WO2024116356A1 - Rolling mill and rolling method - Google Patents

Abstract

The present invention comprises: a plurality of hydraulic cylinders that include drive-side shift cylinders 715C, 715D and operation-side shift cylinders 715A, 715B that are configured to apply force to an upper work roll 710 in the axial direction thereof; and a hydraulic circuit that is configured to send hydraulic fluid to the plurality of hydraulic cylinders to move the drive-side shift cylinders 715C, 715D and the operation-side shift cylinders 715A, 715B in the axial direction and hold the position of the upper work roll 710 in the axial direction. The hydraulic circuit is configured such that, when only either the drive-side shift cylinders 715C, 715D or the operation-side shift cylinders 715A, 715B are applying force to the upper work roll 710 in the axial direction due to external force on the upper work roll 710 after the hydraulic circuit has held the position of the upper work roll 710 in the axial direction, the other hydraulic cylinders move in the opposite direction.

Description

Rolling machine and rolling method

The present invention relates to a rolling machine and a rolling method.

Patent Document 1 describes an upper work roll, a radial bearing and a thrust bearing provided on the operating side and driving side of the upper work roll to support the upper work roll, a shift cylinder provided on the operating side of the upper work roll for applying a force to the thrust bearing in both the operating side and driving side directions, and a shift cylinder provided on the driving side of the upper work roll for applying a force to the radial bearing in both the operating side and driving side directions, and states that the shift cylinders each apply a force to the radial bearing and thrust bearing in the same direction when the upper work roll does not shift axially at least during rolling.

International Publication No. 2022/030004

Patent document 1 discloses a structure that shifts the rolls on both the drive side and the operating side.

When conditions such as rotation change, the direction of the thrust force acting on the rolls of a rolling mill can switch between the drive side and the operating side. In this case, a thrust force in the opposite direction acts on the roll after the roll position is set, causing the roll, or more specifically the members supporting the roll, to temporarily move away from the drive side and operating side arms that support the thrust force. As a result, the positions of the arms on both sides must be adjusted again to support the thrust force of the roll.

However, if there is uneven axial play (gap) in the support part that applies axial force to the roll, it may happen that the thrust force is supported by only one arm.

If one arm cannot support the load, the pressure in the piping connected to the hydraulic cylinder that moves the arm will exceed the relief valve set pressure (maximum pressure), and hydraulic oil will escape through the relief valve, causing the other arm to move as well. However, because the relief valve set pressure is high, it became clear through investigations that this could lead to a shortened lifespan of peripheral equipment such as bearings that are subjected to the load.

It has become clear that this is not limited to the above-mentioned cases, but that problems similar to those described above may occur if the roll expands due to heat from the heated metal band, as this can cause uneven play in the axial direction.

The present invention aims to provide a rolling mill and rolling method that can improve the life of roll support parts such as bearings on both sides of the roll without creating excessive pressure inside the piping connected to the hydraulic cylinder.

The present invention includes a number of means for solving the above problems, and an example thereof includes a mill roll, a number of hydraulic cylinders including a driving side hydraulic cylinder provided on the driving side of the mill roll configured to apply an axial force to the mill roll, and an operating side hydraulic cylinder provided on the operating side of the mill roll configured to apply the axial force, and a hydraulic circuit configured to feed hydraulic oil to the multiple hydraulic cylinders, so that the driving side hydraulic cylinder and the operating side hydraulic cylinder move in the axial direction and maintain the axial position of the mill roll, and the hydraulic circuit is configured such that after the hydraulic circuit has maintained the axial position of the mill roll, when an external force applied to the mill roll causes only one of the driving side hydraulic cylinder or the operating side hydraulic cylinder to apply the axial force to the mill roll, the other of the driving side hydraulic cylinder or the operating side hydraulic cylinder moves in the opposite direction to the one hydraulic cylinder.

According to the present invention, it is possible to improve the life of the roll support parts, such as the bearings on both sides of the roll, without creating excessive pressure inside the piping connected to the hydraulic cylinder. Other issues, configurations and effects than those mentioned above will become clear from the explanation of the embodiments below.

1 is a diagram showing an outline of a rolling facility including a rolling mill according to a first embodiment of the present invention; FIG. 1 is a front view for explaining an outline of a rolling mill according to a first embodiment. This is a view taken along the arrows A-A' in Figure 2. FIG. 1 is a schematic diagram illustrating a problem to be solved by the present invention. FIG. 1 is a schematic diagram illustrating a problem to be solved by the present invention. FIG. 1 is a schematic diagram illustrating a problem to be solved by the present invention. FIG. 2 is a plan view for explaining details of an upper work roll portion of the rolling mill of the first embodiment. FIG. 2 is a plan view for explaining details of an upper work roll portion of the rolling mill of the first embodiment. FIG. 2 is a plan view for explaining details of an upper work roll portion of the rolling mill of the first embodiment. FIG. 4 is a plan view for explaining details of an upper work roll portion of a rolling mill according to a modified example of the first embodiment. FIG. 11 is a plan view for explaining details of an upper work roll portion of a rolling mill according to a second embodiment. FIG. 11 is a plan view for explaining details of an upper work roll portion of a rolling mill according to a third embodiment. FIG. 11 is a plan view for explaining details of an upper work roll portion of a rolling mill according to a third embodiment. FIG. 11 is a plan view for explaining details of an upper work roll portion of a rolling mill according to a fourth embodiment.

Below, an embodiment of the rolling machine and rolling method of the present invention will be explained with reference to the drawings.

In addition, in the drawings used in this specification, identical or corresponding components are given the same or similar reference numerals, and repeated explanations of these components may be omitted.

In addition, in this specification, thrust resistance force refers to the force in the roll axial direction that acts on each roll and its bearing housing of the rolling mill during rolling or when shifting during rolling, and refers to the force that acts on the device that supports that force, and has the same meaning as thrust force. Thrust reaction force refers to the force that arises from the device that supports the thrust resistance force, and refers to a force that is the same magnitude as the thrust resistance force but in the opposite direction.

Example 1
A rolling mill and a rolling method according to a first embodiment of the present invention will be described with reference to FIGS. 1 to 10. FIG.

First, an overview of the rolling equipment equipped with the rolling mill of this embodiment will be described with reference to Figures 1 to 3. Figure 1 is a diagram showing an overview of the rolling equipment equipped with the rolling mill of this embodiment 1, Figure 2 is a front view explaining the overview of the rolling mill, and Figure 3 is a view taken along the line A-A' in Figure 2.

As shown in FIG. 1, the rolling equipment 1 is equipped with multiple rolling mills that hot roll the rolled material 5 into strips, and has a control device 80 and five stands, from the entry side of the rolled material 5, namely, a first stand 30, a second stand 40, a third stand 50, a fourth stand 60, and a fifth stand 70.

Of these, the first stand 30, the second stand 40, the third stand 50, the fourth stand 60, and the fifth stand 70, and the part of the control device 80 that controls each stand, correspond to the rolling mill as referred to in the present invention.

The rolling equipment 1 is not limited to multiple stands such as the five stands shown in FIG. 1, and may be a single stand. In addition, since there is no restriction on the temperature of the rolled material during rolling, it may be a rolling equipment that performs cold rolling.

Next, a part of the outline of the rolling mill of the present invention will be explained using FIG. 2. Note that in FIG. 2 and subsequent figures, the fifth stand 70 shown in FIG. 1 will be explained as an example, but the rolling mill of the present invention can be applied to any of the first stand 30, second stand 40, third stand 50, and fourth stand 60 shown in FIG. 1.

In FIG. 2, the fifth stand 70, which is the rolling mill of this embodiment, is a six-stage rolling mill that rolls the rolled material 5, and has a housing 700, a control device 80, and a hydraulic device 90.

The housing 700 is provided with an upper work roll 710, a lower work roll 711, an upper intermediate roll 720 and a lower intermediate roll 721 that support the upper work roll 710 and the lower work roll 711 by contacting them, respectively. It also is provided with an upper backing roll 730 and a lower backing roll 731 that support the upper intermediate roll 720 and the lower intermediate roll 721 by contacting them, respectively.

Among these, the "mill roll" in the present invention corresponds to any of the upper work roll 710, lower work roll 711, upper intermediate roll 720, lower intermediate roll 721, upper backup roll 730, and lower backup roll 731 described above. In the case of a rolling mill that does not have an intermediate roll such as the first stand 30 or the second stand 40, the upper and lower work rolls and the upper and lower backup rolls correspond to the "mill roll".

Of these rolls, the axial end of the upper work roll 710 is provided on the operating side with a radial bearing 790A (see FIG. 7) that shifts in the axial direction of the roll together with the upper work roll 710 and receives the load from the roll, and this radial bearing 790A is supported by an upper operating side bearing box 712A. Similarly, on the driving side, a radial bearing 790B (see FIG. 7) is provided that shifts in the axial direction of the roll together with the upper work roll 710 and receives the load from the roll, and this radial bearing 790B is supported by an upper driving side bearing box 712B. Here, the operating side radial bearing 790A and the driving side radial bearing 790B are configured to support not only the roll bending force acting in the vertical direction but also the thrust force acting in the roll axial direction.

The lower work roll 711 also has bearings (not shown for convenience of illustration) 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 (bearing box 713A on the operation side, and bearing box 713B on the drive side).

In this embodiment, the upper work roll 710 is configured to be shiftable in the roll axis direction by a shift cylinder 715 as shown in FIG. 3 via an upper operating side bearing housing 712A on the operating side and an upper driving side bearing housing 712B on the driving side. Similarly, the lower work roll 711 is configured to be shiftable in the roll axis direction by a shift cylinder 717 as shown in FIG. 3 via a bearing housing 713A on the operating side and a bearing housing 713B on the driving side.

Also, as shown in FIG. 3, the upper work roll 710 and the lower intermediate roll 721 have tapered portions at their operating side ends, and the lower work roll 711 and the upper intermediate roll 720 have tapered portions at their driving side ends. The upper work roll 710 and the lower work roll 711 are point-symmetrical from top to bottom, and the upper intermediate roll 720 and the lower intermediate roll 721 are point-symmetrical from top to bottom.

Returning to FIG. 2, the entry side fixed member 702 is fixed to the housing 700 on the entry side of the rolled material 5. An exit side fixed member 703 is fixed to the housing 700 on the exit side of the rolled material 5 so as to face the entry side fixed member 702.

In the fifth stand 70, as shown in FIG. 2, on both the operating side and the driving side, the upper work roll bearing box 712 is supported by two upper work roll bending cylinders 740, 742 provided in the axial direction of the roll of the entry side fixed member 702, and two upper work roll bending cylinders 741, 743 provided in the axial direction of the roll of the exit side fixed member 703.

Then, by driving these cylinders appropriately, a bending force is applied vertically to the bearings of the upper work roll 710.

Similarly, on both the operating side and the driving side, the lower work roll bearing housing 713 is supported by lower work roll bending cylinders 744, 746 provided on the entry side fixed member 702 and lower work roll bending cylinders 745, 747 provided on the exit side fixed member 703, and by appropriately driving these cylinders, a bending force is applied vertically to the bearing of the lower work roll 711.

Of these cylinders, the upper work roll bending cylinders 740, 741 are arranged to apply a bending force to the bearing of the upper work roll 710 that contacts the rolled material 5 in the vertical increase side (toward the opposite side of the rolled material). In addition, the upper work roll bending cylinders 742, 743 are arranged to apply a bending force to the bearing in the vertical decrease side (toward the rolled material), which is the opposite direction to the upper work roll bending cylinders 740, 741.

Similarly, the lower work roll bending cylinders 744, 745 are arranged to apply a bending force to the bearing of the lower work roll 711 that contacts the rolled material 5 in the vertical increase direction. In addition, the lower work roll bending cylinders 746, 747 are arranged to apply a bending force to the bearing in the decrease direction, which is the opposite direction to the lower work roll bending cylinders 744, 745.

Furthermore, as shown in FIG. 2, for the purpose of removing backlash, two upper work roll bearing box backlash removing cylinders 760 are provided in the axial direction of the roll on the inlet fixed member 702 on the inlet side of the rolling material 5 so as to apply a horizontal force, specifically a pressing force in the rolling direction, to the upper work roll 710 via the liner (not shown) of the upper work roll bearing box 712.

Similarly, the entry side fixed member 702 is provided with two lower work roll bearing housing clearance cylinders 762 so as to apply a pressing force in the rolling direction to the lower work roll 711 via the liner of the lower work roll bearing housing 713.

These cylinders allow the desired force to be applied to the upper work roll 710, etc. in a direction perpendicular to the roll axis direction.

Furthermore, as shown in FIG. 2, a hydraulic cylinder 705A may be provided on both the drive side and the operation side of the exit side of the housing 700 as a horizontal actuator for adjusting the angle of the upper work roll 710 in the horizontal direction.

Similarly, a hydraulic cylinder 705B may be provided on both the drive side and the operation side of the exit side of the housing 700 as a horizontal actuator for adjusting the angle of the lower work roll 711 in the horizontal direction.

Furthermore, hydraulic cylinders 705E, 705F may be provided on both the drive side and operation side of the exit side of the housing 700, and hydraulic cylinders 706C, 706D may be provided on both the drive side and operation side of the entry side of the housing 700, as horizontal actuators for adjusting the horizontal angles of the upper intermediate roll 720, the lower intermediate roll 721, the upper backing roll 730, and the lower backing roll 731.

These hydraulic cylinders 705A, 705B, 705E, 705F, 706C, and 706D as horizontal actuators are not limited to hydraulic cylinders, and can be other configurations such as worm gears.

Bearings (not shown) are provided at the axial ends of the upper intermediate roll 720 on both the drive side and the operation side, and these bearings are supported by an upper intermediate roll bearing box 722. Similarly, bearings (not shown) are provided at the axial ends of the lower intermediate roll 721 on both the drive side and the operation side, and these bearings are supported by a lower intermediate roll bearing box 723.

On both the operating side and the driving side, the upper intermediate roll 720 supports the upper intermediate roll bearing box 722 with an upper intermediate roll bending cylinder 750 provided on the entry side fixed member 702 and an upper intermediate roll bending cylinder 751 provided on the exit side fixed member 703, and by appropriately driving these cylinders, a bending force is applied to the bearing in the vertical increase direction.

The lower intermediate roll 721, on both the operating side and the driving side, supports the lower intermediate roll bearing box 723 with a lower intermediate roll bending cylinder 752 provided on the entry side fixed member 702 and a lower intermediate roll bending cylinder 753 provided on the exit side fixed member 703, and by appropriately driving these cylinders, a bending force is applied to the bearing in the vertical increase direction.

Also, as shown in FIG. 2, the exit housing 700 is provided with an upper intermediate roll bearing box clearance cylinder 771 so as to apply a horizontal force to the upper intermediate roll 720 via the upper intermediate roll bearing box 722. Similarly, the exit housing 700 is provided with a lower intermediate roll bearing box clearance cylinder 773 so as to apply a horizontal force to the lower intermediate roll 721 via the lower intermediate roll bearing box 723.

Furthermore, bearings (not shown) are provided at the axial end of the upper backup roll 730 on both the drive side and the operation side, and these bearings are supported by an upper backup roll bearing box 732. Similarly, bearings (not shown) are provided at the axial end of the lower backup roll 731 on both the drive side and the operation side, and these bearings are supported by a lower backup roll bearing box 733.

Also, as shown in FIG. 2, the entry housing 700 is provided with an upper backup roll bearing box clearance cylinder 780 so as to apply a horizontal force to the upper backup roll 730 via the upper backup roll bearing box 732. Similarly, the entry housing 700 is provided with a lower backup roll bearing box clearance cylinder 782 so as to apply a horizontal force to the lower backup roll 731 via the lower backup roll bearing box 733.

The hydraulic device 90 is connected to each hydraulic cylinder, such as the above-mentioned bending cylinders, the clearance removing cylinders, the shift cylinders 715, 717, the hydraulic cylinders 705A, 705B, 705E, 705F, 706C, 706D, and the rolling cylinders (not shown) that apply a rolling force to the upper work roll 710 and the lower work roll 711 to roll the rolled material 5, and this hydraulic device 90 is connected to the control device 80.

The control device 80 controls the operation of the hydraulic device 90, and controls the drive of each of the bending cylinders described above by supplying and discharging pressurized oil to those cylinders. As a result, the control device 80 is configured to be able to drive the drive side exit shift cylinder 715C (see FIG. 7) and the operation side exit shift cylinder 715B (see FIG. 7), for example, to shift the upper work roll 710 in the axial direction.

Next, the characteristic parts of the rolling mill and rolling method of the present invention will be described with reference to Figures 4 to 6, taking as an example the configuration related to the upper work roll 710 among the rolls of the fifth stand 70. Note that the lower work roll 711, upper intermediate roll 720, lower intermediate roll 721, upper back-up roll 730, and lower back-up roll 731, as well as the work rolls, intermediate rolls, and back-up rolls of other stands, can have the same configuration and method, and since the detailed configurations are approximately the same, a description will be omitted.

First, the problem of the present invention will be explained using Figures 4 to 6. Figures 4 to 6 are schematic diagrams that explain the problem of the present invention.

In Figure 4, the solenoid switching valve 810 is energized at b to shift toward the drive side, and then the solenoid switching valve is returned to the neutral position, the pilot check valve is closed, and the shift operation toward the drive side is stopped.

To make the explanation easier, the roll set 710A including the upper work roll 710 is shown in a simplified, integrated form. The shift cylinders are installed on the entry side and the exit side, but since the entry side of the rolling material 5 has substantially the same configuration as the exit side, only the driving side exit shift cylinder 515C and the operating side exit shift cylinder 515B are shown here as examples.

As shown in FIG. 4, the axial position of the roll set 710A is supported on the drive side by the drive side output shift cylinder 515C via the drive side arm 714C, and on the drive side by the operation side output shift cylinder 515B via the operation side arm 714B.

The driving side output shift cylinder 515C is a single-rod type cylinder and includes a driving side output plate side hydraulic oil chamber 523a on the rod side, a driving side output opposite plate side hydraulic oil chamber 523b on the head side, a rod 523c, and a piston 523d.

The operating side output shift cylinder 515B is also a single-rod type cylinder, and is equipped with an operating side output plate side hydraulic oil chamber 525a on the rod side, an operating side output opposite plate side hydraulic oil chamber 525b on the head side, a rod 525c, and a piston 525d.

In the hydraulic circuit shown in FIG. 4, a pilot check valve 821 and a relief valve 811 are provided on the pressure line 803, and a pilot check valve 822 and a relief valve 812 are provided on the pressure line 804.

The pressure line 803 branches into a drive side opposite plate side pressure line 505 and an operation side plate side pressure line 506 on the cylinder side of the pilot check valve 821. The drive side opposite plate side pressure line 505 is connected to the drive side outlet side opposite plate side hydraulic oil chamber 523b, and the operation side plate side pressure line 506 is connected to the operation side outlet side plate side hydraulic oil chamber 525a.

The pressure line 804 branches into a drive side plate side pressure line 507 and an operating side opposite plate side pressure line 508 on the cylinder side of the pilot check valve 822. The drive side plate side pressure line 507 is connected to the drive side outlet plate side hydraulic oil chamber 523a, and the operating side opposite plate side pressure line 508 is connected to the operating side outlet opposite plate side hydraulic oil chamber 525b.

4, when the roll set 710A is shifted to the driving side, the thrust resistance force _Ht acting from the roll set 710A to the driving side output shift cylinder 515C and the operation side output shift cylinder 515B is expressed as _{Ht = Hd + Hw} , where _Hw is the force acting on the operation side and _Hd is the force acting on the driving side.

The operating side outlet side opposite plate side hydraulic oil chamber 525b, which is the head side of the operating side outlet shift cylinder 515B, and the driving side outlet plate side hydraulic oil chamber 523a, which is the rod side of the driving side outlet shift cylinder 515C, are connected by the driving side plate side pressure line 507 and the operating side opposite plate side pressure line 508, so that the pressures _pdr , _pwh of each hydraulic oil chamber are equal.

However, since there is an area difference between the cross-sectional area _Awh of piston 525d which receives pressure on the head side of operating side exit shift cylinder 515B and the cross-sectional area _Adr of piston 523d which receives pressure on the rod side of driving side exit shift cylinder 515C, the output Fw of operating side exit shift cylinder 515B is greater than the output Fd of driving side exit shift cylinder 515C and the thrust resistance forces acting from roll set 710A to the shift cylinder have a relationship of _Hw > _Hd , with the thrust resistance force _Hw acting on operating side arm 714B being a greater value.

In this configuration, consider the case where roll set 710A moves to the drive side on its own. Figure 5 shows the moment when roll set 710A moves to the drive side on its own after the shift position of roll set 710A is determined, pilot check valves 821 and 822 are closed, and the shift operation is stopped, and then roll set 710A first hits drive side arm 714C.

On the operating side, there is residual play in the operating side arm 714B. In actual equipment, the play on the drive side and the operating side will never be exactly the same, so the remaining play will never be zero.

Figure 6 shows the state when roll set 710A has moved further toward the driving side from Figure 5, the remaining backlash on the operating side has become zero, and the movement of roll set 710A toward the driving side has stopped.

Here, the area _Adr of the driving side outlet plate side hydraulic oil chamber 523a of the driving side outlet shift cylinder 515C, the area Adh of the driving side outlet opposite plate side hydraulic oil chamber 523b, the area _Awr of the operating side outlet plate side hydraulic oil chamber 525a of the operating side outlet shift cylinder 515B, and the _{area Awh of} the operating side outlet opposite plate side hydraulic oil chamber 525b are shown to be in the relationship _Awh = _2Awr and _Adh = _2Adr .

When it first hits the driving side arm 714C, the driving side exit shift cylinder 515C is pushed by the thrust resistance of the roll set 710A and the pressure of _pdh is generated. _pwr tries to become the same pressure as _pdh . And, since _Awr = _Awh /2, _pwh = _pwr /2 and _pdr = _pwh = _pwr /2 = _pdh /2.

Here, since the relationship is A _dh ×p _dh =H _d +A _dr ×p _dr , by substituting the above relationship,
A _dh × p _dh = H _d + (A _dh / 2) × (p _dh / 2)
This equation gives _Hd = _Adh x _pdh x 3/4. In other words, since pressure is also exerted on the rod side of the driving side output shift cylinder 515C, it can only support up to 3/4 of the pushing force on the head side of the driving side output shift cylinder 515C.

Then, when the driving side output shift cylinder 515C is pushed by _Hd and loses, the driving side output shift cylinder 515C is pushed and moves by 1.

When the driving side output shift cylinder 515C is pushed by _Hd and moves towards the driving side, the operating side arm 714B moves towards the operating side so as to reduce the remaining backlash.

If the driving side outlet shift cylinder 515C moves by 1 to the driving side, hydraulic oil flows from the driving side outlet opposite plate hydraulic oil chamber 523b of the driving side outlet shift cylinder 515C to the operating side outlet plate hydraulic oil chamber 525a of the operating side outlet shift cylinder 515B. Therefore, the piston 525d of the operating side outlet shift cylinder 515B wants to move by 2 to the operating side outlet opposite plate hydraulic oil chamber 525b side, but because the operating side outlet opposite plate hydraulic oil chamber 525b side can support the pushing force from the operating side outlet plate hydraulic oil chamber 525a side with half the pressure of the operating side outlet plate hydraulic oil chamber 525a side due to the area difference, the operating side outlet opposite plate hydraulic oil chamber 525b side can only move 1/2 corresponding to the movement 1 of the driving side outlet plate hydraulic oil chamber 523a side. Therefore, the operating side outlet plate hydraulic oil chamber 525a side cannot move by 2 and only moves 1/2. Therefore, the hydraulic oil equivalent to (2-1/2) on the operating side outlet plate side hydraulic oil chamber 525a flows out from the relief valve 811.

Specifically, if the driving side output shift cylinder 515C moves 1 toward the driving side, the operating side output shift cylinder 515B moves 1/2 toward the operating side. This makes the remaining backlash 0. Therefore, the driving side arm 714C moves toward the driving side by 2/3 of the remaining backlash, and the operating side arm 714B moves toward the operating side by 1/3 of the remaining backlash.

Also, when driving side output shift cylinder 515C is pushed by _Hd and moves 1 in the driving side direction, the rod side of driving side output shift cylinder 515C also moves 1, so the head side of operating side output shift cylinder 515B moves 1/2 the area ratio, and the rod side of operating side output shift cylinder 515B also moves 1/2. Therefore, the amount of hydraulic oil A _dh × 1 - A _wr × 1/2 = A _dh × 3/4 is released from relief valve 811. Then, when driving side arm 714C has moved 2/3 of the remaining backlash and operating side arm 714B has moved 1/3 of the remaining backlash, driving side output shift cylinder 515C and operating side output shift cylinder 515B stop.

The operating side arm 714B moves in the operating side direction by 1/3 of the remaining play, causing the position sensor 716 to move by 1/3 of the remaining play.

The remaining play is the difference between the play on the operating side and the play on the drive side, and if the remaining play is about 1 mm, the position sensor 716 will move about 1 mm x 1/3 = 0.3 mm toward the operating side.

As described above, when roll set 710A is moved toward the driving side while receiving thrust resistance from roll set 710A toward the operating side, and the position of roll set 710A is set, if a thrust resistance in the driving side direction acts on roll set 710A due to a change in conditions such as the rotation of the rolls of the rolling mill, causing only roll set 710A to move toward the driving side, the pressure will rise above the set pressure (maximum pressure) of relief valves 811, 812 before the thrust resistance is supported by both the driving side and the operating side, causing hydraulic oil to leak out of relief valves 811, 812.

In other words, when the drive side alone can support the load, it will do so, but only when the drive side loses will both the drive side and the operating side support the load, and in that case the pressure will exceed the maximum pressure while the hydraulic oil is leaking out of the relief valves 811 and 812.

Therefore, there are problems in that both sides cannot support the pressure until it reaches the set pressure of the relief valves 811 and 812, and when both sides support the pressure, it will exceed the set pressure (maximum pressure).

Furthermore, the shift position of the roll set 710A becomes misaligned, so the shift position needs to be adjusted frequently.

The above shows the case where the driving side arm 714C hits first, leaving the remaining backlash on the operating side, but the same problem occurs when the operating side arm 714B hits first, leaving the remaining backlash on the driving side.

The above explanation has shown the problem that occurs when the direction of the thrust resistance force changes, but when the length of roll set 710A changes due to thermal expansion, the same problem occurs because the same condition occurs as when residual backlash occurs on one side.

Next, the characteristic configuration of this embodiment that can solve these problems will be explained using Figures 7 to 9. Figures 7 to 9 are plan views that explain the details of the upper work roll part of the rolling mill.

As shown in FIG. 7, the entry fixed member 702 on the operation side is provided with an entry shift cylinder 715A on the operation side that applies force to the upper work roll 710 in both the operation side and drive side directions via an operation side arm 714A connected to an upper operation side bearing housing 712A that supports the radial bearing 790A on the operation side.

Furthermore, the operation side exit fixed member 703 is provided with an operation side exit shift cylinder 715B that applies force to the upper work roll 710 in both the operation side and drive side directions via an operation side arm 714B connected to an upper operation side bearing housing 712A that supports the operation side radial bearing 790A.

A position sensor 716 is provided in the operating side exit shift cylinder 715B to detect the position of the upper work roll 710 in the roll axis direction. Note that the position sensor 716 may be provided at any of the other operating side entry shift cylinders 715A and driving side shift cylinders 715C and 715D. Also, it does not have to be one, and two or more may be provided.

Similarly, the drive-side entry fixed member 702 is provided with a drive-side entry shift cylinder 715D that applies force to the upper work roll 710 in both the operating side and drive side directions via a drive-side arm 714D connected to an upper drive-side bearing housing 712B that supports the drive-side radial bearing 790B.

In addition, the drive-side exit fixed member 703 is provided with a drive-side exit shift cylinder 715C that applies force to the upper work roll 710 in both the operating side and drive side directions via a drive-side arm 714C connected to an upper drive-side bearing housing 712B that supports the drive-side radial bearing 790B.

The operating side radial bearing 790A is further subjected to an axial force acting on the upper work roll 710, and is ultimately supported by the operating side shift cylinders 715A and 715B. Similarly, the driving side radial bearing 790B is subjected to an axial force acting on the upper work roll 710, but this force is supported by the driving side shift cylinders 715C and 715D.

Because the axial force acting on the work roll 710 is sometimes in the operating side direction and sometimes in the driving side direction, both the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D can support forces in both the operating side direction and the driving side direction.

All of these operating side entry shift cylinder 715A, operating side exit shift cylinder 715B, driving side exit shift cylinder 715C, and driving side entry shift cylinder 715D are double-rod cylinders in which the internal pistons 923d, 925d (only the exit side is shown in each case) have two rods 923c, 925c (only the exit side is shown in each case).

In addition, this embodiment is equipped with a hydraulic circuit that sends hydraulic oil to multiple hydraulic cylinders, moving the driving side shift cylinders 715C, 715D and the operating side shift cylinders 715A, 715B in the axial direction and maintaining the axial position of the upper work roll 710.

In this hydraulic circuit, after the hydraulic circuit has held the axial position of the upper work roll 710, if an external force received by the upper work roll 710 causes only one of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B to apply an axial force to the upper work roll 710, the other of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B will move in the opposite direction to the other hydraulic cylinder.

In addition, pressure lines 805, 806, 807, and 808 are provided to connect each corresponding hydraulic oil chamber on the inlet and outlet sides. For example, the hydraulic circuit is such that the driving side outlet plate side hydraulic oil chamber 923a, the driving side inlet plate side hydraulic oil chamber 924a, the operating side outlet opposite plate side hydraulic oil chamber 925b, and the operating side inlet opposite plate side hydraulic oil chamber 926b are connected by the driving side plate side pressure line 807 and the operating side opposite plate side pressure line 808, and the driving side outlet opposite plate side hydraulic oil chamber 923b, the driving side inlet opposite plate side hydraulic oil chamber 924b, the operating side outlet plate side hydraulic oil chamber 925a, and the operating side inlet plate side hydraulic oil chamber 926a are connected by the driving side opposite plate side pressure line 805 and the operating side plate side pressure line 806.

As a result, when the direction of an external force changes, or when the distance between the supports on the supported side and the supporting side changes due to thermal expansion of a mechanical device, when either the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B moves a specified stroke, the hydraulic circuit is configured so that the other hydraulic cylinder of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B also moves the same specified stroke in the opposite direction without changing the amount of oil in the connected pressure lines 805, 806, 807, 808.

A radial bearing 790A is arranged in the upper operating side bearing box 712A. A radial bearing 790B is arranged in the upper driving side bearing box 712B.

The forces of the upper work roll bending cylinders 740, 741 and the upper work roll bearing box clearance cylinder 760 act on the radial bearings 790A, 790B. These radial bearings 790A, 790B support these vertical forces acting on the roll axis while rotating.

Furthermore, because radial bearings 790A, 790B also support the axial force acting on upper operation side bearing housing 712A and upper drive side bearing housing 712B, four-row tapered roller bearings are generally used. Also, bearings of the same specifications are used for drive side radial bearing 790B and operation side radial bearing 790A, which can be made to avoid complicated maintenance work.

In the drive system of the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D, there are provided pressure line 801 branching off from pressure line 800A through which pressurized oil discharged from a pump (not shown) of the hydraulic device 90 flows, and solenoid switching valve 810 for adjusting the amount of oil flowing in and out is provided on the outlet side of tank line 802 branching off from tank line 800B connected to a tank (not shown) in which the pressurized oil is stored.

When the solenoid switching valve 810 is energized, the rod side (operating side outlet plate side hydraulic oil chamber 925a side) of the operating side shift cylinders 715A, 715B close to the plate is connected to pressure lines 801, 800A via the operating side plate side pressure line 806 and pressure line 803, and a force in the operating side direction acts on the upper operating side bearing housing 712A.

In addition, the rod side of the driving side shift cylinders 715C, 715D closer to the opposite plate (the driving side outlet side opposite plate side hydraulic oil chamber 923b side) is also connected to pressure lines 801, 800A via driving side opposite plate side pressure line 805 and pressure line 803, and a force in the operating side direction acts on the upper driving side bearing housing 712B.

Furthermore, the rod side of the operating side shift cylinders 715A, 715B facing away from the plate (the operating side outlet side opposite plate side hydraulic oil chamber 925b side) and the rod side of the driving side shift cylinders 715C, 715D facing away from the plate (the driving side outlet side plate side hydraulic oil chamber 923a side) are connected to the tank lines 802, 800B via the operating side opposite plate side pressure line 808 or the driving side plate side pressure line 807 and pressure line 804, respectively, so that both the operating side and driving side shift cylinders generate a shift force towards the operating side.

When the solenoid switching valve 810 is energized, the rod side of the operating side shift cylinders 715A, 715B closest to the plate (the operating side outlet side hydraulic oil chamber 925b side) is connected to the pressure lines 801, 800A via the operating side opposite plate side pressure line 808 and pressure line 804, and a force in the drive side direction acts on the upper operating side bearing housing 712A.

In addition, the rod side (drive side outlet plate side hydraulic oil chamber 923a side) of the drive side shift cylinders 715C, 715D is connected to pressure lines 801, 800A via drive side plate side pressure line 807 and pressure line 804, and a force in the drive side direction acts on the upper drive side bearing box 712B.

Furthermore, the rod side closer to the plate of the operating side shift cylinders 715A, 715B (the operating side outlet plate side hydraulic oil chamber 925a side) and the rod side closer to the opposite plate of the driving side shift cylinders 715C, 715D (the driving side outlet opposite plate side hydraulic oil chamber 923b side) are connected to the tank lines 802, 800B via the operating side plate side pressure line 806 or the driving side opposite plate side pressure line 805 and pressure line 803, respectively, so that both the operating side and driving side shift cylinders generate a shift force towards the driving side.

When the solenoid switching valve 810 is in neutral, the pilot check valves 821, 822 prevent hydraulic oil from flowing to either the rod side closest to the plate or the rod side opposite the plate of the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D.

The configuration of these solenoid switching valves 810 and excitation control by the control device 80 allow the operating side shift cylinders 715A, 715B and driving side shift cylinders 715C, 715D to support the upper work roll 710 so that it does not move in the axial direction when the axial shift of the upper work roll 710 is stopped.

A pilot check valve 822 is provided in the pressure line 804 downstream of the solenoid switching valve 810, and a pilot check valve 821 is provided in the pressure line 803 downstream of the solenoid switching valve 810, and this prevents pressure oil from flowing to both the rod and head sides of the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D when the solenoid switching valve 810 is in neutral. This allows the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D to support the upper work roll 710 so that it does not move in the axial direction, even when the shifting of the upper work roll 710 is stopped.

Furthermore, in consideration of emergencies such as the application of unexpected excessive thrust resistance, relief valves 811, 812 are provided between the pilot check valves 821, 822 and the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D to keep the pressure rise in the piping at the allowable pressure of the machine.

Note that the hydraulic system in Figure 7 only shows the portion that explains the present invention, and flow control valves, check valves, etc. can be added as necessary.

Figure 8 shows the structure around the inlet side shift cylinders on the operating side and drive side. In order to explain the operation, Figure 8 only explains the case where the piping on the rod side closest to the plate on the operating side and the rod side closest to the opposite plate on the drive side are connected, but the same can be said for other piping connections.

8, the center position of the distance between the support positions on the operating side and the drive side is indicated by line M, _Fsde is the force with which the drive side entry shift cylinder 715D supports the upper drive side bearing housing 712B, _Fswe is the force with which the operating side entry shift cylinder 715A supports the upper operating side bearing housing 712A, _La is the distance between the support positions on the operating side and the drive side, and _Ftr is the thrust force acting on the upper work roll 710. Here, it is assumed that a thrust force is acting in the operating side direction.

In the state of FIG. 8, _Fswe and _Fsde are each _Ftr /4, and although not shown, the force _Fswd with which the output side operating side shift cylinder 715B supports the upper operating side bearing housing 712A and the force _Fsdd with which the drive side output shift cylinder 715C supports the upper drive side bearing housing 712B are also _Ftr /4, and the sum of these four is _Ftr , which supports the thrust force _Ftr .

In Figure 9, it is assumed that during rolling, the upper work roll 710 is heated by the rolling material 5, the radial bearings 790A, 790B generate heat as they rotate under load, and the distance La between the support positions on the operating side and the driving side is extended by ΔLa due to changes in the surrounding temperature, etc.

As shown in Figure 9, when the distance La between the support positions on the operating side and the driving side changes by ΔLa, the support position on the driving side moves by ΔLa/2 toward the opposite side to the plate, hydraulic oil flows from the opposite side to the plate of the driving side shift cylinders 715C, 715D to the plate side of the operating side shift cylinders 715A, 715B, and the support position on the operating side moves by ΔLa/2 toward the opposite side to the plate.

In other words, in the hydraulic circuit of this embodiment, even if the distance La between the support positions on the operating side and the driving side changes by ΔLa, the amount of oil in the pressure lines 805, 806, 807, and 808 on the outlet side of the pilot check valves 821 and 822 does not change, so the support force of the upper work roll 710 by the operating side shift cylinders 715A and 715B and the support force of the upper work roll 710 by the driving side shift cylinders 715C and 715D can be maintained in the same state, and the balance of the total support force does not change.

Therefore, line M, which is the center position of the distance between the support positions on the operating side and the driving side, remains at the center position of the distance between the support positions on the operating side and the driving side even if La changes by ΔLa. In other words, since line M is close to the center position of the rolling material 5, even if there is thermal expansion, there is only a very small amount of axial slippage between the upper work roll 710 and the rolling material 5, and rolling is not hindered.

Here we show the case where thermal expansion occurs, but if thermal contraction occurs, the supporting force will not change and the position of line M will not change either.

Next, a modified version of this embodiment will be described with reference to FIG. 10. FIG. 10 is a plan view illustrating the details of the upper work roll portion of a rolling mill that is a modified version of embodiment 1.

FIG. 10 shows an example of a configuration in which a shift block 712A1 containing upper work roll bending cylinders 740, 741 is connected to operating side shift cylinders 715A, 715B on the operating side, and a shift block 712B1 containing upper work roll bending cylinders 740, 741 is connected to driving side shift cylinders 715C, 715D on the driving side.

When using such shift blocks 712A1, 712B1, the thrust reaction force can be made the same on the operating side and the driving side, just as in the case of the configuration shown in Figure 7, in which the entry side fixed member 702 and the exit side fixed member 703 have bending cylinders 740, 741 built in.

In addition, by adopting the configuration shown in FIG. 7 and further providing a pressure measuring device on the secondary side of pilot check valves 821 and 822, it becomes possible to measure the thrust force acting on the roll with high accuracy.

Next, we will explain the effects of this embodiment.

　According to the rolling mill of the first embodiment of the present invention described above, after the hydraulic circuit has held the axial position of the upper work roll 710, if an external force received by the upper work roll 710 causes only one of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B to apply an axial force to the upper work roll 710, the other of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B is configured to move in the opposite direction to the other hydraulic cylinder.

When the direction of the axial external force acting on the mill roll changes after the axial position of the mill roll is maintained, even if the backlash of one of the operating hydraulic cylinder and the driving hydraulic cylinder disappears first, when one hydraulic cylinder is pushed and no longer supported and moves, the other hydraulic cylinder moves the same amount in the opposite direction to the one hydraulic cylinder. This action is continuously repeated until the remaining backlash disappears and the other hydraulic cylinder also begins to support the other hydraulic cylinder, preventing a large axial external force from continuing to act on one hydraulic cylinder until the backlash of the other hydraulic cylinder disappears.

That is, even if thermal expansion occurs, the direction of thrust resistance force changes, or gaps exist in the axial direction of the roll between the bearing housing and the bearing, inside the bearing, between the bearing and the roll, between the bearing housing and the shift device, etc., the thrust reaction force of the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D can be made the same as long as no excessive thrust resistance force acts, and the pressure in the hydraulic cylinders can be prevented from increasing to the set pressure of the relief valves 811, 812 or higher. Therefore, excessive load is not applied to the support parts such as the operating side bearing and the driving side bearing of the mill roll, and the life can be improved. For example, if the life of the bearing is Lh and the load is Pl, in the case of a roller bearing, there is a relationship of Lh ∝ (1/Pl) ^10/3 , so if 1/2 is added to Pl, Lh = 10, and the life of the bearing can be extended by 10 times compared to the case where the thrust force is held on one side.

In addition, in the conventional configuration, when the pressure is increased above the relief valve set pressure, hydraulic oil flows out from the secondary side of the pilot check valve, causing a shift position shift, and therefore requiring frequent adjustment of the shift position. However, in the configuration of this embodiment, the pressure increase above the set pressure of the relief valves 811, 812 can be suppressed, so frequent adjustment of the shift position is not required. In other words, there is no need for a complex pressure measurement device or adjustment of the inflow and outflow oil amount adjustment unit as in the conventional configuration, and a simple device configuration can be achieved. In addition, since this can be achieved without a complex control device, by only controlling the ON/OFF of the solenoid switching valve 810, the device configuration of the control system can also be simplified.

For example, in the case of Patent Document 1 mentioned above, the thrust force may be supported on one side or on both sides, and the state of support of the thrust force may change before and after the relief valve is actuated. In addition, the operating pressure of the relief valve affects the pressure on the secondary side of the pilot check valve, but since the operating pressure of the relief valve changes depending on the flow rate, it may be difficult to determine from the pressure measurement results on the secondary side of the pilot check valve whether the thrust force is supported on one side or on both sides. Therefore, even if a pressure measuring device is installed on the secondary side of the pilot check valve and the pressure is measured, the thrust force is calculated by multiplying the areas of both pressure chambers of the cylinder, and it was found that if it remains uncertain whether the thrust force is supported by one side or both sides of the cylinder, it may be difficult to accurately calculate the thrust force.

However, in the configuration of this embodiment, the thrust force can always be supported on both sides, even when an abnormal thrust force acts and causes the relief valves 811, 812 to operate, so the thrust force can be accurately determined from the pressure measurement results on the secondary side of the pilot check valves 821, 822.

In addition, rolling mills in which the upper and lower rolls are inclined in opposite directions to create a crossed state have high plate crown/plate shape control capabilities, but because a large thrust force acts between the rolled material 5 and the upper work roll 710, there are limits to the load capacity due to the strength of the bearings and roll ends that receive the thrust force.

In particular, when the load conditions are severe, grease cannot be used to lubricate the bearings and it becomes necessary to use oil lubrication such as circulating oil supply. However, using oil lubrication such as circulating oil supply requires complex equipment and high equipment costs.

In contrast, by adopting the configuration of this embodiment described above, if the applied load can be halved, simple grease lubrication can be used as mechanical equipment, which has the advantage of keeping equipment costs and operating costs low. In addition, if the applied load can be halved, the diameter of the upper work roll 710 can be reduced, which leads to a reduction in the rolling load, making it applicable to rolling of hard materials.

The above explanation has been about the case where the bearing receives both bending and thrust forces, but there are also cases where a radial bearing that receives bending forces and a thrust bearing that receives thrust forces are provided separately. The structure of the bearings can be selected appropriately, and even in such structures, the load acting on them can be halved by adopting the configuration of this embodiment, which leads to an extension of the life of the roll support parts such as the bearings.

Furthermore, the vertical resistance of the thrust receiving part affects the rolling load measurement value. If there is a thrust force support device on only one side, it can also cause a differential load. By adopting the configuration of this embodiment, the thrust force can be made the same on the operating side and the driving side, so the differential load can be minimized, although this depends on the friction coefficient of the thrust receiving part.

As a result, by adopting the configuration of this embodiment, it is possible to create a structure that reduces the movement resistance of the thrust receiving part in the rolling direction. This makes it possible to reduce the resistance when changing the inclination during rolling.

In addition, the hydraulic circuit is configured so that the driving side exit plate side hydraulic oil chamber 923a and the operating side exit opposite plate side hydraulic oil chamber 925b are connected by pressure lines 807, 808, and the driving side exit opposite plate side hydraulic oil chamber 923b and the operating side exit plate side hydraulic oil chamber 925a are connected by pressure lines 805, 806, so that the driving side shift cylinders 715C, 715D and the operating side shift cylinders 715A, 715B each apply force to the upper work roll 710 in the same direction. This ensures that the amount of hydraulic oil moving through the piping does not change.

Furthermore, the hydraulic circuit is configured so that when either one of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B moves a specified stroke, the other hydraulic cylinder of the driving side shift cylinders 715C, 715D or the operating side shift cylinders 715A, 715B also moves a specified stroke in the opposite direction without changing the amount of oil in the connected pressure lines 805, 806, 807, 808. This allows the strokes of both the driving side and the operating side to be moved to be the same, the pressure in the piping does not become so high that it exceeds the set pressure of the relief valves 811, 812, and both the driving side and the operating side can apply force in the same direction to the mill roll to support the thrust force.

In addition, the driving side shift cylinders 715C, 715D and the operating side shift cylinders 715A, 715B are double rod cylinders, and the cross-sectional area in the direction in which the force of the hydraulic oil is applied is the same for the driving side outlet plate side hydraulic oil chamber 923a and the driving side outlet opposite plate side hydraulic oil chamber 923b, and the cross-sectional area in the direction in which the force of the hydraulic oil is applied is the same for the operating side outlet plate side hydraulic oil chamber 925a and the operating side outlet opposite plate side hydraulic oil chamber 925b, and the driving side outlet plate side hydraulic oil chamber 923a and the operating side outlet opposite plate side hydraulic oil chamber 925b are pressure lines. 807, 808, and the drive side outlet side opposite plate hydraulic oil chamber 923b and the operation side outlet plate side hydraulic oil chamber 925a are connected by pressure lines 805, 806, so that the force supporting the thrust force in the operation side direction acting on the mill roll can be made equal to the force supporting the thrust force in the drive side direction, and when the bearings on the operation side and drive side of the mill roll are of the same specification, the life of the support parts such as the bearings can be maximized and damage to each part due to load can be reduced. In addition, by using both rods, the bearing box connection part of the drive side hydraulic cylinder and the operation side hydraulic cylinder can be made closer to the plate, so the structure around the bearing box connection part can be made symmetrical on the drive side and the operation side, and the structure can be made common, resulting in a simpler device than other embodiments described later.

Furthermore, the driving side shift cylinders 715C, 715D and the operating side shift cylinders 715A, 715B are provided on the entry side and exit side of the rolling mill, respectively, and by providing pressure lines 805, 806, 807, 808 that connect the corresponding hydraulic oil chambers on the entry side and exit side, the support force on the entry side and exit side of the hydraulic cylinders can be made the same, so that no moment acts on the bearing housing, preventing rotation in the horizontal plane of the mill roll and equalizing the support force on the entry side and exit side of the rolled material 5 with a simple structure.

The device also includes a control device 80 that controls the operation of multiple hydraulic cylinders. The control device 80 is configured to drive the drive side shift cylinders 715C, 715D and the operation side shift cylinders 715A, 715B to shift the upper work roll 710 in the axial direction, thereby enabling automatic axial shifting of the mill roll.

Furthermore, it is equipped with a horizontal actuator that adjusts the angle of each roll horizontally. If the mill roll is tilted at an arbitrary angle relative to the plate, the thrust force acting on the mill roll increases, but this large thrust force is supported by half on the operating side and half on the driving side, making the support forces on the inlet and outlet sides equal with a simple structure, preventing moment from acting on the bearing housing, and reducing the support force per hydraulic cylinder to 1/4.

In addition, it is possible to use a single hydraulic cylinder with two rods and change the diameters of the two rods, i.e., make the cross-sectional areas of the two hydraulic oil chambers different.

In that case, the cross-sectional areas of the hydraulic oil chambers on the drive side closer to the plate and the operation side closer to the opposite plate are matched and connected with piping, and the cross-sectional areas of the drive side closer to the opposite plate and the operation side closer to the plate are matched and connected with piping. This allows the drive side closer to the opposite plate and the operation side closer to the plate, and the drive side closer to the opposite plate and the operation side closer to the opposite plate to each apply the same thrust reaction force, which can halve the thrust reaction force and make it possible to have the same supporting force on the drive side and the operation side, maximizing the life of roll support parts such as bearings.

In addition, if you want to selectively increase the force that supports the thrust force in the direction of the operating side, you can choose to provide a difference in the rod diameter so that the cross-sectional area of the hydraulic oil chamber on the operating side near the plate and the driving side near the plate is larger than the cross-sectional area of the hydraulic oil chamber on the operating side near the plate and the driving side near the plate.

Example 2
A rolling mill and a rolling method according to a second embodiment of the present invention will be described with reference to Fig. 11. Fig. 11 is a plan view for explaining the details of an upper work roll portion of the rolling mill according to the second embodiment.

In the rolling mill of this embodiment shown in Figure 11, the drive side exit shift cylinder 715C1, drive side entry shift cylinder 715D1, operation side entry shift cylinder 715A1, and operation side exit shift cylinder 715B1 are all single rod cylinders, and the single rods 923c1, 925c1 of each cylinder (only the exit side is shown in each example) are oriented in the same direction and are arranged on the operation side.

For this reason, the operating side entry shift cylinder 715A1 is connected to the operating side arm 714A and the upper operating side bearing housing 712A via a transmission member 715A2, and the operating side exit shift cylinder 715B1 is connected to the operating side arm 714B and the upper operating side bearing housing 712A via a transmission member 715B2, thereby supporting the upper work roll 710.

Furthermore, the drive side outlet plate side hydraulic oil chamber 923a1 and the operation side outlet opposite plate side hydraulic oil chamber 925b1 are connected by drive side plate side pressure lines 807A, 807B, and the cross-sectional areas in the direction in which the hydraulic oil force is applied (area of piston 923d1 and piston 925d1) are the same, and the drive side outlet opposite plate side hydraulic oil chamber 923b1 and the operation side outlet plate side hydraulic oil chamber 925a1 are connected by pressure lines 805A, 805B and operation side plate side pressure line 806, and the cross-sectional areas in the direction in which the hydraulic oil force is applied (area of piston 923d1 and piston 925d1) are the same.

　Even with this configuration, as with the configuration of FIG. 7 described in Example 1, even if there is thermal deformation of ΔLa, the driving side and the operating side can be moved to the opposite side by ΔLa/2 on each side of the line M, making it possible to support the driving side and the operating side with equal force.

In other words, roll set 710A is moved toward the drive side while receiving thrust resistance from roll set 710A toward the operation side, and after the position of roll set 710A is set, a thrust resistance in the drive side direction acts on roll set 710A due to changes in conditions such as the rotation of the rolls of the rolling mill, and when only roll set 710A moves toward the drive side, the thrust resistance is evenly supported by both the drive side and the operation side, so the pressure does not rise above the set pressure of relief valves 811, 812.

Even in this case, relief valves 811, 812 may be provided on the secondary side of pilot check valves 821, 822 to take into account emergencies such as the application of unexpected excessive thrust resistance.

The rest of the configuration and operation are substantially the same as those of the rolling mill and rolling method of the first embodiment described above, and details are omitted.

The rolling mill and rolling method of the second embodiment of the present invention also provide substantially the same effects as those of the rolling mill and rolling method of the first embodiment described above.

In addition, in this embodiment, the same hydraulic cylinder can be used on the operating side and the driving side, but the mechanical devices around the cylinder, such as the shift device, have different structures on the operating side and the driving side. This makes the equipment more complex, but the amount of protrusion of the shift device, including the shift cylinder, from the operating side housing can be made smaller than in the configuration of Example 1, so this configuration can be preferably adopted when it is difficult to make the shift device larger due to the need to accommodate a rearrangement device on the operating side, etc.

Specifically, the roll changing device on the operating side can be located close to the rolling mill, which is similar to the case where a shift cylinder is provided only on the operating side of a normal work roll shift, so there is no need to expand the space on the operating side, and space can be saved economically.

In addition, if there are space constraints on the driving side due to the device, it is also possible to make the head side of the operating side shift cylinders 715A1, 715B1 the side away from the plate, and the head side of the driving side shift cylinders 715C1, 715D1 the side closer to the plate.

The configuration of this embodiment is preferable when securing space on the operation side, regardless of whether it is hot rolling or cold rolling.

The configuration of the single rod cylinder in this embodiment is not limited to the form shown in FIG. 11, and the driving side exit shift cylinder 715C1 and the driving side entry shift cylinder 715D1 can also be configured to support the driving side arms 714C, 714D via a transmission member in the same way as the operating side entry shift cylinder 715A1 and the operating side exit shift cylinder 715B1, so that the single rod faces outward in the axial direction. In this case, an intermediate cylinder is further provided as shown in FIG. 14, which will be described later.

By positioning the shift cylinder so that the rod faces outward in this way, the rolling mill becomes more compact. Space can be secured on the operating side for roll changing, and the drive side is similarly compact, so space can be secured as well. Furthermore, because the structure on the drive side can be made symmetrical with the structure on the operating side, it is possible to standardize the structure and achieve a simple device configuration.

Example 3
A rolling mill and a rolling method according to a third embodiment of the present invention will be described with reference to Figures 12 and 13. Figures 12 and 13 are plan views for explaining the details of an upper work roll portion of the rolling mill according to the third embodiment.

In the rolling mill of this embodiment shown in Figures 12 and 13, pressure line 805B1 branching off from pressure line 803 is connected to the drive side entry side opposite plate side hydraulic oil chamber 833b of the drive side entry side shift cylinder 833 of both rods, and pressure line 805B2 branching off from pressure line 803 is connected to the operation side entry side plate side hydraulic oil chamber 830a of the operation side entry side shift cylinder 830 of both rods.

Furthermore, the driving side inlet side opposite plate hydraulic oil chamber 833b and the driving side outlet side opposite plate hydraulic oil chamber 832b of the driving side outlet shift cylinder 832 of both rods are connected by a pressure line 823, this driving side outlet side opposite plate hydraulic oil chamber 832b and the operating side outlet plate side hydraulic oil chamber 831a of the operating side outlet shift cylinder 831 of both rods are connected by a pressure line 824, and this operating side outlet plate side hydraulic oil chamber 831a and the operating side inlet plate side hydraulic oil chamber 830a are connected by a pressure line 825.

In order to explain the operation, only the case where the rod side closest to the plate on the operating side and the rod side closest to the opposite plate on the driving side are connected by piping is explained, but the rod side closest to the opposite plate on the operating side (operating side inlet opposite plate hydraulic oil chamber 830b, operating side outlet opposite plate hydraulic oil chamber 831b) and the rod side closest to the plate on the driving side (drive side inlet plate side hydraulic oil chamber 833a, drive side outlet plate side hydraulic oil chamber 832a) are also connected by piping in the same way.

In Figures 12 and 13, we also assume that a thrust force is acting in the direction of the operating side, as in Figure 8.

Fig. 13 shows a state in which the upper work roll 710 in Fig. 12 has an arbitrary inclination angle with respect to the rolled material 5. The center of the strip width at the strip passing position is set to be approximately the same position as the center of the rolling mill, and in this case, the inclination angle _θc is set counterclockwise around the center position of the rolling mill in the strip width direction.

In Fig. 13, when the pilot check valves 821, 822 are in operation during rolling and a tilt angle _θc is set, if the distance from the rolling mill center position to the thrust force acting position is the same on the operating side and the drive side, the support position on the entry side of the operating side moves toward the plate by _ΔLwe , and the support position on the delivery side of the operating side moves toward the opposite side to the plate by _ΔLwd . Furthermore, the support position on the entry side of the drive side moves toward the opposite side to the plate by _ΔLde , and the support position on the delivery side of the drive side moves toward the plate by _ΔLdd .

These movements cause hydraulic oil to move through pressure lines 805B1, 805B2, 823, 824, and 825, but the total amount of hydraulic oil on the outlet side (secondary side) of pilot check valves 821 and 822 does not change.

Since the rod side opposite the plate on the operating side and the rod side closest to the plate on the drive side are similarly connected by pressure lines, the total amount of hydraulic oil on the outlet side (secondary side) of pilot check valves 821, 822 similarly does not change.

On the other hand, the upper work roll 710 can shift to various positions, and even when it does not shift, the distance from the rolling mill center to the thrust force acting position can differ between the operating side and the driving side.

In this case, the distance between the support positions on the operating side and the driving side changes slightly due to the inclination of the upper work roll 710. In response to this change, a flow of hydraulic oil occurs between the operating side and the driving side, similar to when the distance between the support positions on the operating side and the driving side changes due to thermal expansion of the upper work roll 710 or the like. However, although the values of ΔL _we , ΔL _wd , ΔL _de , and ΔL _dd deviate slightly from the geometrically determined position of action of the thrust force due to the inclination of the upper work roll 710, there is no significant change.

In this way, in a mill that shifts work rolls, when tilting the upper work roll 710 during rolling, it is possible to tilt it without significantly changing the shift position, and without applying excessive load that would increase the pressure above the set pressure of the relief valves 811, 812 during the tilting process.

Furthermore, when tilting, there is only a slight deviation centered on the line M, so the upper work roll 710 can be tilted with almost no slippage between the rolled material 5 and the upper work roll 710.

After the shift position of the upper work roll 710 has been determined, or even if the mill does not have a shift, the axial position of the upper work roll 710 is determined using the configuration of this embodiment, no excessive force is applied to the shift device even if the inclination angle is changed during rolling or the pilot check valves 821, 822 remain in their activated state.

The deviation in the roll axis direction caused by changing the tilt angle is very small because the deviation between the center of the distance between the support positions and the center of the tilt (rolling mill center position) is small. When this very small deviation occurs, the total amount of hydraulic oil on the secondary side of the pilot check valves 821 and 822 does not change.

In addition, even in other embodiments such as that shown in FIG. 11, if the total amount of hydraulic oil on the secondary side of the pilot check valves 821, 822 does not change even if the rolls are tilted relative to the rolled material 5 during rolling, the support force of the operating side and driving side of each cylinder can be made equal.

The rest of the configuration and operation are substantially the same as those of the rolling mill and rolling method of the first embodiment described above, and details are omitted.

The rolling mill and rolling method of the third embodiment of the present invention also provide substantially the same effects as those of the rolling mill and rolling method of the first embodiment described above.

Example 4
A rolling mill and a rolling method according to a fourth embodiment of the present invention will be described with reference to Fig. 14. Fig. 14 is a plan view for explaining the details of the upper work roll portion of the rolling mill according to the fourth embodiment. Note that Fig. 14 shows only the exit side, but the entry side has a similar structure, and the details are omitted.

In the rolling mill of this embodiment shown in FIG. 14, the driving side exit shift cylinder 935C and the operating side exit shift cylinder 935B are single-rod cylinders. The rod 943c of the driving side exit shift cylinder 935C and the rod 945c of the operating side exit shift cylinder 935B are oriented in opposite directions and are each positioned on the rolling material 5 side.

Furthermore, there are two single-rod intermediate cylinders, a first intermediate cylinder 971 and a second intermediate cylinder 973. These first intermediate cylinder 971 and second intermediate cylinder 973 are dummy cylinders, and there is no particular object to be pressed.

In addition, the driving side outlet rod side hydraulic oil chamber 943a of the driving side outlet shift cylinder 935C and the rod side hydraulic oil chamber 971b of the first intermediate cylinder 971 are connected by an intermediate rod pressure line 807C2, and the driving side outlet head side hydraulic oil chamber 943b and the head side hydraulic oil chamber 973a of the second intermediate cylinder 973 are connected by an intermediate rod pressure line 805C2.

Furthermore, the operating side outlet rod side hydraulic oil chamber 945a of the operating side outlet shift cylinder 935B and the rod side hydraulic oil chamber 973b of the second intermediate cylinder 973 are connected by an intermediate rod pressure line 805C1, and the operating side outlet head side hydraulic oil chamber 945b and the head side hydraulic oil chamber 971a of the first intermediate cylinder 971 are connected by an intermediate rod pressure line 807C1.

In addition, the ratio of the cross-sectional area between the drive side outlet rod side hydraulic oil chamber 943a and the drive side outlet head side hydraulic oil chamber 943b in the direction in which the hydraulic oil force is applied, the ratio of the cross-sectional area between the operation side outlet rod side hydraulic oil chamber 945a and the operation side outlet head side hydraulic oil chamber 945b in the direction in which the hydraulic oil force is applied, the ratio of the cross-sectional area between the rod side hydraulic oil chamber 971b and the head side hydraulic oil chamber 971a in the direction in which the hydraulic oil force is applied, and the ratio of the cross-sectional area between the rod side hydraulic oil chamber 973b and the head side hydraulic oil chamber 973a in the direction in which the hydraulic oil force is applied are the same for all cylinders.

In this case too, when the driving side arm 714C moves to the driving side by half the remaining backlash, the operating side arm 714B moves to the operating side by half the remaining backlash, and the amount of hydraulic oil on the secondary side of the pilot check valves 821 and 822 does not change.

In addition, the cross-sectional area of the operating side shift cylinder 935B and the driving side shift cylinder 935C that the hydraulic oil hits is _{Awr <} Adh, and the pressure is pwr > _pdh , and the relationship is _Awr × _pwr = _Adh × _pdh , so the supporting force of the driving side arm 714C and the operating side arm 714B is the same.

Similarly, when a thrust force acts on the roll set 710A in the direction of the operating side, a thrust reaction force of the same force is generated on the rod side of the driving side and the head side of the operating side, so even in the configuration of this embodiment, the support force for the thrust force on the operating side and the driving side can be halved.

The rest of the configuration and operation are substantially the same as those of the rolling mill and rolling method of the first embodiment described above, and details are omitted.

The rolling mill and rolling method of the fourth embodiment of the present invention also provide substantially the same effects as those of the rolling mill and rolling method of the first embodiment described above.

In addition, in the configuration of this embodiment 4, the bearing housing connection part of the hydraulic cylinder on the driving side and the bearing housing connection part of the hydraulic cylinder on the operating side can be located closer to the rolled material 5, so the structure around the bearing housing connection part can be made symmetrical on the driving side and the operating side, making it possible to standardize the structure and resulting in a simple device.

In addition, the length of the hydraulic cylinder is shorter than in the double-rod configuration of Example 1, so the protrusion on the operating side of the shift device can be reduced, making it possible to secure space for the roll changing device.

The piston 973d of the second intermediate cylinder 973, the piston 943d of the driving side output shift cylinder 935C, the piston 945d of the operating side output shift cylinder 935B, and the piston 971d of the first intermediate cylinder 971 can have the same cross-sectional area, but this is not necessary as long as the ratio of the cross-sectional area of the head/rod side of the pistons of each cylinder is the same.

＜Other＞
The present invention is not limited to the above-mentioned embodiment, but includes various modified examples. The above-mentioned embodiment has been described in detail to explain the present invention in an easily understandable manner, and the present invention is not necessarily limited to the embodiment having all of the described configurations.

It is also possible to replace part of the configuration of one embodiment with the configuration of another embodiment, and it is also possible to add the configuration of another embodiment to the configuration of one embodiment. It is also possible to add, delete, or replace part of the configuration of each embodiment with other configurations.

For example, the above description is based on a rolling mill in which the mill rolls shift in the axial direction of the rolls, but the present invention also covers rolling mills that are equipped with hydraulic cylinders that fix the axial position, i.e., rolling mills that do not shift in the axial direction.

1...Rolling equipment 5...Rolled material 30...First stand (rolling mill)
40...Second stand (rolling mill)
50...Third stand (rolling mill)
60...4th stand (rolling mill)
70...5th stand (rolling mill)
80... Control device 90... Hydraulic device 700... Housing 702... Inlet side fixed member 703... Outlet side fixed member 705A, 705B, 705E, 705F, 706C, 706D... Hydraulic cylinder (horizontal actuator)
710...Upper work roll (mill roll)
710A...Roll set 711...Lower work roll (mill roll)
712...Upper work roll bearing housing 712A...Upper operation side bearing housing 712A1...Shift block 712B...Upper drive side bearing housing 712B1...Shift block 713...Lower work roll bearing housing 713A, 713B...Bearing housing 714A, 714B... Operation side arm 714C, 714D...Drive side arm 715...Shift cylinder (hydraulic cylinder)
715A, 715A1, 830...operation side entry shift cylinder (hydraulic cylinder, operation side hydraulic cylinder)
715A2, 715B2...Transmission members 715B, 715B1, 831, 935B...Operation side output shift cylinder (hydraulic cylinder, operation side hydraulic cylinder)
715C, 715C1, 832, 935C... Drive side output shift cylinder (hydraulic cylinder, drive side hydraulic cylinder)
715D, 715D1, 833... Drive side entry shift cylinder (hydraulic cylinder, drive side hydraulic cylinder)
716: Position sensor 717: Shift cylinder (hydraulic cylinder)
720...Upper intermediate roll (mill roll)
721...Lower intermediate roll (mill roll)
722...Upper intermediate roll bearing housing 723...Lower intermediate roll bearing housing 730...Upper reinforcement roll (mill roll)
731...Lower reinforcement roll (mill roll)
732 ... Upper backing roll bearing housing 733 ... Lower backing roll bearing housing 740, 741, 742, 743 ... Upper work roll bending cylinder 744, 745, 746, 747 ... Lower work roll bending cylinder 750, 751 ... Upper intermediate roll bending cylinder 752, 753 ... Lower intermediate roll bending cylinder 760 ... Upper work roll bearing housing backlash removal cylinder 762 ... Lower work roll bearing housing backlash removal cylinder 771 ... Upper intermediate roll bearing housing backlash removal cylinder 773 ... Lower intermediate roll bearing housing backlash removal cylinder 780 ... Upper backing roll bearing housing backlash removal cylinder 782 ... Lower backing roll bearing housing backlash removal cylinder 790A, 790B ... Radial bearing 800A, 801 ... Pressure line 800B, 802 ... Tank line 803, 804 ... Pressure line 805 ... Drive side opposite plate side pressure line (piping)
805A, 805B, 805B1, 805B2, 823, 824, 825...Pressure lines (piping)
805C1, 805C2...Intermediate rod pressure line (piping)
806: Operation side plate side pressure line (piping)
807: Drive side plate pressure line (piping)
807A, 807B... Drive side plate side pressure line 807C1, 807C2... Intermediate rod pressure line 808... Operation side opposite plate side pressure line (piping)
810... Solenoid switching valves 811, 812... Relief valves 821, 822...Pilot check valve 830a...Operation side inlet plate side hydraulic oil chamber 830b...Operation side inlet opposite plate side hydraulic oil chamber 831a...Operation side outlet plate side hydraulic oil chamber 831b...Operation side outlet opposite plate side hydraulic oil chamber 833a...Drive side inlet plate side hydraulic oil chamber 833b...Drive side inlet opposite plate side hydraulic oil chamber 832a, 923a, 923a1...Drive side outlet plate side hydraulic oil chamber (drive side plate side hydraulic oil chamber)
832b, 923b, 923b1...driving side, outlet side, opposite plate side hydraulic oil chamber (driving side, opposite plate side hydraulic oil chamber)
923c, 925c...Rod 923c1...Single rod (driving side hydraulic cylinder rod)
923d, 923d1, 925d, 925d1, 943d, 945d, 971d, 973d... piston 924a... drive side inlet plate side hydraulic oil chamber (drive side plate side hydraulic oil chamber)
924b...Drive side inlet side opposite plate side hydraulic oil chamber (drive side opposite plate side hydraulic oil chamber)
925a, 925a1...operation side outlet plate side hydraulic oil chamber (operation side plate side hydraulic oil chamber)
925b, 925b1...operation side, outlet side, opposite plate side hydraulic oil chamber (operation side, opposite plate side hydraulic oil chamber)
925c1... Single rod (operation side hydraulic cylinder rod)
926a...operation side inlet plate side hydraulic oil chamber (operation side plate side hydraulic oil chamber)
926b...operation side inlet side opposite plate side hydraulic oil chamber (operation side opposite plate side hydraulic oil chamber)
943a...Drive side outlet rod side hydraulic oil chamber (drive side plate side hydraulic oil chamber)
943b... Drive side outlet head side hydraulic oil chamber (drive side opposite plate side hydraulic oil chamber)
943c...Rod (driving side hydraulic cylinder rod)
945a...Operation side outlet rod side hydraulic oil chamber (operation side plate side hydraulic oil chamber)
945b...operation side outlet head side hydraulic oil chamber (operation side opposite plate side hydraulic oil chamber)
945c...Rod (operation side hydraulic cylinder rod)
971...first intermediate cylinder 971a...head side hydraulic oil chamber 971b...rod side hydraulic oil chamber 973...second intermediate cylinder 973a...head side hydraulic oil chamber 973b...rod side hydraulic oil chamber

Claims (13)

1. Mill rolls and
   a plurality of hydraulic cylinders including a drive side hydraulic cylinder provided on a drive side of the mill roll configured to apply an axial force to the mill roll, and an operation side hydraulic cylinder provided on an operation side of the mill roll configured to apply the axial force;
   a hydraulic circuit configured to supply hydraulic oil to the plurality of hydraulic cylinders, so that the driving hydraulic cylinder and the operating hydraulic cylinder move in the axial direction and maintain the axial position of the mill roll;
   The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, when an external force received by the mill roll causes only one of the driving side hydraulic cylinder or the operating side hydraulic cylinder to apply the axial force to the mill roll, the other of the driving side hydraulic cylinder or the operating side hydraulic cylinder moves in the opposite direction to the one of the hydraulic cylinders.
2. 2. The rolling mill according to claim 1,
   In the hydraulic circuit, a driving side plate-side hydraulic oil chamber and an operating side opposite-plate-side hydraulic oil chamber are connected by piping, and a driving side opposite-plate-side hydraulic oil chamber and an operating side plate-side hydraulic oil chamber are connected by piping, so that the driving side hydraulic cylinder and the operating side hydraulic cylinder each apply a force in the same direction to the mill roll.
3. 3. The rolling mill according to claim 2,
   The hydraulic circuit is configured such that, when either one of the driving side hydraulic cylinder or the operating side hydraulic cylinder moves a predetermined stroke, the other of the driving side hydraulic cylinder or the operating side hydraulic cylinder also moves in the opposite direction to the predetermined stroke without changing the amount of oil in the connected piping.
4. 2. The rolling mill according to claim 1,
   The driving side hydraulic cylinder and the operating side hydraulic cylinder are double rod cylinders,
   The cross-sectional areas of the drive side plate-side hydraulic oil chamber and the drive side opposite plate-side hydraulic oil chamber in the direction in which the hydraulic oil force is applied are the same,
   The cross-sectional areas of the operation side plate-side hydraulic oil chamber and the operation side opposite plate-side hydraulic oil chamber in the direction in which the hydraulic oil force is applied are the same,
   the driving side plate side hydraulic oil chamber and the operation side opposite plate side hydraulic oil chamber are connected by piping, and the driving side opposite plate side hydraulic oil chamber and the operation side plate side hydraulic oil chamber are connected by piping.
5. 2. The rolling mill according to claim 1,
   The driving side hydraulic cylinder and the operating side hydraulic cylinder are single rod cylinders,
   The driving side hydraulic cylinder rod and the operating side hydraulic cylinder rod are oriented in the same direction.
   The drive side plate-side hydraulic oil chamber and the operation side opposite plate-side hydraulic oil chamber are connected by piping, and the cross-sectional areas in the direction in which the hydraulic oil force is applied are the same.
   A rolling mill in which the drive side, opposite plate side hydraulic oil chamber and the operation side, plate side hydraulic oil chamber are connected by piping and have the same cross-sectional area in the direction in which the hydraulic oil force is applied.
6. 2. The rolling mill according to claim 1,
   The driving side hydraulic cylinder and the operating side hydraulic cylinder are single rod cylinders,
   The directions of the drive side hydraulic cylinder rod and the operation side hydraulic cylinder rod are reversed,
   Equipped with two or more single rod intermediate cylinders,
   The rod side hydraulic oil chamber of the drive side and the rod side hydraulic oil chamber of the first intermediate cylinder are connected by a pipe.
   The drive-side head-side hydraulic oil chamber and the second intermediate cylinder head-side hydraulic oil chamber are connected by piping,
   The operating side rod side hydraulic oil chamber and the second intermediate cylinder rod side hydraulic oil chamber are connected by piping,
   The operating side head side hydraulic oil chamber and the first intermediate cylinder head side hydraulic oil chamber are connected by piping,
   A rolling mill in which a ratio of cross-sectional areas between the driving side rod side hydraulic oil chamber and the driving side head side hydraulic oil chamber in the direction in which the force of the hydraulic oil is applied, a ratio of cross-sectional areas between the operating side rod side hydraulic oil chamber and the operating side head side hydraulic oil chamber in the direction in which the force of the hydraulic oil is applied, a ratio of cross-sectional areas between the first intermediate cylinder rod side hydraulic oil chamber and the first intermediate cylinder head side hydraulic oil chamber in the direction in which the force of the hydraulic oil is applied, and a ratio of cross-sectional areas between the second intermediate cylinder rod side hydraulic oil chamber and the second intermediate cylinder head side hydraulic oil chamber in the direction in which the force of the hydraulic oil is applied are the same.
7. 7. The rolling mill according to claim 6,
   A rolling mill configured such that a drive-side hydraulic cylinder rod and an operation-side hydraulic cylinder rod face outward in the axial direction.
8. In the rolling mill according to any one of claims 1 to 7,
   the driving side hydraulic cylinder and the operating side hydraulic cylinder are provided on the inlet side and the outlet side of the rolling mill, respectively;
   the rolling mill comprising piping connecting corresponding hydraulic oil chambers on the inlet side and the outlet side.
9. In the rolling mill according to any one of claims 1 to 7,
   A control device is provided for controlling the operation of the hydraulic cylinders,
   the control device is configured to drive the drive-side hydraulic cylinder and the operation-side hydraulic cylinder to shift the mill roll in the axial direction.
10. In the rolling mill according to any one of claims 1 to 7,
    A rolling mill comprising a horizontal actuator for adjusting the angle of the mill roll in the horizontal direction.
11. Mill rolls and
    a plurality of hydraulic cylinders including a drive side hydraulic cylinder provided on a drive side of the mill roll configured to apply an axial force to the mill roll, and an operation side hydraulic cylinder provided on an operation side of the mill roll configured to apply the axial force;
    and a hydraulic circuit configured to supply hydraulic oil to the plurality of hydraulic cylinders, so that the driving hydraulic cylinder and the operating hydraulic cylinder move in the axial direction, and maintain the axial position of the mill roll, comprising:
    the hydraulic circuit is configured such that, after the hydraulic circuit has held the axial position of the mill roll, when an external force applied to the mill roll causes only one of the driving side hydraulic cylinder and the operating side hydraulic cylinder to apply the axial force to the mill roll, the other of the driving side hydraulic cylinder and the operating side hydraulic cylinder moves in a direction opposite to that of the one hydraulic cylinder,
    A rolling method for rolling the rolled material.
12. The rolling method according to claim 11,
    The hydraulic circuit is configured to connect a driving side plate-side hydraulic oil chamber and an operating side opposite-plate-side hydraulic oil chamber with piping, and to connect the driving side opposite-plate-side hydraulic oil chamber and the operating side plate-side hydraulic oil chamber with piping, so that the driving side hydraulic cylinder and the operating side hydraulic cylinder each apply a force in the same direction to the mill roll, and the rolling method rolls the rolled material.
13. The rolling method according to claim 12,
    The hydraulic circuit is configured so that, when either one of the driving side hydraulic cylinder or the operating side hydraulic cylinder moves a predetermined stroke, the other of the driving side hydraulic cylinder or the operating side hydraulic cylinder is also moved in the opposite direction to the predetermined stroke without changing the amount of oil in the connected piping, thereby rolling the rolled material.

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