and the inner reaction force F2. Then, the relationship is Fg2 = Fd + F1 + F2. When either F1 or F2 becomes 0, the liner does not hit, which is not preferable. Here, since Fg2 is generated near the Fd action position, Fg2 can be set to a relatively small value. That is, the pressing force of the second cylinder can be reduced.

On the other hand, FIG. 8 shows a case where only the upper intermediate roll bearing box on the outer side in the drive side is driven by the take-off cylinder 771, and the pressing force of the second cylinder acts at a position away from the vicinity of the central portion in the longitudinal direction of the bearing. The case is shown. Similarly, the pressing force Fg1 of the second cylinder has a relationship of Fg1 = Fd + F1 + F2. In order to prevent F2 from becoming 0, Fg1 becomes a large value due to the balance of moments. This requires a larger second cylinder, which makes it difficult to structurally accommodate the larger cylinder in the upper intermediate roll bending block portion 727.

As shown in FIG. 7, by applying the pressing force of the second cylinder to the vicinity of the central portion in the longitudinal direction of the bearing, the output required for the second cylinder is suppressed, the size of the cylinder is suppressed, and the upper middle roll bending block portion is formed. It can be stored in the 727.

Further, a control device 80 for driving the first cylinder is further provided, and the control device 80 is configured to drive three or more first cylinders so that the resultant force is applied to the central portion of the bearing 790. , The structure can be such that the bending resultant force is applied to the vicinity of the central portion in the longitudinal direction of the bearing. Therefore, even with a simple structure, the eccentric load on the bearing can be reduced.

<Example 2>
Next, the second embodiment of the rolling mill of the present invention will be described with reference to FIGS. 9 and 10. FIG. 9 is a diagram showing a part of the cross section taken along the line BB'in FIG. FIG. 10 is a plan view illustrating the details of the work roll portion.

9 and 10 will explain the differences from FIGS. 4 and 5. In this embodiment, on the drive side and the operation side of the upper work roll 710, one first cylinder 740 and one second cylinder 760 are provided on the entry side of the rolled material 5, and the second cylinder on the operation side. A first cylinder 740 is provided on the outer side of the 760 in the axial direction. Further, one first cylinder 741 is provided on the exit side of the rolled material 5, and when viewed from the rolling direction, the first cylinder 741 is axially inside the second cylinder 760 on the entry side on the operation side. It is provided. Further, on the drive side, the first cylinder 740 is provided inside the second cylinder 760 in the axial direction. Further, one first cylinder 741 is provided on the exit side of the rolled material 5, and when viewed from the rolling direction, the first cylinder 741 is axially outside the second cylinder 760 on the entry side on the drive side. It is provided.

As a result, in the upper working roll bearing box 712, the range of action of the pressing force of the second cylinder can be suppressed to greatly exceed the range of action of the bending resultant force of the first cylinder, so that the bending force and the pressing force are appropriate. It is possible to suppress the increase in size of the device while acting on the bearing.

In the upper work roll 710, when viewed from the rolling direction, the first cylinder on the entry side is provided on the inner side in the axial direction from the second cylinder on the operation side, and the first cylinder on the exit side is more shaft than the second cylinder. It may be provided outside the direction. Further, on the drive side, the first cylinder on the entry side may be provided on the outermost side in the axial direction, and the first cylinder on the exit side may be provided on the innermost side in the axial direction. Further, the axial position of the second cylinder may be the same as the axial position of the first cylinder on the entry side and the exit side, whichever is not provided with the second cylinder.

Although the above describes the working roll, the above can be applied to the intermediate roll.

Further, although the case where the shift amount _LS is a certain amount has been described above, it can also be applied to a roll in which the _LS is 0 and the shift amount is not shifted. That is, the present invention can be applied to any rolling mill that applies a bending force in the vertical direction and a pressing force in the rolling direction to the bearing. Since the range of action of the pressing force of the second cylinder can be suppressed to greatly exceed the range of action of the bending resultant force of the first cylinder, the bending force and the pressing force are appropriately applied to the bearing, and the size of the device is large. It is possible to suppress the change.

<Others>
The present invention is not limited to the above embodiment, and various modifications and applications are possible. The above-mentioned examples have been described in detail in order to explain the present invention in an easy-to-understand manner, and are not necessarily limited to those having all the described configurations.

1 ... Rolling equipment 5 ... Rolled material 10 ... First stand (rolling machine)
20 ... 2nd stand (rolling machine)
30 ... 3rd stand (rolling machine)
40 ... 4th stand (rolling machine)
50 ... 5th stand (rolling machine)
60 ... 6th stand (rolling machine)
70 ... 7th stand (rolling machine)
80 ... Control device 700 ... Housing 702 ... Enter side fixing member 703 ... Outer side fixing member 710 ... Upper work roll (roll)
711 ... Lower work roll (roll)
712 ... Upper work roll bearing box 713 ... Lower work roll bearing box 714 ... Work roll bending block portion 715, 716,725,726 ... Shift cylinder 720 ... Upper intermediate roll (roll)
721 ... Lower middle roll (roll)
722,722A ... Upper intermediate roll bearing box 723,723A ... Lower intermediate roll bearing box 725A ... Shift mechanism 727 ... Upper intermediate roll bending block portion 728 ... Lower intermediate roll bending block portion 730 ... Upper reinforcing roll 731 ... Lower reinforcing roll 732 ... Upper reinforcing roll bearing box 733 ... Lower reinforcing roll bearing box 740, 741 ... Upper working roll bending cylinder (first cylinder)
742,743 ... Upper work roll bending cylinder 744,745 ... Lower work roll bending cylinder (first cylinder)
746,747 ... Lower work roll bending cylinder 750, 750A, 751,751A ... Upper intermediate roll bending cylinder (first cylinder)
752, 753 ... Lower intermediate roll bending cylinder (first cylinder)
760 ... Upper work roll bearing box backlash removal cylinder (second cylinder)
762 ... Lower work roll bearing box backlash removal cylinder (second cylinder)
771, 771A ... Upper intermediate roll bearing box backlash removal cylinder (second cylinder)
773 ... Lower intermediate roll bearing box backlash removal cylinder (second cylinder)
780 ... Upper reinforcing roll bearing box backlash removing cylinder 782 ... Lower reinforcing roll bearing box backlash removing cylinder 790 ... Bearing 812AB ... Upper working roll bearing box brim 822AB ... Upper intermediate roll bearing box brim

Claims (3)

Rolls for rolling rolled material and
Bearings that receive the load from the roll and
One or more first cylinders arranged on both the entry side and the exit side in the rolling direction to apply a bending force in the vertical direction to the bearing to bend the roll.
A second cylinder that applies a pressing force to the bearing in the rolling direction or on the side opposite to the rolling direction is provided on either the entry side or the exit side in the rolling direction.
All the first cylinders arranged on either the entry side or the exit side in the rolling direction are arranged so as to be offset in the axial direction of the roll when viewed from the rolling direction.
The second cylinder on the drive side is attached to the rolled material among all the first cylinders arranged on either the entry side or the exit side in the rolling direction on the drive side when viewed from the rolling direction. It is located at or between the axial position of the first cylinder closest to it and the axial position of the first cylinder farthest from the rolled material .
The second cylinder on the operation side is attached to the rolled material among all the first cylinders arranged on either the entry side or the exit side in the rolling direction on the operation side when viewed from the rolling direction. It is characterized in that it is located at the same level as or between the axial position of the first cylinder arranged closest to the rolled material and the axial position of the first cylinder arranged farthest from the rolled material. Rolling machine. In the rolling mill according to claim 1,
A rolling mill characterized in that the first cylinder is arranged one by one on both the entry side and the exit side in the rolling direction . In the rolling mill according to claim 1 or 2.
Further equipped with a control device for driving the first cylinder,
The control device is a rolling mill configured to drive two or more of the first cylinders so that the resultant force is applied to the central portion of the bearing.

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