Rolling mill and rolling method

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

Technical Field

[0001] The present invention relates to a rolling mill and a rolling method.

Background Art

[0002] Patent Document 1 describes an upper work roll, radial bearings and thrust bearings provided on the operating side and the driving side of the upper work roll for supporting the upper work roll, a shift cylinder provided on the operating side of the upper work roll for applying forces in both the operating side and the driving side directions to the thrust bearing, and a shift cylinder provided on the driving side of the upper work roll for applying forces in both the operating side and the driving side directions to the radial bearing. The shift cylinders apply forces in the same direction to the radial bearing and the thrust bearing, respectively, when the upper work roll does not axially shift at least during rolling.

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] Patent Document 1 discloses a structure for roll shifting on both the driving side and the operating side.

[0005] Due to changes in conditions such as rotation, the direction of the thrust force acting on the roll of a rolling mill may switch between the driving side and the operating side. In this case, after setting the roll position, a thrust force in the opposite direction acts, causing the roll, more specifically, the member supporting the roll, to be temporarily separated from the arms on the driving side and the operating side that support the thrust force. Therefore, the positions of the arms on both sides must be readjusted to support the thrust force of the roll.

[0006] However, in some cases, the thrust force may be supported by only one arm due to uneven axial play (gap) in the support section that applies axial force to the roll.

[0007] If one arm cannot support the load, the pressure inside the piping connected to the hydraulic cylinder that moves the arm will exceed the relief valve setting pressure (maximum pressure), causing the hydraulic fluid to leak out of the relief valve and move the other arm as well. However, since the relief valve setting pressure is high, investigations have revealed that this may lead to a reduction in the lifespan of peripheral equipment such as bearings that are subjected to the load.

[0008] It has become clear that, not limited to the cases described above, if the roll expands due to the heat generated by the metal strip, uneven play in the axial direction can occur, potentially leading to the same problems as described above.

[0009] The present invention aims to provide a rolling mill and a rolling method that can improve the lifespan of roll support parts, such as bearings on both sides of the roll, without creating excessive pressure in the piping connected to the hydraulic cylinder. [Means for solving the problem]

[0010] The present invention includes multiple means for solving the above problems, but one example is a mill roll, a plurality of hydraulic cylinders including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply the axial force, and a hydraulic circuit configured to supply hydraulic fluid to the plurality of hydraulic cylinders, causing the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction and maintain the axial position of the mill roll. The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are both rod cylinders, and the drive-side plate-side hydraulic oil chamber and the drive-side recoil plate-side hydraulic oil chamber have the same cross-sectional area in the direction to which the hydraulic fluid force is applied, and the operating-side plate-side hydraulic oil chamber and the operating-side recoil plate-side hydraulic oil chamber have the same cross-sectional area in the direction to which the hydraulic fluid force is applied, and the drive-side plate-side hydraulic oil chamber and the operating-side recoil plate-side hydraulic oil chamber are connected by piping, and the drive-side recoil plate-side hydraulic oil chamber and the operating-side plate-side hydraulic oil chamber are connected by piping,The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply an axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. [Effects of the Invention]

[0011] According to the present invention, the lifespan of roll support parts such as bearings on both sides of the roll can be improved without creating excessive pressure in the piping connected to the hydraulic cylinder. Problems, configurations, and effects other than those described above will be clarified by the following description of embodiments. [Brief explanation of the drawing]

[0012] [Figure 1] This diagram shows an overview of the rolling equipment equipped with the rolling mill of Example 1. [Figure 2] This is a front view illustrating the overview of the rolling mill in Example 1. [Figure 3] This is a view along the line A-A' in Figure 2. [Figure 4] This is a schematic diagram illustrating the problem of the present invention. [Figure 5] This is a schematic diagram illustrating the problem of the present invention. [Figure 6] This is a schematic diagram illustrating the problem of the present invention. [Figure 7] This is a plan view illustrating the details of the upper work roll section of the rolling mill in Example 1. [Figure 8] This is a plan view illustrating the details of the upper work roll portion of the rolling mill in Example 1. [Figure 9] This is a plan view illustrating the details of the upper work roll portion of the rolling mill in Example 1. [Figure 10] This is a plan view illustrating the details of the upper work roll portion of a rolling mill, which is a modified example of Example 1. [Figure 11] This is a plan view illustrating the details of the upper work roll section of the rolling mill in Example 2. [Figure 12] This is a plan view illustrating the details of the upper work roll section of the rolling mill in Example 3. [Figure 13] This is a plan view illustrating the details of the upper work roll section of the rolling mill in Example 3. [Figure 14] This is a plan view illustrating the details of the upper work roll portion of the rolling mill in Example 4. [Modes for carrying out the invention]

[0013] Examples of the rolling mill and rolling method of the present invention will be described below with reference to the drawings.

[0014] In the drawings used in this specification, identical or corresponding components are denoted by the same or similar reference numerals, and repeated explanations of these components may be omitted.

[0015] Furthermore, in this specification, thrust resistance force refers to the force acting on each roll and its bearing housing of a rolling mill in the direction of the roll axis during rolling or when the rolling mill is shifting, and the force acting on the device that supports that force; it has the same meaning as thrust force. Thrust reaction force refers to the force generated from the device that supports the thrust resistance force, and means a force of the same magnitude but in the opposite direction to the thrust resistance force.

[0016] <Example 1> One embodiment of the rolling mill and rolling method of the present invention will be described with reference to Figures 1 to 10.

[0017] First, an overview of the rolling equipment equipped with the rolling mill of this embodiment will be described using Figures 1 to 3. Figure 1 is an overview of the rolling equipment equipped with the rolling mill of this embodiment 1, Figure 2 is a front view illustrating the overview of the rolling mill, and Figure 3 is a view taken along the line A-A' in Figure 2.

[0018] As shown in Figure 1, the rolling equipment 1 is equipped with multiple rolling mills for hot-rolling the rolled material 5 into strips, and has a control device 80 and five stands, the first stand 30, the second stand 40, the third stand 50, the fourth stand 60, and the fifth stand 70, starting from the entry side of the rolled material 5.

[0019] Of these, the first stand 30, the second stand 40, the third stand 50, the fourth stand 60, and the fifth stand 70, as well as the part of the control device 80 that controls each stand, correspond to the rolling mill as defined in this invention.

[0020] Furthermore, the rolling mill 1 is not limited to multiple stands like the five stands shown in Figure 1, but may also consist of a single stand. Also, since there is no restriction on the temperature of the rolled material during rolling, it may also be a cold rolling mill.

[0021] Next, a part of the overview of the rolling mill of the present invention will be explained using Figure 2. In Figures 2 and beyond, the fifth stand 70 shown in Figure 1 will be used as an example, but the rolling mill of the present invention can be applied to any of the stands shown in Figure 1, such as the first stand 30, the second stand 40, the third stand 50, and the fourth stand 60.

[0022] In Figure 2, the fifth stand 70, which is the rolling mill in this embodiment, is a six-stage rolling mill for rolling the rolled material 5, and includes a housing 700, a control device 80, and a hydraulic device 90.

[0023] The housing 700 includes an upper work roll 710 and a lower work roll 711, and 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. Furthermore, it includes an upper reinforcing roll 730 and a lower reinforcing roll 731 that support the upper intermediate roll 720 and the lower intermediate roll 721 by contacting them, respectively.

[0024] In this invention, the term "mill roll" refers to any of the above-mentioned upper work roll 710, lower work roll 711, upper intermediate roll 720, lower intermediate roll 721, upper reinforcing roll 730, and lower reinforcing roll 731. In the case of a rolling mill that does not have intermediate rolls such as the first stand 30 or the second stand 40, the upper and lower work rolls and the upper and lower reinforcing rolls refer to the "mill rolls."

[0025] Of these rolls, the upper work roll 710 has a radial bearing 790A (see Figure 7) at its operating end, which shifts axially with the upper work roll 710 and receives the load from the roll. This radial bearing 790A is supported by an upper operating-side bearing housing 712A. Similarly, the drive-side has a radial bearing 790B (see Figure 7) which shifts axially with the upper work roll 710 and receives the load from the roll. This radial bearing 790B is supported by an upper drive-side bearing housing 712B. Here, the radial bearing 790A on the operating side and the radial bearing 790B on the drive-side are configured to support not only the roll bending force acting vertically but also the thrust force acting in the direction of the roll axis.

[0026] Similarly, the lower work roll 711 also has bearings (omitted for illustrative purposes) at both the drive and operating ends in the axial direction, and these bearings are supported by the lower work roll bearing housing 713 (bearing housing 713A on the operating side and bearing housing 713B on the drive side).

[0027] 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 Figure 3, via an upper operating bearing housing 712A on the operating side and an upper driving bearing housing 712B on the driving side. Similarly, the lower work roll 711 is also configured to be shiftable in the roll axis direction by a shift cylinder 717, as shown in Figure 3, via an operating bearing housing 713A and a driving bearing housing 713B.

[0028] Furthermore, as shown in Figure 3, the upper work roll 710 and the lower intermediate roll 721 have tapered ends on the operating side, and the lower work roll 711 and the upper intermediate roll 720 have tapered ends on the driving side. The upper work roll 710 and the lower work roll 711 are point-symmetrical vertically, and the upper intermediate roll 720 and the lower intermediate roll 721 are point-symmetrical vertically.

[0029] Returning to Figure 2, the inlet fixing member 702 is fixed to the inlet housing 700 of the rolled material 5. The outlet fixing member 703 is fixed to the outlet housing 700 of the rolled material 5 so as to be opposite to the inlet fixing member 702.

[0030] In the fifth stand 70, as shown in Figure 2, the upper work roll bearing housing 712 is supported on both the operating and driving sides by upper work roll bending cylinders 740 and 742, which are provided in the axial direction of the roll of the input fixing member 702, and upper work roll bending cylinders 741 and 743, which are provided in the axial direction of the roll of the output fixing member 703.

[0031] Then, by driving these cylinders as needed, a bending force is applied vertically to the bearing of the upper work roll 710.

[0032] Similarly, on both the operating and driving sides, the lower work roll bearing housing 713 is supported by lower work roll bending cylinders 744 and 746 provided on the input fixing member 702 and lower work roll bending cylinders 745 and 747 provided on the output fixing member 703. By appropriately driving these cylinders, a bending force is applied to the bearing of the lower work roll 711 in the vertical direction.

[0033] Of these cylinders, the upper work roll bending cylinders 740 and 741 are positioned to apply a bending force to the bearing of the upper work roll 710 that contacts the rolled material 5 in the vertical increase direction (away from the rolled material direction). The upper work roll bending cylinders 742 and 743 are positioned to apply a bending force to the bearing in the vertical decrease direction (away from the rolled material direction), which is the opposite direction to that of the upper work roll bending cylinders 740 and 741.

[0034] Similarly, the lower work roll bending cylinders 744 and 745 are positioned to apply a bending force to the bearing of the lower work roll 711 that contacts the rolled material 5 in the vertical increasing direction. The lower work roll bending cylinders 746 and 747 are positioned to apply a bending force to the bearing in the opposite direction to that of the lower work roll bending cylinders 744 and 745, in the decreasing direction.

[0035] Furthermore, as shown in Figure 2, for the purpose of eliminating play, two upper work roll bearing housing play-eliminating cylinders 760 are provided in the axial direction of the roll on the entry side fixing member 702 on the entry side of the rolled 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 housing 712.

[0036] Similarly, the entry-side fixing member 702 is provided with two lower work roll bearing housing cylinders 762 that apply pressing force in the rolling direction to the lower work roll 711 via the liner of the lower work roll bearing housing 713.

[0037] These cylinders allow the desired force to be applied to the upper work roll 710, etc., in a direction perpendicular to the roll axis.

[0038] Furthermore, as shown in Figure 2, a hydraulic cylinder 705A may be provided on both the drive side and the operating side of the housing 700 as a horizontal actuator for adjusting the angle of the upper work roll 710 in the horizontal direction.

[0039] Similarly, a hydraulic cylinder 705B may be provided on either the drive side or the operating side of the housing 700 as a horizontal actuator for adjusting the angle of the lower work roll 711 in the horizontal direction.

[0040] Furthermore, in some cases, hydraulic cylinders 705E and 705F are provided on both the drive side and the operating side of the exit side of the housing 700, and hydraulic cylinders 706C and 706D are provided on both the drive side and the operating side of the inlet side of the housing 700, respectively, as horizontal actuators for adjusting the angle of the upper intermediate roll 720, lower intermediate roll 721, upper reinforcing roll 730, and lower reinforcing roll 731 in the horizontal direction.

[0041] These hydraulic cylinders 705A, 705B, 705E, 705F, 706C, and 706D, which serve as horizontal actuators, are not limited to hydraulic cylinders and can be configured with other elements such as worm gears.

[0042] Bearings (not shown) are provided at the axial ends of the upper intermediate roll 720 on both the drive side and the operating side, and these bearings are supported by the upper intermediate roll bearing housing 722. Similarly, bearings (not shown) are provided at the axial ends of the lower intermediate roll 721 on both the drive side and the operating side, and these bearings are supported by the lower intermediate roll bearing housing 723.

[0043] The upper intermediate roll 720 supports the upper intermediate roll bearing housing 722 on both the operating and driving sides by an upper intermediate roll bending cylinder 750 provided on the input side fixing member 702 and an upper intermediate roll bending cylinder 751 provided on the output side fixing member 703. By appropriately driving these cylinders, a bending force is applied to the bearing in the vertical increasing direction.

[0044] The lower intermediate roll 721 is also supported on both the operating and driving sides by a lower intermediate roll bending cylinder 752 provided on the entry side fixing member 702 and a lower intermediate roll bending cylinder 753 provided on the exit side fixing member 703, and by driving these cylinders as appropriate, a bending force is applied to the bearing in the vertical increasing direction.

[0045] Furthermore, as shown in Figure 2, the exit housing 700 is provided with an upper intermediate roll bearing housing camber cylinder 771 to apply a horizontal force to the upper intermediate roll 720 via the upper intermediate roll bearing housing 722. Similarly, the exit housing 700 is provided with a lower intermediate roll bearing housing camber cylinder 773 to apply a horizontal force to the lower intermediate roll 721 via the lower intermediate roll bearing housing 723.

[0046] Furthermore, bearings (not shown) are provided at the axial ends of the upper reinforcing roll 730 on both the drive side and the operating side, and these bearings are supported by the upper reinforcing roll bearing housing 732. Similarly, the lower reinforcing roll 731 also has bearings (not shown) at its axial ends on both the drive side and the operating side, and these bearings are supported by the lower reinforcing roll bearing housing 733.

[0047] Furthermore, as shown in Figure 2, the inlet housing 700 is provided with an upper reinforcing roll bearing box relief cylinder 780 to apply a horizontal force to the upper reinforcing roll 730 via the upper reinforcing roll bearing box 732. Similarly, the inlet housing 700 is provided with a lower reinforcing roll bearing box relief cylinder 782 to apply a horizontal force to the lower reinforcing roll 731 via the lower reinforcing roll bearing box 733.

[0048] The hydraulic system 90 is connected to each of the aforementioned bending cylinders, backlash cylinders, shift cylinders 715, 717, hydraulic cylinders 705A, 705B, 705E, 705F, 706C, 706D, or reduction cylinders (not shown) that apply reduction force to the upper work roll 710 and lower work roll 711 for rolling the rolled material 5, and this hydraulic system 90 is connected to the control device 80.

[0049] The control device 80 operates the hydraulic system 90 to supply and discharge pressurized oil to each of the bending cylinders mentioned above, thereby driving each of these cylinders. As a result, the control device 80 is configured to drive, for example, the drive-side exit shift cylinder 715C (see Figure 7) and the operating-side exit shift cylinder 715B (see Figure 7), thereby enabling the upper work roll 710 to be shifted in the axial direction.

[0050] Next, the characteristic features of the rolling mill and rolling method in the present invention will be explained using Figures 4 to 6, with an example of 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 reinforcing roll 730, lower reinforcing roll 731, and even the work rolls, intermediate rolls, and reinforcing rolls of the other stands can be configured and used in a similar manner, and their detailed configurations are substantially the same, so their explanation will be omitted.

[0051] First, the problems of the present invention will be explained using Figures 4 to 6. Figures 4 to 6 are schematic diagrams illustrating the problems of the present invention.

[0052] Figure 4 shows the moment when the electromagnetic switching valve 810 is excited to b and shifted in the drive direction, and then the electromagnetic switching valve is moved to the neutral position and the pilot check valve is closed, stopping the shifting operation in the drive direction.

[0053] For the sake of simplicity, the roll set 710A, including the upper work roll 710, is shown here in a simplified, integrated form. Shift cylinders are installed on both the inlet and outlet sides, but since the inlet side of the rolled material 5 has almost the same configuration as the outlet side, only the drive-side outlet shift cylinder 515C and the operating-side outlet shift cylinder 515B are shown as examples here.

[0054] As shown in Figure 4, the roll set 710A is supported in the axial position by the drive side exit shift cylinder 515C via the drive side arm 714C on the drive side. operation On the other side, the axial position is supported by the operating side exit shift cylinder 515B via the operating side arm 714B.

[0055] The drive-side exit-side shift cylinder 515C is a single-rod type cylinder and includes a drive-side exit-side plate-side hydraulic oil chamber 523a on the rod side, a drive-side exit-side reverse-plate-side hydraulic oil chamber 523b on the head side, a rod 523c, and a piston 523d, among others.

[0056] The operating-side exit-side shift cylinder 515B is also a single-rod type cylinder and includes the operating-side exit-side plate-side hydraulic oil chamber 525a on the rod side, the operating-side exit-side reverse-plate-side hydraulic oil chamber 525b on the head side, a rod 525c, and a piston 525d.

[0057] In the hydraulic circuit shown in Figure 4, a pilot check valve 821 and a relief valve 811 are provided on pressure line 803, and a pilot check valve 822 and a relief valve 812 are provided on pressure line 804.

[0058] The pressure line 803 branches into the drive-side deflector plate pressure line 505 and the operating-side plate pressure line 506 on the cylinder side of the pilot check valve 821. The drive-side deflector plate pressure line 505 is connected to the drive-side outlet deflector plate hydraulic oil chamber 523b, and the operating-side plate pressure line 506 is connected to the operating-side outlet plate hydraulic oil chamber 525a.

[0059] The pressure line 804 branches into a drive-side plate-side pressure line 507 and an operation-side counter-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-side plate-side hydraulic oil chamber 523a, and the operation-side counter-plate-side pressure line 508 is connected to the operation-side outlet-side counter-plate-side hydraulic oil chamber 525b.

[0060] In the configuration shown in FIG. 4, when shifting the roll set 710A to the drive side, the thrust resistance force H acting on the drive-side outlet-side shift cylinder 515C and the operation-side outlet-side shift cylinder 515B from the roll set 710A t is, H t =H d +H w is represented by. Here, H w is the force acting on the operation side, and H d is the force acting on the drive side.

[0061] The operation-side outlet-side counter-plate-side hydraulic oil chamber 525b, which is the head side of the operation-side outlet-side shift cylinder 515B, and the drive-side outlet-side plate-side hydraulic oil chamber 523a, which is the rod side of the drive-side outlet-side shift cylinder 515C, are connected by the drive-side plate-side pressure line 507 and the operation-side counter-plate-side pressure line 508. Therefore, the pressures p dr , p wh of each hydraulic oil chamber are equal.

[0062] However, since there is an area difference between the cross-sectional area A wh of the piston 525d that receives the pressure on the head side of the operation-side outlet-side shift cylinder 515B and the cross-sectional area A dr of the piston 523d that receives the pressure on the rod side of the drive-side outlet-side shift cylinder 515C, the output Fw of the operation-side outlet-side shift cylinder 515B is larger than the output Fd of the drive-side outlet-side shift cylinder 515C, and the thrust resistance force acting on the shift cylinder from the roll set 710A is H w >H d The relationship is such that the thrust resistance force H w acting on the operation-side arm 714B has a larger value.

[0063] In this configuration, consider the case when the roll set 710A moves on its own toward the drive side. Figure 5 shows the moment when the roll set 710A moves on its own toward the drive side and first hits the drive side arm 714C after the shift position of the roll set 710A has been determined, the pilot check valves 821 and 822 have been closed and the shift operation has been stopped.

[0064] On the operating side, there is some remaining play in the operating 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.

[0065] Figure 6 shows the point when the roll set 710A moves further in the drive direction from Figure 5, the remaining play on the operating side becomes zero, and the movement of the roll set 710A in the drive direction stops.

[0066] Here, the area A of the drive-side outlet plate-side hydraulic oil chamber 523a of the drive-side outlet shift cylinder 515C. dr Area A of the hydraulic oil chamber 523b on the drive side, exit side, and reverse plate side. dh Area A of the operating side outlet plate side hydraulic oil chamber 525a of the operating side outlet shift cylinder 515B wr , and the area A of the operating side outlet side hydraulic oil chamber 525b wh However, A wh =2A wr and A dh =2A dr This shows the case where the relationship is as follows.

[0067] When it first hits the drive arm 714C, the drive exit shift cylinder 515C is pushed by the thrust resistance force of the roll set 710A and p dh The pressure arises. wr is p dh It tries to reach the same pressure as A. wr =A wh / 2 so p wh =p wr / 2, also p dr =p wh =p wr / 2=p dh It tries to become / 2.

[0068] Here, A dh ×p dh =H d +A dr ×p dr Because of the relationship, substituting the above relationship, A dh ×p dh =H d +(A dh / 2) × (p dh / 2) The relationship holds, and from this equation H d =A dh ×p dh This results in a force of 3 / 4. In other words, pressure is also generated on the rod side of the drive-side exit shift cylinder 515C, so it can only support up to 3 / 4 of the pushing force on the head side of the drive-side exit shift cylinder 515C.

[0069] Then, the drive-side exit-side shift cylinder 515C is H d When pushed and defeated, suppose the drive-side exit-side shift cylinder 515C is pushed and moves by 1 unit.

[0070] Drive side exit shift cylinder 515C is H d When pushed and moved in the drive direction, the operating arm 714B will move towards the operating side to reduce the remaining play.

[0071] If the drive-side exit shift cylinder 515C moves 1 unit to the drive side, hydraulic fluid flows from the drive-side exit plate-side hydraulic fluid chamber 523b of the drive-side exit shift cylinder 515C to the operating-side exit plate-side hydraulic fluid chamber 525a of the operating-side exit shift cylinder 515B. Therefore, although the piston 525d of the operating-side exit shift cylinder 515B wants to move 2 units to the operating-side exit plate-side hydraulic fluid chamber 525b, the operating-side exit plate-side hydraulic fluid chamber 525b can withstand the pushing force from the operating-side exit plate-side hydraulic fluid chamber 525a with half the pressure due to the difference in area. As a result, the operating-side exit plate-side hydraulic fluid chamber 525b can only move 1 / 2 of the movement corresponding to the 1 unit movement of the drive-side exit plate-side hydraulic fluid chamber 523a. Consequently, the operating-side exit plate-side hydraulic fluid chamber 525a cannot move 2 units, but only moves 1 / 2 of the way. Therefore, the hydraulic fluid corresponding to (2-1 / 2) on the operating side outlet plate side hydraulic fluid chamber 525a will flow out from the relief valve 811.

[0072] Specifically, if the drive-side exit shift cylinder 515C moves 1 unit towards the drive side, the operating-side exit shift cylinder 515B moves 1 / 2 unit towards the operating side. This reduces the remaining play to 0. Therefore, the drive-side arm 714C moves in the drive direction by 2 / 3 of the remaining play, and the operating-side arm 714B moves in the operating direction by 1 / 3 of the remaining play.

[0073] Also, the drive-side exit-side shift cylinder 515C is H d When pushed and moved by 1 unit in the drive direction, the rod side of the drive-side exit shift cylinder 515C also moves by 1 unit, so the head side of the operating-side exit shift cylinder 515B moves by 1 / 2 of the area ratio, and the rod side of the operating-side exit shift cylinder 515B also moves by 1 / 2. Therefore, the amount of hydraulic fluid is A dh ×1-A wr × 1 / 2 = A dh 3 / 4 of the force is released from the relief valve 811. Then, when the drive arm 714C has moved 2 / 3 of the remaining play and the operating arm 714B has moved 1 / 3 of the remaining play, the drive side exit shift cylinder 515C and the operating side exit shift cylinder 515B stop.

[0074] The operating arm 714B moves in the operating direction by the remaining 1 / 3 of the play, causing the position sensor 716 to move by the remaining 1 / 3 of the play.

[0075] The remaining play is the difference between the play on the operating side and the play on the driving side. If the remaining play is about 1 mm, the position sensor 716 will move approximately 1 mm × 1 / 3 = 0.3 mm towards the operating side.

[0076] As described above, when the roll set 710A is moved in the drive direction while receiving a thrust resistance force in the operating direction from the roll set 710A, and after the position of the roll set 710A is set, a thrust resistance force in the drive direction acts on the roll set 710A due to changes in conditions such as the rotation of the rolling mill's rolls, causing only the roll set 710A to move in the drive direction, the pressure rises above the set pressure (maximum pressure) of the relief valves 811 and 812 before the thrust resistance force is supported by both the drive and operating sides, causing the hydraulic fluid to leak out of the relief valves 811 and 812.

[0077] In other words, when the drive side alone can support the load, it does so alone. However, when the drive side fails, both the drive side and the operating side will support the load, and in that case, the pressure will exceed the maximum pressure while the hydraulic fluid is being released from the relief valves 811 and 812.

[0078] Therefore, there are problems in that the system cannot be supported on both sides until the set pressure of the relief valves 811 and 812 is reached, and when it is supported on both sides, the pressure will exceed the set pressure (maximum pressure).

[0079] Furthermore, the shift position of the Rollset 710A will be misaligned, requiring frequent adjustment of the shift position.

[0080] The above describes the case where the drive arm 714C makes contact first, leaving the remaining play on the operating side. However, the same problem occurs when the operating arm 714B makes contact first, leaving the remaining play on the drive side.

[0081] Furthermore, while the above explanation described the problem that occurs when the direction of thrust resistance changes, a similar problem arises when the length of the roll set 710A changes due to thermal expansion, as this creates a similar situation to when play is left on one side.

[0082] Next, the characteristic configuration of this embodiment, which can solve these problems, will be explained using Figures 7 to 9. Figures 7 to 9 are plan views illustrating the details of the upper work roll portion of the rolling mill.

[0083] As shown in Figure 7, the entry-side fixing member 702 on the operating side is provided with an operating-side entry-side shift cylinder 715A that applies force to the upper work roll 710 in both the operating and driving directions via an operating-side arm 714A connected to an upper operating-side bearing housing 712A that supports the operating-side radial bearing 790A.

[0084] Furthermore, the operating-side exit fixing member 703 is provided with an operating-side exit shift cylinder 715B that applies force to the upper work roll 710 in both the operating and driving directions via an operating-side arm 714B connected to an upper operating-side bearing housing 712A that supports the operating-side radial bearing 790A.

[0085] 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. The position of the position sensor 716 is not limited to this location and may also be located at the other operating-side in-side shift cylinder 715A or the drive-side shift cylinders 715C and 715D. Furthermore, there is no requirement for only one sensor; two or more sensors can be provided.

[0086] Similarly, the drive-side entry-side fixing member 702 is provided with a drive-side entry-side shift cylinder 715D that applies force to the upper work roll 710 in both the operating and driving directions via a drive-side arm 714D connected to an upper drive-side bearing housing 712B that supports the drive-side radial bearing 790B.

[0087] Furthermore, the drive-side outlet fixing member 703 is provided with a drive-side outlet shift cylinder 715C that applies force to the upper work roll 710 in both the operating and driving directions via a drive-side arm 714C connected to an upper drive-side bearing housing 712B that supports the drive-side radial bearing 790B.

[0088] The radial bearing 790A on the operating side is 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 radial bearing 790B on the driving side 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.

[0089] Since the axial force acting on the upper work roll 710 can be in the operating direction or the driving direction, each of the operating-side shift cylinders 715A, 715B and the driving-side shift cylinders 715C, 715D can support forces in either the operating or driving direction.

[0090] All of these, the operating-side in-shift cylinder 715A, the operating-side out-shift cylinder 715B, the drive-side out-shift cylinder 715C, and the drive-side in-shift cylinder 715D, are double-rod type cylinders in which the internal pistons 923d and 925d (only the out-side is shown as an example) have two rods 923c and 925c (only the out-side is shown as an example).

[0091] Furthermore, this embodiment includes a hydraulic circuit configured to supply hydraulic fluid to multiple hydraulic cylinders, causing the drive-side shift cylinders 715C, 715D and the operating-side shift cylinders 715A, 715B to move axially and maintain the axial position of the upper work roll 710.

[0092] In this hydraulic circuit, after the hydraulic circuit has maintained the axial position of the upper work roll 710, if the external force acting on the upper work roll 710 causes only one of the hydraulic cylinders—either the drive-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 hydraulic cylinder among the drive-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.

[0093] Furthermore, it is equipped with pressure lines 805, 806, 807, and 808 that connect the corresponding hydraulic fluid chambers on the inlet and outlet sides. For example, in the hydraulic circuit, the drive-side exit plate-side hydraulic oil chamber 923a, the drive-side in-plate-side hydraulic oil chamber 924a and the operator-side exit plate-side hydraulic oil chamber 925b and the operator-side in-plate-side hydraulic oil chamber 926b are connected by the drive-side plate-side pressure line 807 and the operator-side plate-side pressure line 808, respectively, so that the drive-side shift cylinders 715C and 715D and the operator-side shift cylinders 715A and 715B each apply force to the upper work roll 710 in the same direction. In addition, the drive-side exit plate-side hydraulic oil chamber 923b and the drive-side in-plate-side hydraulic oil chamber 924b and the operator-side exit plate-side hydraulic oil chamber 925a and the operator-side in-plate-side hydraulic oil chamber 926a are connected by the drive-side plate-side pressure line 805 and the operator-side plate-side pressure line 806.

[0094] As a result, when the direction of an external force changes, or when the distance between the supports on the supported side and the support on the supporting side changes due to thermal expansion of the mechanical device, etc., when one of the hydraulic cylinders among the drive-side shift cylinders 715C, 715D or the operating-side shift cylinders 715A, 715B moves a predetermined stroke, the hydraulic circuit is configured such that the other hydraulic cylinder of the drive-side shift cylinder 715C, 715D or the operating-side shift cylinder 715A, 715B moves in the opposite direction by the same predetermined stroke without changing the amount of oil in the connected pressure lines 805, 806, 807, 808.

[0095] A radial bearing 790A is installed in the upper operating side bearing housing 712A. A radial bearing 790B is installed in the upper driving side bearing housing 712B.

[0096] The radial bearings 790A and 790B are subjected to forces from the upper work roll bending cylinders 740 and 741 and the upper work roll bearing housing camber cylinder 760. These radial bearings 790A and 790B support these vertical forces acting on the roll axis while rotating.

[0097] Furthermore, since the radial bearings 790A and 790B also support the axial forces acting on the upper operating side bearing housing 712A and the upper driving side bearing housing 712B, four-row tapered roller bearings are generally used. In addition, the same specifications are used for the driving side radial bearing 790B and the operating side radial bearing 790A, which helps to avoid complicating maintenance work.

[0098] In the drive systems of the operating-side shift cylinders 715A, 715B and the driving-side shift cylinders 715C, 715D, an electromagnetic switching valve 810 is provided at the outlet of a pressure line 801 branched from a pressure line 800A through which pressurized oil discharged from a pump (not shown) of the hydraulic device 90 flows, and a tank line 802 branched from a tank line 800B connected to a tank (not shown) where pressurized oil is stored, to adjust the amount of oil flowing in and out.

[0099] When the electromagnetic switching valve 810 is energized, the rod side of the operating-side shift cylinders 715A and 715B near the plate (operating-side outlet plate-side hydraulic oil chamber 925a side) is connected to pressure lines 801 and 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.

[0100] Furthermore, the rod side of the drive-side shift cylinders 715C and 715D near the deflector plate (the drive-side exit deflector plate side hydraulic oil chamber 923b side) is also connected to pressure lines 801 and 800A via drive-side deflector plate side pressure line 805 and pressure line 803, and a force in the operating direction acts on the upper drive-side bearing housing 712B.

[0101] Furthermore, the rod side of the operating-side shift cylinders 715A and 715B closest to the anti-plate (operating-side outlet anti-plate hydraulic oil chamber 925b side) and the rod side of the driving-side shift cylinders 715C and 715D closest to the plate (driving-side outlet plate hydraulic oil chamber 923a side) are connected to tank lines 802 and 800B via the operating-side anti-plate pressure line 808 or the driving-side plate pressure line 807 and pressure line 804, respectively, so that both the operating-side and driving-side shift cylinders generate a shift force in the operating-side direction.

[0102] When the electromagnetic switching valve 810 is energized, the rod side of the operating-side shift cylinders 715A and 715B near the turntable (operating-side outlet turntable-side hydraulic oil chamber 925b side) is connected to pressure lines 801 and 800A via operating-side turntable-side pressure line 808 and pressure line 804, and a force in the driving direction acts on the upper operating-side bearing housing 712A.

[0103] Furthermore, the rod side of the drive-side shift cylinders 715C and 715D that is closer to the plate (the drive-side outlet plate-side hydraulic oil chamber 923a side) is connected to pressure lines 801 and 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 housing 712B.

[0104] Furthermore, the rod side of the operating-side shift cylinders 715A and 715B closest to the plate (operating-side outlet plate-side hydraulic oil chamber 925a side) and the rod side of the driving-side shift cylinders 715C and 715D closest to the opposite plate (driving-side outlet plate-side hydraulic oil chamber 923b side) are connected to tank lines 802 and 800B via the operating-side plate-side pressure line 806 or the driving-side 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 in the driving-side direction.

[0105] When the electromagnetic switching valve 810 is in the neutral position, the pilot check valves 821 and 822 prevent hydraulic fluid from flowing to both the rod side closer to the plate and the rod side closer to the opposite plate in both the operating-side shift cylinders 715A and 715B and the driving-side shift cylinders 715C and 715D.

[0106] The configuration of these electromagnetic switching valves 810 and the excitation control by the control device 80 provide a device that, when the axial shift of the upper work roll 710 is stopped, supports the upper work roll 710 so that it does not move in the axial direction, with the operating-side shift cylinders 715A, 715B and the driving-side shift cylinders 715C, 715D.

[0107] A pilot check valve 822 is provided on the pressure line 804 downstream of the electromagnetic switching valve 810, and a pilot check valve 821 is provided on the pressure line 803 downstream of the electromagnetic switching valve 810. This configuration prevents pressurized oil from flowing to both the rod side and head side of the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D when the electromagnetic switching valve 810 is in the neutral position. As a result, even when the shift of the upper work roll 710 is stopped, the operating side shift cylinders 715A, 715B and the driving side shift cylinders 715C, 715D support the upper work roll 710 so that it does not move in the axial direction.

[0108] Furthermore, to account for emergencies such as the application of unexpectedly excessive thrust resistance, relief valves 811 and 812 are provided between pilot check valves 821 and 822 and the operating-side shift cylinders 715A and 715B and the driving-side shift cylinders 715C and 715D, ensuring that the pressure increase in the piping is kept within the machine's allowable pressure.

[0109] Note that the hydraulic system shown in Figure 7 only illustrates the part illustrating the present invention, and flow control valves, check valves, etc., may be added as needed.

[0110] Figure 8 shows the structure around the shift cylinder on the operating and driving sides. In Figure 8, for the purpose of explaining the operation, the diagram only illustrates the case where the piping on the rod side near the plate on the operating side and the piping on the rod side near the opposite plate on the driving side are connected, but the same applies to other piping connections.

[0111] In Figure 8, the center position of the distance between the support positions of the operating side and the driving side is indicated by line M, and F sde The force with which the drive-side entry-side shift cylinder 715D supports the upper drive-side bearing housing 712B is F swe The force with which the operating side entry shift cylinder 715A supports the upper operating side bearing housing 712A is L a F is the distance between the support positions of the operating side and the driving side. tr This is the thrust force acting on the upper work roll 710. Here, we assume that a thrust force is acting in the operating direction.

[0112] In the state shown in Figure 8, F swe and F sde These are F tr The force F is / 4, although not shown, when the exit side operating side exit shift cylinder 715B supports the upper operating side bearing housing 712A. swd And the force F that the drive-side exit shift cylinder 715C supports the upper drive-side bearing housing 712B sdd F tr / 4, and the sum of these four is F tr Therefore, the thrust force F tr I support this.

[0113] Figure 9 shows a scenario in Figure 8 where, during rolling, the upper work roll 710 is heated by the rolled material 5, the radial bearings 790A and 790B generate heat when rotating under load, and the distance La between the support positions on the operating and driving sides expands by ΔLa due to ambient temperature changes, etc.

[0114] As shown in Figure 9, when the distance La between the support positions of the operating and driving sides changes by ΔLa, the support position of the driving side moves ΔLa / 2 closer to the anti-plate, and hydraulic fluid flows from the anti-plate side of the driving side shift cylinders 715C and 715D to the plate side of the operating side shift cylinders 715A and 715B, causing the support position of the operating side to move ΔLa / 2 closer to the anti-plate.

[0115] In other words, in the hydraulic circuit of this embodiment, even if the distance La between the support positions La on the operating side and the drive 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. Therefore, 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 drive side shift cylinders 715C and 715D remain the same, so the balance of the total support force does not change.

[0116] Therefore, line M, which is the center position of the distance between the support positions on the operating side and the drive side, remains the center position of the distance between the support positions on the operating side and the drive side even if La changes by ΔLa. In other words, since line M is close to the center position of the rolled material 5, even if there is thermal expansion, only a very small amount of axial slip occurs between the upper work roll 710 and the rolled material 5, and does not hinder rolling.

[0117] Here, we have shown the case where thermal expansion occurs, but even in the case of thermal contraction, the support force does not change, and the position of line M also does not change.

[0118] Next, a modified example of this embodiment will be described using Figure 10. Figure 10 is a plan view illustrating the details of the upper work roll portion of the rolling mill in the modified example of Embodiment 1.

[0119] Figure 10 shows an example configuration in which, on the operating side, a shift block 712A1 containing upper work roll bending cylinders 740 and 741 is connected to the operating side shift cylinders 715A and 715B, and on the driving side, a shift block 712B1 containing upper work roll bending cylinders 740 and 741 is connected to the driving side shift cylinders 715C and 715D.

[0120] Even when using such shift blocks 712A1 and 712B1, the thrust reaction force can be made the same on the operating side and the driving side, similar to the configuration shown in Figure 7, in which the input fixing member 702 and the output fixing member 703 contain the bending cylinders 740 and 741.

[0121] Furthermore, by adopting the configuration shown in Figure 7 and adding pressure measuring devices to the secondary side of the pilot check valves 821 and 822, the thrust force acting on the roll can be measured with high accuracy.

[0122] Next, the effects of this embodiment will be described.

[0123] According to the rolling mill of Embodiment 1 of the present invention described above, after the hydraulic circuit has maintained the axial position of the upper work roll 710, if the external force acting on the upper work roll 710 causes only one of the hydraulic cylinders among the drive-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 hydraulic cylinder among the drive-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.

[0124] After maintaining the axial position of the mill roll, when the direction of the axial external force acting on the mill roll changes, even if the play in one of the hydraulic cylinders—the operating cylinder and the driving cylinder—is eliminated first, when one hydraulic cylinder is pushed and loses its support and moves, the other hydraulic cylinder moves by the same amount in the opposite direction to the first hydraulic cylinder. This action is repeated continuously, and eventually the remaining play is eliminated, and the other hydraulic cylinder also becomes supportive. This prevents a large axial external force from continuously acting on one hydraulic cylinder until the play in the other hydraulic cylinder is eliminated.

[0125] In other words, even if thermal expansion occurs, the direction of thrust resistance 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, or between the bearing housing and the shift device, as long as an excessive thrust resistance force does not act, the thrust reaction force of the operating-side shift cylinders 715A, 715B and the driving-side shift cylinders 715C, 715D themselves can be made the same, and it is possible to avoid the pressure inside the hydraulic cylinder rising above the set pressure of the relief valves 811, 812. Therefore, excessive load does not act on the support parts such as the operating-side bearings and driving-side bearings of the mill roll, and the lifespan can be improved. For example, if the lifespan of the bearing is Lh and the load is Pl, then in the case of a roller bearing, Lh ∝ (1 / Pl) 10 / 3 Because of this relationship, if we substitute 1 / 2 for Pl, Lh becomes 10, so the bearing life can be extended by 10 times compared to when thrust force is maintained on one side.

[0126] Furthermore, in conventional configurations, if the pressure rises above the relief valve set pressure, hydraulic fluid leaks out from the secondary side of the pilot check valve, causing a shift position shift and requiring frequent shift position adjustments. However, in this embodiment, the pressure rise above the relief valve 811 and 812 set pressure can be suppressed, thus eliminating the need for frequent shift position adjustments. In other words, complex pressure measuring devices and adjustments to the inflow and outflow oil volume adjustment section, as in conventional systems, become unnecessary, resulting in a simpler device configuration. In addition, since this can be achieved simply by ON / OFF control of the electromagnetic switching valve 810 without complex control devices, the device configuration of the control system can also be simplified.

[0127] 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 thrust force support may change before and after the relief valve is activated. Furthermore, 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 can 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 determined by multiplying the area of ​​both pressure chambers of the cylinder, so it has been found that if it is uncertain whether the cylinder supporting the thrust force is on one side or both sides, it may be difficult to accurately determine the thrust force.

[0128] 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 the relief valves 811 and 812 are activated. Therefore, the thrust force can be accurately determined from the pressure measurement results on the secondary side of the pilot check valves 821 and 822.

[0129] Furthermore, a rolling mill in which the upper and lower rolls are tilted in opposite directions to form a cross shape has high plate crown / plate shape control capability, but because a large thrust force acts between the rolled material 5 and the upper work roll 710, there was a limit to the load capacity depending on the strength of the bearings and roll ends that receive the thrust force.

[0130] In particular, under severe load conditions, grease cannot be used for bearing lubrication, and it becomes necessary to employ oil lubrication such as circulating oil supply. However, when oil lubrication such as circulating oil supply is adopted, the equipment becomes complex and the equipment costs become high.

[0131] In contrast, by adopting the configuration of the above embodiment, if the applied load can be halved, a simple grease lubrication system can be used for the machinery, which has the advantage of keeping equipment and operating costs low. Furthermore, 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 the rolling of hard materials as well.

[0132] The above explanation describes a case where the bearing is subjected to both bending and thrust forces. However, 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 bearing is selected as appropriate, and even in those structures, adopting the configuration of this embodiment can reduce the load acting on it by half, leading to an extension of the lifespan of roll support parts such as bearings.

[0133] Furthermore, vertical resistance in the thrust bearing portion affects the measured rolling load. If the thrust force support device is located on only one side, it can also cause differential load. By adopting the configuration of this embodiment, the thrust force can be made the same on both the operating and driving sides, so the differential load can be minimized, although this also depends on the friction coefficient of the thrust bearing portion.

[0134] Therefore, by adopting the configuration of this embodiment, it is possible to create a structure in which the resistance to movement of the thrust bearing portion in the rolling direction is reduced. This makes it possible to reduce the resistance when changing the inclination during rolling.

[0135] Furthermore, the hydraulic circuit is configured such that the drive-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. The drive-side outlet plate-side hydraulic oil chamber 923a and the operating-side outlet plate-side hydraulic oil chamber 925b are connected by pressure lines 807 and 808, and the drive-side outlet plate-side hydraulic oil chamber 923b and the operating-side outlet plate-side hydraulic oil chamber 925a are connected by pressure lines 805 and 806. This configuration ensures that the amount of hydraulic oil moving through the piping remains constant.

[0136] Furthermore, the hydraulic circuit is configured such that when either the drive-side shift cylinders 715C, 715D or the operating-side shift cylinders 715A, 715B move a predetermined stroke, the other hydraulic cylinder of the drive-side shift cylinders 715C, 715D or the operating-side shift cylinders 715A, 715B also moves a predetermined stroke in the opposite direction without changing the amount of oil in the connected pressure lines 805, 806, 807, 808. This allows both the drive-side and operating-side to move with the same stroke, preventing the pressure in the piping from becoming so high as to exceed the relief valve 811, 812 set pressure, and enabling the thrust force to be supported by applying force in the same direction to the mill roll on both the drive-side and operating-side.

[0137] Furthermore, the drive-side shift cylinders 715C, 715D and the operating-side shift cylinders 715A, 715B are double-rod cylinders, the drive-side outlet plate-side hydraulic oil chamber 923a and the drive-side outlet plate-side hydraulic oil chamber 923b have the same cross-sectional area in the direction to which the hydraulic oil force is applied, the operating-side outlet plate-side hydraulic oil chamber 925a and the operating-side outlet plate-side hydraulic oil chamber 925b have the same cross-sectional area in the direction to which the hydraulic oil force is applied, and the drive-side outlet plate-side hydraulic oil chamber 923a and the operating-side outlet plate-side hydraulic oil chamber 925b are connected to pressure line 8 The connection is made between 07 and 808, and the hydraulic oil chamber 923b on the drive side, exit side, and reverse side of the plate is connected to the hydraulic oil chamber 925a on the operating side, exit side of the plate by pressure lines 805 and 806. This makes it possible to equalize the force supporting the thrust force acting on the mill roll in the operating direction and the force supporting the thrust force in the drive direction. When the bearings on the operating and drive sides of the mill roll are of the same specifications, this maximizes the lifespan of the bearings and other support parts, and reduces wear on various parts due to the load. Furthermore, by using two rods, the bearing housing connection between the hydraulic cylinder on the drive side and the hydraulic cylinder on the operating side can be positioned closer to the plate. This allows for symmetrical construction of the structure around the bearing housing connection between the drive and operating sides, enabling structural commonality and resulting in a simpler device compared to other embodiments described later.

[0138] Furthermore, the drive-side shift cylinders 715C, 715D and the operating-side shift cylinders 715A, 715B are each provided on the inlet and outlet sides of the rolling mill, and pressure lines 805, 806, 807, and 808 are provided to connect the corresponding hydraulic fluid chambers on the inlet and outlet sides. This makes it possible to equalize the support forces on the inlet and outlet sides of the hydraulic cylinders, thereby preventing a moment from acting on the bearing housing, which in turn prevents rotation of the mill roll in the horizontal plane, and also allows for equal support forces on the inlet and outlet sides of the rolled material 5 with a simple structure.

[0139] Furthermore, the system includes a control device 80 that controls the drive of multiple hydraulic cylinders. The control device 80 drives the drive-side shift cylinders 715C, 715D and the operating-side shift cylinders 715A, 715B, enabling the upper work roll 710 to be shifted axially, thereby allowing the mill roll to be shifted automatically in the axial direction.

[0140] Furthermore, it is equipped with a horizontal actuator to adjust the angle of each roll horizontally. When the mill roll is tilted at an arbitrary angle relative to the plate, the thrust force acting on the mill roll increases. However, this large thrust force is supported equally by the operating side and the driving side, and the support forces on the input and output sides are made equal with a simple structure, so that no moment acts on the bearing housing, and the support force per hydraulic cylinder can be reduced to 1 / 4.

[0141] Furthermore, it is possible to use a single hydraulic cylinder with two rods, where the diameters of the two rods are different, meaning that the cross-sectional areas of the two hydraulic fluid chambers are different.

[0142] In this case, by matching the cross-sectional area of ​​the hydraulic oil chambers on the drive side near the plate and the operating side near the plate and connecting them with piping, and by matching the cross-sectional area of ​​the drive side near the plate and the operating side near the plate and connecting them with piping, the drive side near the plate and the operating side near the plate, and the drive side near the plate and the operating side near the plate, can each apply the same force as a thrust reaction force, thereby halving the thrust reaction force and making it possible to have the same supporting force on the drive side and the operating side, and maximizing the lifespan of roll support parts such as bearings.

[0143] Furthermore, if it is desired to selectively increase the force supporting the thrust force in the operating direction, it is possible to choose to create a difference in the rod diameter such that the cross-sectional area of ​​the hydraulic fluid chambers on the operating side (near the reverse plate) and the driving side (near the plate) is larger than the cross-sectional area of ​​the hydraulic fluid chambers on the operating side (near the plate) and the driving side (near the reverse plate).

[0144] <Example 2> The rolling mill and rolling method of Embodiment 2 of the present invention will be explained with reference to Figure 11. Figure 11 is a plan view illustrating the details of the upper work roll portion of the rolling mill of Embodiment 2.

[0145] In the rolling mill of this embodiment shown in Figure 11, the drive-side exit shift cylinder 715C1, the drive-side in-side shift cylinder 715D1, the operating-side in-side shift cylinder 715A1, and the operating-side exit shift cylinder 715B1 are all single-rod cylinders, and the orientation of the single rods 923c1 and 925c1 (only the exit side is shown as an example) of each cylinder is the same and the operating side direction to Turn It is positioned.

[0146] For this purpose, the operating-side in-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 out-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.

[0147] Furthermore, the drive-side outlet plate-side hydraulic oil chamber 923a1 and the operating-side outlet plate-side hydraulic oil chamber 925b1 are connected by drive-side plate-side pressure lines 807A and 807B, and the cross-sectional area in the direction to which the hydraulic fluid force is applied (area of ​​pistons 923d1 and 925d1) is the same. Additionally, the drive-side outlet plate-side hydraulic oil chamber 923b1 and the operating-side outlet plate-side hydraulic oil chamber 925a1 are connected by pressure lines 805A and 805B and the operating-side plate-side pressure line 806, and the cross-sectional area in the direction to which the hydraulic fluid force is applied (area of ​​pistons 923d1 and 925d1) is the same.

[0148] With this configuration, similar to the configuration shown in Figure 7 in Example 1, even if there is a thermal deformation of ΔLa, the drive side and the operating side move to opposite sides by ΔLa / 2 each across the line M, making it possible to support the object with equal force on both the drive side and the operating side.

[0149] In other words, when the roll set 710A is moved in the drive direction while receiving a thrust resistance force in the operating direction from the roll set 710A, and after the position of the roll set 710A is set, a thrust resistance force in the drive direction acts on the roll set 710A due to changes in conditions such as the rotation of the rolling mill rolls, and when only the roll set 710A moves in the drive direction, the thrust resistance force can be supported equally on both the drive side and the operating side, so the pressure will not rise above the set pressure of the relief valves 811 and 812.

[0150] Even in this case, relief valves 811 and 812 may be provided on the secondary side of pilot check valves 821 and 822 to take into consideration emergencies such as the application of unexpectedly excessive thrust resistance.

[0151] The other configurations and operations are substantially the same as those of the rolling mill and rolling method described in Example 1 above, and details are omitted.

[0152] In the rolling mill and rolling method of Embodiment 2 of the present invention, substantially the same effects as those of the rolling mill and rolling method of Embodiment 1 described above can be obtained.

[0153] Furthermore, in this embodiment, the same hydraulic cylinder can be used on both the operating and driving sides, but the mechanical devices surrounding the cylinder, such as the shift mechanism, have different structures on the operating and driving sides. Although this makes the equipment more complex, it allows for a smaller protrusion of the shift mechanism, including the shift cylinder, from the operating side housing compared to the configuration in Embodiment 1. Therefore, this configuration is suitable for use when it is difficult to enlarge the shift mechanism due to connections with the rearrangement device on the operating side.

[0154] Specifically, the roll rearrangement device on the operating side can be positioned close to the rolling mill, and the setup can be similar to that of a normal work roll shift where the shift cylinder is only installed on the operating side. Therefore, there is no need to expand the space on the operating side, resulting in an economical space configuration.

[0155] Additionally, if there are space constraints on the drive side due to the device, it is possible to have the head side of the operating-side shift cylinders 715A1 and 715B1 be on the side closer to the plate, and the head side of the drive-side shift cylinders 715C1 and 715D1 be on the side closer to the plate.

[0156] The configuration of this embodiment is preferable when securing space on the operating side, regardless of whether it is hot rolling or cold rolling.

[0157] In this embodiment, the configuration of the single-rod cylinder is not limited to the form shown in Figure 11. The drive-side exit shift cylinder 715C1 and the drive-side in-side shift cylinder 715D1 can also be configured to support the drive-side arms 714C and 714D via transmission members, similar to the operating-side in-side 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 provided as shown in Figure 14, which will be described later.

[0158] By arranging the shift cylinder so that the rod faces outward, the rolling mill becomes more compact. Space can be secured for roll rearrangement on the operating side, and similarly, space can be secured on the drive side as well. Furthermore, since 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 create a simpler device configuration.

[0159] <Example 3> The rolling mill and rolling method of Embodiment 3 of the present invention will be described with reference to Figures 12 and 13. Figures 12 and 13 are plan views illustrating the details of the upper work roll portion of the rolling mill of Embodiment 3.

[0160] In the rolling mill of this embodiment shown in Figures 12 and 13, a pressure line 805B1 branched from pressure line 803 is connected to the drive-side inlet-side anti-plate side hydraulic oil chamber 833b of the drive-side inlet-side shift cylinder 833 of both rods, and a pressure line 805B2 branched from pressure line 803 is connected to the operating-side inlet-side plate side hydraulic oil chamber 830a of the operating-side inlet-side shift cylinder 830 of both rods.

[0161] Furthermore, the drive-side inlet-side flip-plate hydraulic oil chamber 833b and the drive-side outlet-side flip-plate hydraulic oil chamber 832b of the drive-side outlet-side shift cylinder 832 of both rods are connected by a pressure line 823, the drive-side outlet-side flip-plate hydraulic oil chamber 832b and the operating-side outlet-plate hydraulic oil chamber 831a of the operating-side outlet-side shift cylinder 831 of both rods are connected by a pressure line 824, and the operating-side outlet-plate hydraulic oil chamber 831a and the operating-side inlet-side plate hydraulic oil chamber 830a are connected by a pressure line 825.

[0162] For the purpose of explaining the operation, only the case where the piping on the rod side near the operating plate and the rod side near the reverse plate on the driving side are connected is described. However, the rod side near the reverse plate on the operating side (operating side inlet / reverse plate side hydraulic oil chamber 830b, operating side outlet / reverse plate side hydraulic oil chamber 831b) and the rod side near the plate on the driving side (driving side inlet / plate side hydraulic oil chamber 833a, driving side outlet / plate side hydraulic oil chamber 832a) are similarly connected by piping.

[0163] In Figures 12 and 13, we assume the same case as in Figure 8, where a thrust force is acting in the direction of the operator.

[0164] Figure 13 shows the state in Figure 12 where the upper work roll 710 has an arbitrary inclination angle with respect to the rolled material 5. The center of the plate width at the plate passage position is approximately the same as the center of the rolling mill, and here the inclination angle θ is centered on the center position in the plate width direction of the rolling mill. c They are arranged in a counterclockwise direction.

[0165] In Figure 13, the tilt angle θ is shown with pilot check valves 821 and 822 activated during rolling. c When a support is provided, if the distance from the center position of the rolling mill to the thrust force application position is the same on the operating side and the drive side, then the support position on the entry side of the operating side is ΔL we Only the support position on the board side is ΔL. wd It moves only towards the anti-plate. Furthermore, the support position on the drive side's entry side is ΔL de Only the back plate is closer, and the support position on the drive side is ΔL dd Move only towards the board.

[0166] These movements cause the hydraulic fluid to move within the pressure lines 805B1, 805B2, 823, 824, and 825, but the total amount of hydraulic fluid at the outlet (secondary side) of the pilot check valves 821 and 822 does not change.

[0167] Since both the rod side on the operating side near the plate and the rod side on the driving side near the plate are connected by pressure lines, the total amount of hydraulic fluid on the outlet (secondary side) of pilot check valves 821 and 822 remains unchanged.

[0168] On the other hand, the upper work roll 710 can shift and take on various positions, and even when it does not shift, the distance from the rolling mill center to the thrust force application position may differ between the operating side and the driving side.

[0169] In this case, the distance between the support positions on the operating and driving sides changes slightly due to the tilt of the upper work roll 710. This change causes a flow of hydraulic fluid between the operating and driving sides, similar to when the distance between the support positions changes due to thermal expansion of the upper work roll 710. However, ΔL we ,ΔL wd ,ΔL de ,ΔL dd Although each of these values ​​will shift slightly from the geometrically determined thrust force application point due to the inclination of the upper work roll 710, there will be no significant change.

[0170] Thus, in a mill that shifts the 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 an excessive load that would rise above the set pressure of the relief valves 811 and 812 during the tilting process.

[0171] Furthermore, since the tilting involves only a slight displacement around line M, the upper work roll 710 can be tilted with almost no slippage between the rolled material 5 and the upper work roll 710.

[0172] After determining the shift position of the upper work roll 710, or even in a mill without a shift mechanism, after determining the axial position of the upper work roll 710 using the configuration of this embodiment, even if the inclination angle is changed during rolling, and even if the pilot check valves 821 and 822 remain engaged, no excessive force will be applied to the shift device.

[0173] The displacement in the roll axis direction due to the change in tilt angle is very small because the difference between the center of the distance between support positions and the center of the tilt (rolling mill center position) is small. When this very small displacement occurs, the total amount of hydraulic fluid on the secondary side of pilot check valves 821 and 822 does not change.

[0174] Furthermore, in the configuration of other embodiments as shown in Figure 11, even if the rolls are tilted relative to the rolled material 5 during rolling, if the total amount of hydraulic fluid on the secondary side of the pilot check valves 821 and 822 does not change, the support forces on the operating and driving sides of each cylinder can be made equal.

[0175] The other configurations and operations are substantially the same as those of the rolling mill and rolling method described in Example 1 above, and details are omitted.

[0176] In the rolling mill and rolling method of Embodiment 3 of the present invention, substantially the same effects as those of the rolling mill and rolling method of Embodiment 1 described above can be obtained.

[0177] <Example 4> The rolling mill and rolling method of Embodiment 4 of the present invention will be described with reference to Figure 14. Figure 14 is a plan view illustrating the details of the upper work roll portion of the rolling mill of Embodiment 4. Although only the exit side is shown in Figure 14, the inlet side has a similar structure, and details are omitted.

[0178] In the rolling mill of this embodiment shown in Figure 14, the drive-side exit shift cylinder 935C and the operating-side exit shift cylinder 935B are single-rod cylinders. The rods 943c of the drive-side exit shift cylinder 935C and the rod 945c of the operating-side exit shift cylinder 935B are oriented in opposite directions, and are on the rolled material 5 side, respectively. direction to Turn It is positioned.

[0179] Furthermore, it is equipped with two first intermediate cylinders 971 and second intermediate cylinders 973 on one rod. These first intermediate cylinders 971 and second intermediate cylinders 973 are dummy cylinders and do not have a specific object to press against.

[0180] Furthermore, the drive-side outlet rod-side hydraulic oil chamber 943a of the drive-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 drive-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.

[0181] 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.

[0182] Furthermore, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the drive-side outlet rod-side hydraulic fluid chamber 943a and the drive-side outlet head-side hydraulic fluid chamber 943b, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the operator-side outlet rod-side hydraulic fluid chamber 945a and the operator-side outlet head-side hydraulic fluid chamber 945b, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the rod-side hydraulic fluid chamber 971b and the head-side hydraulic fluid chamber 971a, and the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the rod-side hydraulic fluid chamber 973b and the head-side hydraulic fluid chamber 973a are the same for all cylinders.

[0183] In this case as well, when the drive arm 714C moves to the drive side by half of the remaining play, the operating arm 714B moves to the operating side by half of the remaining play, and the amount of hydraulic fluid on the secondary side of the pilot check valves 821 and 822 does not change.

[0184] Furthermore, the cross-sectional area in which the hydraulic fluid in the operating-side shift cylinder 935B and the driving-side shift cylinder 935C comes into contact is A wr dh , pressure is p wr >p dh And so, A wr ×p wr =Ad h ×p dh As a result of this relationship, the support forces of the drive arm 714C and the operating arm 714B are the same.

[0185] Similarly, when a thrust force is applied to the roll set 710A in the operating direction, the same thrust reaction force is generated on both the drive rod side and the operating head side. Therefore, in the configuration of this embodiment, the supporting forces of the thrust force on the operating side and the drive side can be halved.

[0186] The other configurations and operations are substantially the same as those of the rolling mill and rolling method described in Example 1 above, and details are omitted.

[0187] In the rolling mill and rolling method of Example 4 of the present invention, substantially the same effects as those of the rolling mill and rolling method of Example 1 described above can be obtained.

[0188] Furthermore, in the configuration of this embodiment 4, the bearing housing connection portion of the hydraulic cylinder on the drive side and the bearing housing connection portion of the hydraulic cylinder on the operating side can be positioned closer to the rolled material 5. This allows the structure around the bearing housing connection portion to be symmetrical on the drive side and the operating side, enabling structural commonality and resulting in a simpler device.

[0189] Furthermore, since the length of the hydraulic cylinder is shorter compared to the configuration of both rods as in Example 1, the protrusion on the operating side of the shift device can be reduced, making it possible to secure space for the roll rearrangement device.​

[0190] The piston 973d of the second intermediate cylinder 973, the piston 943d of the drive-side exit shift cylinder 935C, the piston 945d of the operating-side exit shift cylinder 935B, and the piston 971d of the first intermediate cylinder 971 can have the same cross-sectional area, but they do not need to be the same; it is sufficient that the ratio of the cross-sectional area of ​​the head / rod side of the piston of each cylinder is the same.

[0191] <Other> It should be noted that the present invention is not limited to the embodiments described above, and includes various modifications. The embodiments described above are explained in detail for the purpose of clearly illustrating the present invention, and are not necessarily limited to those having all the configurations described.

[0192] Furthermore, it is possible to replace parts of the configuration of one embodiment with parts of the configuration of another embodiment, and it is also possible to add parts of the configuration of another embodiment to the configuration of one embodiment. In addition, it is possible to add, delete, or replace parts of the configuration of each embodiment with parts of other configurations.

[0193] For example, although we have described a rolling mill in which the mill rolls shift in the direction of the roll axis, the present invention also applies to rolling mills equipped with hydraulic cylinders that fix the axial position, i.e., rolling mills that do not shift in the axial direction. [Explanation of symbols]

[0194] 1…Rolling equipment 5… Rolled material 30…Stand 1 (Rolling Mill) 40…Second stand (rolling mill) 50…Third stand (rolling mill) 60…Stand 4 (Rolling Mill) 70…Stand 5 (Rolling Mill) 80...Control device 90... Hydraulic system 700... Housing 702...Inlet fixing member 703...Outlet fixing member 705A, 705B, 705E, 705F, 706C, 706D… Hydraulic cylinders (horizontal actuators) 710... Upper work roll (mill roll) 710A... Roll Set 711... Lower work roll (mill roll) 712... Upper work roll bearing housing 712A…Upper operating side bearing box 712A1... Shift Block 712B…Upper drive side bearing housing 712B1... Shift Block 713... Lower work roll bearing housing 713A, 713B… Bearing housing 714A, 714B… Operating arm 714C, 714D… Drive side arm 715... Shift cylinder (hydraulic cylinder) 715A, 715A1, 830... Operating side entry side shift cylinder (hydraulic cylinder, operating side hydraulic cylinder) 715A2, 715B2… Transmission members 715B, 715B1, 831, 935B... Operating side exit shift cylinder (hydraulic cylinder, operating side hydraulic cylinder) 715C, 715C1, 832, 935C... Drive-side exit-side shift cylinder (hydraulic cylinder, drive-side hydraulic cylinder) 715D, 715D1, 833... Drive-side intake-side 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 reinforcing roll (mill roll) 731... Lower reinforcing roll (mill roll) 732... Upper reinforced roll bearing housing 733... Lower reinforced roll bearing housing 740, 741, 742, 743… Upper work roll bending cylinder 744, 745, 746, 747… Lower work roll bending cylinder 750, 751… Upper and intermediate roll bending cylinders 752, 753… Lower intermediate roll bending cylinder 760... Upper work roll bearing housing play removal cylinder 762...Lower work roll bearing housing play removal cylinder 771... Upper intermediate roll bearing housing play-free cylinder 773...Lower intermediate roll bearing housing play-free cylinder 780... Upper reinforced roll bearing housing cylinder with play control 782... Lower reinforced roll bearing housing play-free cylinder 790A, 790B... Radial bearings 800A, 801… Pressure lines 800B, 802… Tank Line 803, 804… pressure lines 805... Drive side, anti-plate side pressure line (piping) 805A, 805B, 805B1, 805B2, 823, 824, 825… Pressure lines (piping) 805C1, 805C2…Intermediate rod pressure line (piping) 806...Operating side plate side pressure line (piping) 807... Drive side plate side pressure line (piping) 807A, 807B… Drive side plate side pressure line 807C1, 807C2…Intermediate rod pressure line 808...Operating side, counter-plate side pressure line (piping) 810... Solenoid directional control valve 811, 812… Relief valve 821, 822… Pilot check valve 830a...Operation side entry side plate side hydraulic oil chamber 830b…Operation side inlet side opposite plate side hydraulic oil chamber 831a...Operation side outlet plate side hydraulic oil chamber 831b…Operation side outlet side opposite plate side hydraulic oil chamber 833a...Drive side intake plate side hydraulic oil chamber 833b... Drive side, intake side, reverse 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... Drive side outlet side reciprocating plate side hydraulic oil chamber (drive side reciprocating plate side hydraulic oil chamber) 923c, 925c... Rods 923c1…Single rod (drive side hydraulic cylinder rod) 923d, 923d1, 925d, 925d1, 943d, 945d, 971d, 973d… piston 924a...Drive side intake plate side hydraulic oil chamber (drive side plate side hydraulic oil chamber) 924b...Driving side intake side reversal plate side hydraulic oil chamber (Driving side reversal plate side hydraulic oil chamber) 925a, 925a1...Operation side outlet plate side hydraulic oil chamber (operation side plate side hydraulic oil chamber) 925b, 925b1...Operating side outlet side opposite plate side hydraulic oil chamber (operating side opposite plate side hydraulic oil chamber) 925c1…Single rod (operating side hydraulic cylinder rod) 926a...Operation side inlet side plate side hydraulic oil chamber (operation side plate side hydraulic oil chamber) 926b...Operating side inlet side opposite plate side hydraulic oil chamber (operating side opposite plate side hydraulic oil chamber) 943a... Drive side exit rod side hydraulic oil chamber (drive side plate side hydraulic oil chamber) 943b...Drive side exit side head side hydraulic oil chamber (drive side reverse plate side hydraulic oil chamber) 943c... Rod (drive-side hydraulic cylinder rod) 945a...Operating side outlet rod side hydraulic oil chamber (operating side plate side hydraulic oil chamber) 945b...Operating side outlet head side hydraulic oil chamber (operating side reversal plate side hydraulic oil chamber) 945c... Rod (operating hydraulic cylinder rod) 971...First intermediate cylinder 971a...Hydraulic oil chamber on the head side 971b...Rod-side hydraulic oil chamber 973... Second intermediate cylinder 973a...Hydraulic oil chamber on the head side 973b...Rod-side hydraulic oil chamber

Claims

1. Mill Roll and, A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A hydraulic circuit is provided which is configured to supply hydraulic fluid to a plurality of hydraulic cylinders, causing the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are both rod cylinders. The hydraulic fluid chamber on the drive side plate and the hydraulic fluid chamber on the drive side reverse plate have the same cross-sectional area in the direction to which the hydraulic fluid force is applied. The hydraulic fluid chamber on the operating side plate and the hydraulic fluid chamber on the operating side reverse plate have the same cross-sectional area in the direction to which the hydraulic fluid force is applied. The hydraulic oil chamber on the drive side plate and the hydraulic oil chamber on the operating side reversing plate are connected by piping, and the hydraulic oil chamber on the drive side reversing plate and the hydraulic oil chamber on the operating side plate are connected by piping. The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. Rolling mill.

2. A mill roll and A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A hydraulic circuit is provided which is configured to supply hydraulic fluid to a plurality of hydraulic cylinders, causing the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are single-rod cylinders. The driving hydraulic cylinder rod and the operating hydraulic cylinder rod are oriented in the same direction. The hydraulic fluid chamber on the drive side plate and the hydraulic fluid chamber on the operating side reverse plate are connected by piping, and the cross-sectional area in the direction to which the hydraulic fluid force is applied is the same. The hydraulic fluid chamber on the drive side and the hydraulic fluid chamber on the operating side are connected by piping, and the cross-sectional area in the direction to which the hydraulic fluid force is applied is the same. The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. Rolling mill.

3. A mill roll and A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A hydraulic circuit is provided which is configured to supply hydraulic fluid to a plurality of hydraulic cylinders, causing the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are single-rod cylinders. The direction of the drive-side hydraulic cylinder rod and the operating-side hydraulic cylinder rod are reversed. Equipped with two or more intermediate cylinders on a single rod, The hydraulic fluid chamber on the drive rod side and the hydraulic fluid chamber on the first intermediate cylinder rod side are connected by piping. The hydraulic fluid chamber on the drive side head and the hydraulic fluid chamber on the second intermediate cylinder head side are connected by piping. The operating rod side hydraulic oil chamber and the second intermediate cylinder rod side hydraulic oil chamber are connected by piping. The hydraulic fluid chamber on the operating head side and the hydraulic fluid chamber on the first intermediate cylinder head side are connected by piping. The ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the drive-side rod-side hydraulic fluid chamber and the drive-side head-side hydraulic fluid chamber, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the operating-side rod-side hydraulic fluid chamber and the operating-side head-side hydraulic fluid chamber, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the first intermediate cylinder rod-side hydraulic fluid chamber and the first intermediate cylinder head-side hydraulic fluid chamber, and the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the second intermediate cylinder rod-side hydraulic fluid chamber and the second intermediate cylinder head-side hydraulic fluid chamber are the same. The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. Rolling mill.

4. In the rolling mill according to any one of claims 1 to 3, The hydraulic circuit is configured such that when either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves a predetermined stroke, the other hydraulic cylinder of the drive-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. Rolling mill.

5. In the rolling mill according to claim 3, The drive-side hydraulic cylinder rod and the operating-side hydraulic cylinder rod are configured to face outward in the axial direction. Rolling mill.

6. In a rolling mill according to any one of claims 1 to 3, 5, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are each provided on the inlet and outlet sides of the rolling mill. The system includes piping that connects the corresponding hydraulic fluid chambers at the inlet and outlet ends. Rolling mill.

7. In a rolling mill according to any one of claims 1 to 3, 5, The system includes a control device that controls the driving of multiple hydraulic cylinders, The control device is configured to drive the drive-side hydraulic cylinder and the operating-side hydraulic cylinder so that the mill roll can be shifted in the axial direction. Rolling mill.

8. In the rolling mill according to any one of claims 1 to 3, 5, The mill roll is equipped with a horizontal actuator for adjusting its angle horizontally. Rolling mill.

9. Mill Roll and, A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A method for rolling a rolled material using a rolling mill comprising a hydraulic circuit configured to supply hydraulic fluid to a plurality of hydraulic cylinders, the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction, and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are both rod cylinders. The hydraulic fluid chamber on the drive side plate and the hydraulic fluid chamber on the drive side reverse plate have the same cross-sectional area in the direction to which the hydraulic fluid force is applied. The operating side plate-side hydraulic fluid chamber and the operating side counter-plate-side hydraulic fluid chamber have the same cross-sectional area in the direction to which the hydraulic fluid force is applied. The hydraulic oil chamber on the drive side plate and the hydraulic oil chamber on the operating side reversing plate are connected by piping, and the hydraulic oil chamber on the drive side reversing plate and the hydraulic oil chamber on the operating side plate are connected by piping, The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. The rolled material is rolled. Rolling method.

10. A mill roll and A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A method for rolling a rolled material using a rolling mill comprising a hydraulic circuit configured to supply hydraulic fluid to a plurality of hydraulic cylinders, the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction, and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are single-rod cylinders. The direction of the drive-side hydraulic cylinder rod and the operating-side hydraulic cylinder rod are the same. The hydraulic fluid chamber on the drive side plate and the hydraulic fluid chamber on the operating side reverse plate are connected by piping, and the cross-sectional area in the direction to which the hydraulic fluid force is applied is the same. The hydraulic fluid chamber on the drive side and the hydraulic fluid chamber on the operating side are connected by piping, and the cross-sectional area in the direction to which the hydraulic fluid force is applied is the same. The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. The rolled material is rolled. Rolling method.

11. A mill roll and A plurality of hydraulic cylinders, including a drive-side hydraulic cylinder provided on the drive side of the mill roll and configured to apply axial force to the mill roll, and an operating-side hydraulic cylinder provided on the operating side of the mill roll and configured to apply axial force, A method for rolling a rolled material using a rolling mill comprising a hydraulic circuit configured to supply hydraulic fluid to a plurality of hydraulic cylinders, the drive-side hydraulic cylinder and the operating-side hydraulic cylinder to move in the axial direction, and to maintain the axial position of the mill roll, The drive-side hydraulic cylinder and the operating-side hydraulic cylinder are single-rod cylinders. The direction of the drive-side hydraulic cylinder rod and the operating-side hydraulic cylinder rod are reversed. Equipped with two or more intermediate cylinders on a single rod, The hydraulic fluid chamber on the drive rod side and the hydraulic fluid chamber on the first intermediate cylinder rod side are connected by piping. The hydraulic fluid chamber on the drive side head and the hydraulic fluid chamber on the second intermediate cylinder head side are connected by piping. The hydraulic fluid chamber on the operating rod side and the hydraulic fluid chamber on the second intermediate cylinder rod side are connected by piping. The hydraulic fluid chamber on the operating head side and the hydraulic fluid chamber on the first intermediate cylinder head side are connected by piping. The ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the drive-side rod-side hydraulic fluid chamber and the drive-side head-side hydraulic fluid chamber, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the operating-side rod-side hydraulic fluid chamber and the operating-side head-side hydraulic fluid chamber, the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the first intermediate cylinder rod-side hydraulic fluid chamber and the first intermediate cylinder head-side hydraulic fluid chamber, and the ratio of the cross-sectional area in the direction to which the hydraulic fluid force is applied between the second intermediate cylinder rod-side hydraulic fluid chamber and the second intermediate cylinder head-side hydraulic fluid chamber are the same. The hydraulic circuit is configured such that, after the hydraulic circuit has maintained the axial position of the mill roll, if an external force acting on the mill roll causes only one of the hydraulic cylinders, either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder, to apply axial force to the mill roll, the other hydraulic cylinder of the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves in the opposite direction to the other hydraulic cylinder. The rolled material is rolled. Rolling method.

12. In the rolling method according to any one of claims 9 to 11, The hydraulic circuit is configured such that when either the drive-side hydraulic cylinder or the operating-side hydraulic cylinder moves a predetermined stroke, the other hydraulic cylinder of the connected piping also moves in the opposite direction to the predetermined stroke without changing the amount of oil in the piping, thereby rolling the rolled material. Rolling method.

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