Rolling mill and rolling method

Abstract

The present invention is provided with: a plurality of hydraulic cylinders including drive-side displacement cylinders (715C), (715D) and operation-side displacement cylinders (715A), (715B) configured so as to apply an axial force to an upper work roll (710); and a hydraulic circuit configured to supply hydraulic oil to the plurality of hydraulic cylinders so that the drive-side displacement cylinders (715C), (715D) and the operation-side displacement cylinders (715A), (715B) move in the axial direction, and maintain the position of the upper working roll (710) in the axial direction, the hydraulic circuit being configured to supply hydraulic oil to the plurality of hydraulic cylinders so that the drive-side displacement cylinders (715C), (715D) and the operation-side displacement cylinders (715A), (715B) move in the axial direction, after the position of the upper working roll (710) in the axial direction is maintained by the hydraulic circuit. When only one of the hydraulic cylinders of the drive-side displacement cylinders (715C, 715D) and the operation-side displacement cylinders (715A, 715B) applies an axial force to the upper work roll (710) due to an external force applied to the upper work roll (710), the other hydraulic cylinder moves in the opposite direction.

Description

Technical Field

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

[0002] Patent document 1 discloses the following contents: an upper working roll; a radial bearing and a thrust bearing which are arranged on the operating side and the driving side of the upper working roll and support the upper working roll; a displacement cylinder which is arranged on the operating side of the upper working roll and applies forces in two directions, namely, the operating side and the driving side, to the thrust bearing; and a displacement cylinder which is arranged on the driving side of the upper working roll and applies forces in two directions, namely, the operating side and the driving side, to the radial bearing, wherein the displacement cylinders each apply forces in the same direction to the radial bearing and the thrust bearing when the upper working roll does not displace axially at least during the rolling process.

[0003] Prior art literature

[0004] Patent Literature

[0005] Patent Document 1: International Publication No. 2022 / 030004 Summary of the invention

[0006] Patent Document 1 discloses a structure in which a roll is displaced on both sides, namely, a driving side and an operating side.

[0007] The rollers of a rolling mill sometimes switch the direction of the thrust acting on the rollers on the driving side or the operating side according to changes in conditions such as rotation. In this case, after the roller position is set, the thrust in the opposite direction acts, and the rollers, more specifically, the parts supporting the rollers, temporarily move away from the arms on the driving side and the operating side supporting the thrust. Therefore, the arms on both sides must be repositioned to support the thrust of the rollers.

[0008] However, the arms have uneven gaps (clearances) in the axial direction at the supporting portions that apply the axial force to the rolls, and as a result, there are cases where only one arm supports the thrust.

[0009] When one arm cannot be fully supported, the pressure in the pipe connected to the hydraulic cylinder that moves the arm becomes higher than the relief valve setting pressure (maximum pressure), and the hydraulic oil is separated from the relief valve, so that the other arm also moves. However, the results of research have shown that since the relief valve setting pressure is high, there is a concern that the life of peripheral equipment such as bearings acting on the load may be reduced.

[0010] This is not limited to the above case. It is clear that even when the rollers thermally expand due to the heat of the heated metal strip, uneven gaps may be generated in the axial direction, so there is a possibility that the same problem as above may occur.

[0011] An object of the present invention is to provide a rolling mill and a rolling method that can improve the life of roll support parts such as bearings on both sides of a roll without causing excessive pressure in a pipe connected to a hydraulic cylinder.

[0012] The present invention includes multiple solutions for solving the above-mentioned problems, but if one example is cited, it includes: a rolling roller; multiple hydraulic cylinders, including a driving side hydraulic cylinder configured to apply an axial force to the above-mentioned rolling roller and arranged on the driving side of the above-mentioned rolling roller, and an operating side hydraulic cylinder configured to apply the above-mentioned axial force and arranged on the operating side of the above-mentioned rolling roller; and a hydraulic circuit, which is configured to supply working oil to the multiple hydraulic cylinders so that the above-mentioned driving side hydraulic cylinder and the above-mentioned operating side hydraulic cylinder move along the above-mentioned axial direction to maintain the above-mentioned axial position of the above-mentioned rolling roller, and the above-mentioned hydraulic circuit is configured so that after the above-mentioned hydraulic circuit maintains the above-mentioned axial position of the above-mentioned rolling roller, when it becomes a state that only one of the hydraulic cylinders of the above-mentioned driving side hydraulic cylinder and the above-mentioned operating side hydraulic cylinder applies the above-mentioned axial force to the above-mentioned rolling roller due to the external force applied to the above-mentioned rolling roller, the hydraulic cylinder of the other of the above-mentioned driving side hydraulic cylinder and the above-mentioned operating side hydraulic cylinder moves in the opposite direction of the above-mentioned one hydraulic cylinder.

[0013] Effects of the Invention

[0014] According to the present invention, the life of the roll support parts such as the bearings on both sides of the roll can be improved without excessive pressure in the pipe connected to the hydraulic cylinder. Other problems, structures and effects than those described above will be clarified by the following description of the embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0015] Figure 1 This is a diagram showing an outline of a rolling facility including a rolling mill according to the first embodiment.

[0016] Figure 2 This is a front view illustrating the outline of the rolling mill according to the first embodiment.

[0017] Figure 3 yes Figure 2 A-A' view.

[0018] Figure 4 This is a schematic diagram for explaining the subject of the present invention.

[0019] Figure 5 This is a schematic diagram for explaining the subject of the present invention.

[0020] Figure 6 This is a schematic diagram for explaining the subject of the present invention.

[0021] Figure 7 This is a plan view illustrating details of the upper work roll portion in the rolling mill of Example 1.

[0022] Figure 8 This is a plan view illustrating details of the upper work roll portion in the rolling mill of Example 1.

[0023] Fig. 9 This is a plan view illustrating details of the upper work roll portion in the rolling mill of Example 1.

[0024] Fig.10 This is a plan view illustrating details of an upper work roll portion in a rolling mill according to a modified example of the first embodiment.

[0025] Fig.11 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 2.

[0026] Fig.12 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 3.

[0027] Fig.13 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 3.

[0028] Fig.14 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 4. DETAILED DESCRIPTION

[0029] Hereinafter, embodiments of a rolling mill and a rolling method according to the present invention will be described with reference to the drawings.

[0030] In addition, in the drawings used in this specification, the same or similar reference numerals are attached to the same or corresponding components, and duplicate description of these components may be omitted.

[0031] In addition, in this specification, thrust resistance refers to the force acting on the roller axial direction of each roller and its bearing box of the rolling mill during rolling or during positive displacement during rolling, and refers to the force acting on the device supporting the force, which has the same meaning as thrust. Thrust reaction force is the force generated from the device supporting the thrust resistance, and refers to the force with the opposite direction and the same magnitude as the thrust resistance.

[0032] <Example 1>

[0033] use Figures 1 to 10 A first embodiment of the rolling mill and the rolling method of the present invention will be described.

[0034] First, use Figures 1 to 3 An overview of a rolling facility including a rolling mill according to the present embodiment will be described. Figure 1 1 is a diagram showing an overview of a rolling facility including a rolling mill according to the first embodiment. Figure 2 is a front view showing an overview of a rolling mill, Figure 3 yes Figure 2A-A' view.

[0035] like Figure 1 As shown, the rolling equipment 1 has a plurality of rolling mills for hot rolling a rolled material 5 into a steel strip, and includes a control device 80 and five stands, namely, a first stand 30 , a second stand 40 , a third stand 50 , a fourth stand 60 , and a fifth stand 70 from the entry side of the rolled material 5 .

[0036] Among them, each of the first stand 30, the second stand 40, the third stand 50, the fourth stand 60, the fifth stand 70 and the portion of the control device 80 that controls each stand corresponds to the rolling mill mentioned in the present invention.

[0037] In addition, the rolling equipment 1 is not limited to Figure 1 A plurality of stands such as the five stands shown may be one stand. In addition, since the temperature of the rolled material during rolling is not limited, a rolling facility that performs cold rolling may also be used.

[0038] Next, use Figure 2 A part of the outline of the rolling mill of the present invention is described. Figure 2 and later Figure 1 The fifth stand 70 shown in the figure is used as an example for explanation, but the rolling mill of the present invention can also be applied to Figure 1 Any of the first base 30, the second base 40, the third base 50, and the fourth base 60 shown.

[0039] exist Figure 2 In FIG. 1 , the fifth stand 70 of the rolling mill of the present embodiment is a six-stage rolling mill for rolling the rolling material 5 , and includes a frame 700 , a control device 80 , and a hydraulic device 90 .

[0040] The stand 700 includes an upper working roll 710 and a lower working roll 711, and an upper intermediate roll 720 and a lower intermediate roll 721 that are supported by contacting the upper working roll 710 and the lower working roll 711. In addition, the stand 700 includes an upper reinforcing roll 730 and a lower reinforcing roll 731 that are supported by contacting the upper intermediate roll 720 and the lower intermediate roll 721.

[0041] The "rolling roll" in the present invention corresponds to any one of the upper working roll 710, the lower working roll 711, the upper intermediate roll 720, the lower intermediate roll 721, the upper reinforcing roll 730, and the lower reinforcing roll 731. In addition, in the case of a rolling mill without intermediate rolls such as the first stand 30 and the second stand 40, the upper and lower working rolls and the upper and lower reinforcing rolls correspond to the "rolling roll".

[0042] In each of these rolls, a radial bearing 790A (see FIG. 1 ) is provided on the operating side of the axial end of the upper working roll 710, which is displaced in the axial direction of the roll together with the upper working roll 710 and receives the load from the roll. Figure 7 ), the radial bearing 790A is supported by the upper operating side bearing box 712A. Similarly, a radial bearing 790B is provided on the driving side, which moves along the axial direction of the roll together with the upper working roll 710 and bears the load from the roll (see Figure 7 ), the radial bearing 790B is supported by the upper drive side bearing box 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 in the vertical direction, but also the thrust acting in the axial direction of the roll.

[0043] Similarly, the lower working roller 711 is provided with bearings (omitted for the convenience of illustration) at the axial ends, on the driving side and the operating side, and these bearings are supported by the lower working roller bearing box 713 (bearing box 713A on the operating side and bearing box 713B on the driving side).

[0044] In this embodiment, the upper working roll 710 is configured to pass through an upper operating side bearing box 712A on the operating side and an upper driving side bearing box 712B on the driving side and pass through Figure 3 Similarly, the lower working roll 711 is also configured to be displaced in the axial direction of the roll via a bearing box 713A on the operating side and a bearing box 713B on the driving side. Figure 3 The displacement cylinder 717 shown in the figure can be displaced along the axial direction of the roller.

[0045] In addition, if Figure 3 As shown, in the upper working roller 710 and the lower intermediate roller 721, a tapered portion is provided at the end of the operating side, and in the lower working roller 711 and the upper intermediate roller 720, a tapered portion is provided at the end of the driving side, the upper working roller 710 and the lower working roller 711 are point symmetrical along the upper and lower sides, and the upper intermediate roller 720 and the lower intermediate roller 721 are point symmetrical along the upper and lower sides.

[0046] return Figure 2 The entry-side fixing member 702 is fixed to the frame 700 on the entry side of the rolled material 5. The exit-side fixing member 703 is fixed to the frame 700 on the exit side of the rolled material 5 so as to face the entry-side fixing member 702.

[0047] In the fifth stand 70, as Figure 2As shown, on both the operating side and the driving side, the upper working roll bearing box 712 is supported by two upper working roll bending cylinders 740, 742 arranged in the axial direction of the roll of the entry side fixing component 702 and two upper working roll bending cylinders 741, 743 arranged in the axial direction of the roll of the exit side fixing component 703.

[0048] Then, by appropriately driving these cylinders, a bending force is applied to the bearing of the upper work roll 710 in the vertical direction.

[0049] Similarly, on both the operating side and the driving side, the lower working roll bearing box 713 is supported by the lower working roll bending cylinders 744, 746 provided on the entry side fixing component 702 and the lower working roll bending cylinders 745, 747 provided on the exit side fixing component 703, and by appropriately driving these cylinders, a bending force is applied to the bearing of the lower working roll 711 in the vertical direction.

[0050] Among these cylinders, the upper work roll bending cylinders 740 and 741 are configured to apply bending force to the bearing of the upper work roll 710 in contact with the rolled material 5 on the vertical direction increasing side (the direction opposite to the rolled material side). In addition, the upper work roll bending cylinders 742 and 743 are configured to apply bending force to the bearing on the vertical direction decreasing side (the direction opposite to the rolled material side) which is the opposite direction of the upper work roll bending cylinders 740 and 741.

[0051] Similarly, the lower work roll bending cylinders 744 and 745 are configured to apply bending force to the bearing of the lower work roll 711 in contact with the rolled material 5 in the vertical direction. In addition, the lower work roll bending cylinders 746 and 747 are configured to apply bending force to the bearing in the opposite direction of the lower work roll bending cylinders 744 and 745.

[0052] Moreover, if Figure 2 As shown, for the purpose of eliminating looseness, two upper working roll bearing box looseness elimination cylinders 760 are provided on the axial direction of the roll at the entry side fixing component 702 of the entry side of the rolled material 5, so that a horizontal force is applied to the upper working roll 710 via the liner plate (omitted in the figure) of the upper working roll bearing box 712, specifically, a pressing force is applied along the rolling direction.

[0053] Similarly, two lower working roll bearing box loosening elimination cylinders 762 are provided on the entry side fixing component 702, so that pressing force is applied to the lower working roll 711 along the rolling direction through the lining plate of the lower working roll bearing box 713.

[0054] These cylinders can apply a desired force to the upper work roll 710 and the like in a direction orthogonal to the roll axial direction.

[0055] Moreover, if Figure 2As shown, as a horizontal actuator for adjusting the angle of the upper working roll 710 in the horizontal direction, there is also a case where a hydraulic cylinder 705A is provided on both the driving side and the operating side of the exit side of the frame 700.

[0056] Similarly, as a horizontal actuator for adjusting the angle of the lower work roll 711 in the horizontal direction, there is a case where a hydraulic cylinder 705B is provided on both the driving side and the operating side of the exit side of the frame 700.

[0057] Moreover, as horizontal actuators for adjusting the angles of the upper intermediate roller 720, the lower intermediate roller 721, the upper reinforcing roller 730 and the lower reinforcing roller 731 in the horizontal direction, there are hydraulic cylinders 705E and 705F provided on the driving side and the operating side of the exit side of the frame 700, and hydraulic cylinders 706C and 706D provided on the driving side and the operating side of the entry side of the frame 700.

[0058] The hydraulic cylinders 705A, 705B, 705E, 705F, 706C, and 706D as these horizontal actuators are not limited to hydraulic cylinders, and other structures such as worm gears may also be used.

[0059] The upper intermediate roller 720 is provided with bearings (not shown) at the end portions in the axial direction on both the driving side and the operating side, and these bearings are supported by the upper intermediate roller bearing box 722. Similarly, the lower intermediate roller 721 is provided with bearings (not shown) at the end portions in the axial direction on both the driving side and the operating side, and these bearings are supported by the lower intermediate roller bearing box 723.

[0060] The upper intermediate roller 720 is supported on both the operating side and the driving side by an upper intermediate roller bending cylinder 750 provided on the entry side fixing component 702 and an upper intermediate roller bending cylinder 751 provided on the exit side fixing component 703. By appropriately driving these cylinders, a bending force is applied to the bearing in the vertical direction.

[0061] The lower intermediate roller 721 is also on the operating side and the driving side, and the lower intermediate roller bearing box 723 is supported by the lower intermediate roller bending cylinder 752 provided on the entry side fixing component 702 and the lower intermediate roller bending cylinder 753 provided on the exit side fixing component 703. By appropriately driving these cylinders, a bending force is applied to the bearing in the vertical direction.

[0062] In addition, if Figure 2As shown, the frame 700 on the exit side is provided with an upper intermediate roller bearing box loose elimination cylinder 771, so that a horizontal force is applied to the upper intermediate roller 720 via the upper intermediate roller bearing box 722. Similarly, the frame 700 on the exit side is provided with a lower intermediate roller bearing box loose elimination cylinder 773, so that a horizontal force is applied to the lower intermediate roller 721 via the lower intermediate roller bearing box 723.

[0063] Moreover, at the axial ends of the upper reinforcing roller 730, bearings (not shown) are provided on both the driving side and the operating side, and these bearings are supported by the upper reinforcing roller bearing box 732. Similarly, at the axial ends of the lower reinforcing roller 731, bearings (not shown) are provided on both the driving side and the operating side, and these bearings are supported by the lower reinforcing roller bearing box 733.

[0064] In addition, if Figure 2 As shown, the frame 700 on the entry side is provided with an upper reinforcing roller bearing box loose elimination cylinder 780, so that a horizontal force is applied to the upper reinforcing roller 730 via the upper reinforcing roller bearing box 732. Similarly, the frame 700 on the entry side is provided with a lower reinforcing roller bearing box loose elimination cylinder 782, so that a horizontal force is applied to the lower reinforcing roller 731 via the lower reinforcing roller bearing box 733.

[0065] The hydraulic device 90 is connected to each hydraulic cylinder such as the above-mentioned bending cylinders and looseness elimination cylinders, displacement cylinders 715, 717, hydraulic cylinders 705A, 705B, 705E, 705F, 706C, 706D, or a pressing cylinder (omitted in the figure) that applies a pressing force to the upper working roll 710 and the lower working roll 711 for rolling the rolled material 5, and the hydraulic device 90 is connected to the control device 80.

[0066] The control device 80 controls the operation of the hydraulic device 90, and controls the driving of each of the above-mentioned bending cylinders by supplying and discharging hydraulic oil to each of the above-mentioned bending cylinders. Figure 7 ) and the operating side outgoing displacement cylinder 715B (refer to Figure 7 ) is driven so that the upper working roller 710 can be displaced axially.

[0067] Next, use Figures 4 to 6 , the characteristic part of the rolling mill and the rolling method in the present invention is described by taking the structure related to the upper working roll 710 among the rolls of the fifth stand 70 as an example. In addition, the lower working roll 711 and the upper intermediate roll 720, the lower intermediate roll 721, the upper reinforcing roll 730 and the lower reinforcing roll 731, and the working rolls, intermediate rolls, and reinforcing rolls of other stands can also be set to the same structure and method, and since their detailed structures are roughly the same, the description is omitted.

[0068] First, use Figures 4 to 6 The subject of the present invention will be described. Figures 4 to 6 This is a schematic diagram for explaining the subject of the present invention.

[0069] exist Figure 4 , the moment when the electromagnetic switching valve 810 is set to b excitation and displaced in the driving side direction, and then the electromagnetic switching valve is set to the neutral position and the hydraulic control check valve is closed to stop the displacement action in the driving side direction is shown.

[0070] Here, for ease of explanation, the roll group 710A headed by the working roll 710 is represented in a simplified integrated form. The displacement cylinders are provided on the entry side and the exit side, but the entry side of the rolled material 5 is substantially the same as the exit side, so only the drive side exit side displacement cylinder 515C and the operating side exit side displacement cylinder 515B are illustrated here.

[0071] like Figure 4 As shown, the roller group 710A is axially supported by the driving side output displacement cylinder 515C via the driving side arm 714C on the driving side, and is axially supported by the operating side output displacement cylinder 515B on the driving side via the operating side arm 714B.

[0072] The driving side output side displacement cylinder 515C is a single-rod cylinder, and has a driving side output side plate side working oil chamber 523a on the piston rod side, a driving side output side reverse plate side working oil chamber 523b on the rodless cavity side, a piston rod 523c and a piston 523d.

[0073] The operating side output side displacement cylinder 515B is also a single-rod type cylinder, and has an operating side output side plate side working oil chamber 525a on the piston rod side, an operating side output side reverse plate side working oil chamber 525b on the rodless cavity side, a piston rod 525c and a piston 525d.

[0074] exist Figure 4 In the hydraulic circuit shown, a hydraulic control one-way valve 821 and an overflow valve 811 are provided on the pressure pipeline 803 , and a hydraulic control one-way valve 822 and an overflow valve 812 are provided on the pressure pipeline 804 .

[0075] The pressure pipe 803 is branched into a driving side reverse plate side pressure pipe 505 and an operating side plate side pressure pipe 506 at the cylinder side of the hydraulic control check valve 821. The driving side reverse plate side pressure pipe 505 is connected to the driving side outlet reverse plate side working oil chamber 523b, and the operating side plate side pressure pipe 506 is connected to the operating side outlet plate side working oil chamber 525a.

[0076] The pressure pipe 804 is branched into a driving side plate side pressure pipe 507 and an operating side reverse plate side pressure pipe 508 at the cylinder side of the hydraulic control check valve 822. The driving side plate side pressure pipe 507 is connected to the driving side outlet plate side working oil chamber 523a, and the operating side reverse plate side pressure pipe 508 is connected to the operating side outlet reverse plate side working oil chamber 525b.

[0077] exist Figure 4 In the structure in FIG. 1 , when the roller group 710A is displaced toward the driving side, the thrust resistance H acting from the roller group 710A on the driving side outlet displacement cylinder 515C and the operating side outlet displacement cylinder 515B is t H t =H d +H w Here, H w is the force acting on the operating side, H d is the force acting on the driving side.

[0078] The operating side output side reverse plate side working oil chamber 525b of the rodless chamber side of the operating side output side displacement cylinder 515B is connected to the driving side output side plate side working oil chamber 523a of the piston rod side of the driving side output side displacement cylinder 515C through the driving side plate side pressure pipeline 507 and the operating side reverse plate side pressure pipeline 508, so the pressure p of each working oil chamber is dr 、p wh equal.

[0079] However, the cross-sectional area A of the piston 525d receiving pressure on the rodless chamber side of the operating side output displacement cylinder 515B is wh and the cross-sectional area A of the piston 523d ​​receiving the pressure on the piston rod side of the drive side output displacement cylinder 515C dr There is an area difference in the middle, so the output Fw of the operating side output displacement cylinder 515B is greater than the output Fd of the driving side output displacement cylinder 515C, and the thrust resistance acting on the displacement cylinder from the roller group 710A becomes H w >H d The thrust resistance H acting on the operating side arm 714B is w becomes a larger value.

[0080] In such a structure, the moment when the roller group 710A moves toward the driving side by itself is considered. Figure 5 The figure shows the moment when the displacement position of the roller group 710A is determined, the hydraulic control check valves 821 and 822 are closed, and the displacement action is stopped, and the roller group 710A moves toward the driving side by itself and first touches the driving side arm 714C.

[0081] On the operating side, there is a residual gap with respect to the operating side arm 714B. In an actual device, since the gaps on the driving side and the operating side are not exactly the same, the residual gap will not be zero.

[0082] Figure 6 Roller group 710A is shown from Figure 5 The roller group 710A further moves toward the driving side, and the remaining gap generated on the operating side becomes 0, and the movement of the roller group 710A toward the driving side stops.

[0083] Here, the area A of the driving side outlet plate side working oil chamber 523a of the driving side outlet side displacement cylinder 515C is shown. dr , the area A of the driving side outlet side counter plate side working oil chamber 523b dh , the area A of the operating side output side plate side working oil chamber 525a of the operating side output side displacement cylinder 515B wr and the area A of the operating side outlet side counter plate side working oil chamber 525b wh In A wh =2A wr And A dh =2A dr relationship situation.

[0084] When the drive side arm 714C is first touched, the drive side output side displacement cylinder 515C is pressed by the thrust resistance of the roller group 710A. dh The pressure is established. wr To become with p dh The same pressure. And, A wr =A wh / 2, so p wh =p wr / 2, in addition, to become p dr =p wh =p wr / 2=p dh / 2.

[0085] Here, since A dh ×p dh =H d +A dr ×p dr So if we import the above relationship, the following relationship will hold:

[0086] A dh ×p dh =H d +(A dh / 2)×(p dh / 2)

[0087] According to this formula, H d =A dh ×pdh × 3 / 4. That is, since pressure also occurs on the piston rod side of the driving side output side displacement cylinder 515C, support can be provided only with 3 / 4 of the pressing force on the rodless chamber side of the driving side output side displacement cylinder 515C.

[0088] Furthermore, it is assumed that the output displacement cylinder 515C on the driving side is d When the pressure is not sufficient, the drive side output displacement cylinder 515C is pressed and moves 1.

[0089] The drive side output displacement cylinder 515C is d When being pressed and moved in the driving side direction, the operating side arm 714B moves to the operating side so as to reduce the remaining gap.

[0090] If the driving side outlet displacement cylinder 515C moves 1 to the driving side, the working oil flows from the driving side outlet side reverse plate side working oil chamber 523b of the driving side outlet displacement cylinder 515C to the operating side outlet plate side working oil chamber 525a of the operating side outlet displacement cylinder 515B. Therefore, although the piston 525d of the operating side outlet displacement cylinder 515B wants to move 2 to the operating side outlet side reverse plate side working oil chamber 525b side, the operating side outlet side reverse plate side working oil chamber 525b side supports the pushing force from the operating side outlet plate side working oil chamber 525a side with half the pressure of the operating side outlet plate side working oil chamber 525a side due to the area difference, and therefore, the operating side outlet side reverse plate side working oil chamber 525b side can only move 1 / 2 corresponding to the movement 1 of the driving side outlet plate side working oil chamber 523a side. Therefore, the operating side outlet plate side working oil chamber 525a side cannot move 2, and only moves 1 / 2. Therefore, the working oil corresponding to (2-1 / 2) of the working oil chamber 525 a side on the operation-side outlet-side plate side flows out from the relief valve 811 .

[0091] Specifically, if the driving side exit displacement cylinder 515C moves 1 to the driving side, the operating side exit displacement cylinder 515B moves 1 / 2 to the operating side. As a result, the remaining gap becomes 0. Therefore, the driving side arm 714C moves toward the driving side by the remaining gap × 2 / 3, and the operating side arm 714B moves toward the operating side by the remaining gap × 1 / 3.

[0092] In addition, the output displacement cylinder 515C on the driving side is d When the pressure is pressed and the cylinder moves toward the driving side by 1, the piston rod side of the driving side output displacement cylinder 515C also moves by 1, so the rodless chamber side of the operating side output displacement cylinder 515B moves by 1 / 2 of the area ratio, and the piston rod side of the operating side output displacement cylinder 515B also moves by 1 / 2. Therefore, the working oil volume is separated from the relief valve 811 by A dh ×1-A wr ×1 / 2=A dh× 3 / 4. Furthermore, the driving side arm 714C moves at 2 / 3 of the remaining gap, and the operating side arm 714B moves at 1 / 3 of the remaining gap, at which time the driving side exit displacement cylinder 515C and the operating side exit displacement cylinder 515B stop.

[0093] Since the operating side arm 714B moves in the operating side direction by the remaining gap×1 / 3, a movement of the remaining gap×1 / 3 occurs in the position sensor 716.

[0094] The remaining gap is the difference between the gap on the operating side and the gap on the driving side. When the remaining gap is about 1 mm, the position sensor 716 moves toward the operating side by about 1 mm×1 / 3=0.3 mm.

[0095] As described above, the roller group 710A is moved toward the driving side while receiving the thrust resistance in the operating side direction from the roller group 710A. After the position of the roller group 710A is set, when the thrust resistance in the driving side direction acts on the roller group 710A according to changes in conditions such as the rotation of the rollers of the rolling mill and only the roller group 710A moves toward the driving side, the pressure rises to be higher than the set pressure (maximum pressure) of the relief valves 811 and 812 until the thrust resistance is supported on both the driving side and the operating side, and the working oil is separated from the relief valves 811 and 812.

[0096] That is, when the driving side alone can support, only the driving side is used for support, but when only the driving side cannot support, both the driving side and the operating side are used for support. At this time, the pressure becomes higher than the maximum pressure while the working oil gradually separates from the relief valves 811 and 812.

[0097] Therefore, there is a problem that the pressure cannot be supported on both sides until the set pressure of the relief valves 811 and 812 is reached, and when the pressure is supported on both sides, the pressure exceeds the set pressure (maximum pressure).

[0098] Furthermore, since the displacement position of the roll group 710A is deviated, it is necessary to frequently perform displacement position adjustment.

[0099] The above shows the time when the driving side arm 714C comes into contact first and a residual gap is generated on the operating side, but the same problem occurs when the operating side arm 714B comes into contact first and a residual gap is generated on the driving side.

[0100] In the above description, the problem when the direction of the thrust resistance changes is shown. When the length of the roll group 710A changes due to thermal expansion, the same state as the case where an excess gap is generated on one side occurs, and thus the same problem occurs.

[0101] Next, use Figures 7 to 9 The characteristic structure of this embodiment that can solve such problems will be described. Figures 7 to 9 It is a top view illustrating details of the upper work roll portion in the rolling mill.

[0102] like Figure 7 As shown, an operating side entry side displacement cylinder 715A is provided on the entry side fixing component 702 of the operating side, which applies forces in two directions, the operating side and the driving side, to the upper working roller 710 via an operating side arm 714A connected to the upper operating side bearing box 712A supporting the radial bearing 790A on the operating side.

[0103] In addition, an operating side outlet displacement cylinder 715B is provided on the operating side outlet fixing component 703, which applies force in two directions of the operating side and the driving side to the upper working roller 710 via an operating side arm 714B connected to the upper operating side bearing box 712A supporting the radial bearing 790A on the operating side.

[0104] A position sensor 716 is provided at the part of the operating side exit displacement cylinder 715B to detect the position of the upper work roll 710 in the roll axial direction. The position where the position sensor 716 is provided is not limited to this, and may be other positions of the operating side entry displacement cylinder 715A and the driving side displacement cylinders 715C and 715D. In addition, there is no need to be one, and two or more may be provided.

[0105] Similarly, a driving side entry side displacement cylinder 715D is provided on the driving side entry side fixing component 702, which applies force in two directions, the operating side and the driving side, to the upper working roller 710 via a driving side arm 714D connected to the upper driving side bearing box 712B supporting the radial bearing 790B on the driving side.

[0106] In addition, a drive side output side displacement cylinder 715C is provided on the drive side output side fixing component 703, which applies force in two directions, the operating side and the drive side, to the upper working roller 710 via a drive side arm 714C connected to the upper drive side bearing box 712B supporting the radial bearing 790B on the drive side.

[0107] The radial bearing 790A on the operating side also has an axial force acting on the upper working roll 710, which is ultimately supported by the operating side displacement cylinders 715A and 715B. Similarly, the radial bearing 790B on the driving side has an axial force acting on the upper working roll 710, which is ultimately supported by the driving side displacement cylinders 715C and 715D.

[0108] The axial force acting on the upper working roller 710 is in both the operating side direction and the driving side direction. Therefore, any one of the operating side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D will support the force in one direction of the operating side and the driving side.

[0109] The operating side entry displacement cylinder 715A, the operating side exit displacement cylinder 715B, the driving side exit displacement cylinder 715C, and the driving side entry displacement cylinder 715D are all double-rod cylinders with built-in pistons 923d, 925d (only one side is shown) and two piston rods 923c, 925c (only one side is shown).

[0110] In addition, in this embodiment, a hydraulic circuit is provided, which is configured to supply working oil to multiple hydraulic cylinders so that the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B move axially, thereby maintaining the axial position of the upper working roll 710.

[0111] The hydraulic circuit is constructed such that after the hydraulic circuit maintains the axial position of the upper working roller 710, when the hydraulic circuit becomes in a state where only the hydraulic cylinder of one of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B applies axial force to the upper working roller 710 due to the external force applied to the upper working roller 710, the hydraulic cylinder of the other of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B moves in the opposite direction of one of the hydraulic cylinders.

[0112] In addition, pressure pipes 805, 806, 807, and 808 are provided for connecting the corresponding working oil chambers to each other on the inlet side and the outlet side. For example, in the hydraulic circuit, the driving side output plate side working oil chamber 923a, the driving side input plate side working oil chamber 924a and the operating side output side reverse plate side working oil chamber 925b, and the operating side input side reverse plate side working oil chamber 926b are connected with the driving side plate side pressure pipeline 807 and the operating side reverse plate side pressure pipeline 808, and the driving side output side reverse plate side working oil chamber 923b, the driving side input side reverse plate side working oil chamber 924b and the operating side output side plate side working oil chamber 925a, and the operating side input side plate side working oil chamber 926a are connected with the driving side reverse plate side pressure pipeline 805 and the operating side plate side pressure pipeline 806, so that the driving side displacement cylinder 715C, 715D and the operating side displacement cylinder 715A, 715B each apply force to the upper working roller 710 in the same direction.

[0113] Thus, the structure is such that when the direction of the external force changes, the distance between the supports on the side supported and the distance between the supports on the side performing the support change due to the thermal expansion of the mechanical device, etc., when the hydraulic cylinder of one of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B moves with a prescribed stroke, the hydraulic circuit does not change the amount of oil in the connected pressure pipes 805, 806, 807, 808, and the other hydraulic cylinder of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B also moves in the opposite direction with a prescribed stroke of the same size.

[0114] A radial bearing 790A is disposed in the upper operation-side bearing box 712A. A radial bearing 790B is disposed in the upper drive-side bearing box 712B.

[0115] The forces of the upper work roll bending cylinders 740, 741 and the upper work roll bearing box loose elimination cylinder 760 act on the radial bearings 790A, 790B. These radial bearings 790A, 790B support the forces in the vertical direction acting on the roll shaft while rotating.

[0116] Furthermore, the radial bearings 790A and 790B also support the axial force acting on the upper operating side bearing box 712A and the upper driving side bearing box 712B, so four-row tapered roller bearings are generally used. In addition, the radial bearing 790B on the driving side and the radial bearing 790A on the operating side use bearings of the same specifications, which can be set to avoid complicated maintenance work.

[0117] In the driving system of the operating side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D, there is provided an electromagnetic switching valve 810 for regulating the inflow and outflow of oil on the outlet side of a pressure pipe 801 branched from a pressure pipe 800A for supplying hydraulic oil ejected from a pump (omitted in the figure) of the hydraulic device 90, and a tank pipe 802 branched from a tank pipe 800B connected to an oil tank (omitted in the figure) storing hydraulic oil.

[0118] If the electromagnetic switching valve 810 is magnetized, the piston rod side of the operating side displacement cylinder 715A, 715B close to the plate (the operating side output plate side working oil chamber 925a side) is connected to the pressure pipes 801, 800A via the operating side plate side pressure pipe 806 and the pressure pipe 803, exerting a force in the operating side direction on the upper operating side bearing box 712A.

[0119] In addition, the piston rod side of the driving side displacement cylinders 715C and 715D away from the plate (the driving side output side anti-plate side working oil chamber 923b side) is also connected to the pressure pipes 801 and 800A via the driving side anti-plate side pressure pipe 805 and the pressure pipe 803, exerting force in the operating side direction on the upper driving side bearing box 712B.

[0120] Moreover, the piston rod side of the operating side displacement cylinders 715A and 715B away from the plate (the operating side output side anti-plate side working oil chamber 925b side) and the piston rod side of the driving side displacement cylinders 715C and 715D close to the plate (the driving side output side plate side working oil chamber 923a side) are respectively connected to the tank pipes 802 and 800B via the operating side anti-plate side pressure pipe 808 or the driving side plate side pressure pipe 807 and the pressure pipe 804, thereby the displacement cylinders on either the operating side or the driving side generate a displacement force toward the operating side.

[0121] If the electromagnetic switching valve 810 is magnetized in b position, the piston rod side of the operating side displacement cylinder 715A, 715B away from the plate (the operating side output side counter-plate side working oil chamber 925b side) is connected to the pressure pipes 801, 800A via the operating side counter-plate side pressure pipe 808 and the pressure pipe 804, exerting a force in the driving side direction on the upper operating side bearing box 712A.

[0122] In addition, the piston rod side of the driving side displacement cylinders 715C and 715D close to the plate (driving side output plate side working oil chamber 923a side) is connected to the pressure pipes 801 and 800A via the driving side plate side pressure pipe 807 and the pressure pipe 804, exerting a force in the driving side direction on the upper driving side bearing box 712B.

[0123] Moreover, the piston rod side of the operating side displacement cylinders 715A and 715B close to the plate (the operating side output plate side working oil chamber 925a side) and the piston rod side of the driving side displacement cylinders 715C and 715D away from the plate (the driving side output side anti-plate side working oil chamber 923b side) are respectively connected to the oil tank pipes 802 and 800B via the operating side plate side pressure pipe 806 or the driving side anti-plate side pressure pipe 805 and the pressure pipe 803. Thus, any displacement cylinder on the operating side and the driving side generates a displacement force in the direction of the driving side.

[0124] When the electromagnetic switching valve 810 becomes neutral, working oil does not flow to the piston rod side close to the plate or the piston rod side away from the plate in any of the operating side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D through the hydraulic control check valves 821, 822.

[0125] Through the structure of these electromagnetic switching valves 810 and the excitation control performed by the control device 80, the following device is formed: when the axial displacement of the upper working roller 710 is stopped, the upper working roller 710 is supported by operating the side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D so that the upper working roller 710 does not move axially.

[0126] The structure is as follows: a hydraulic control check valve 822 is provided in the pressure pipe 804 on the downstream side of the electromagnetic switching valve 810, and a hydraulic control check valve 821 is provided in the pressure pipe 803 on the downstream side of the electromagnetic switching valve 810, so as to prevent the hydraulic oil from flowing to the piston rod side and rodless cavity side of the operating side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D when the electromagnetic switching valve 810 becomes neutral. Therefore, when the displacement of the upper working roll 710 is stopped, the upper working roll 710 is supported by the operating side displacement cylinders 715A, 715B and the driving side displacement cylinders 715C, 715D so that the upper working roll 710 does not move in the axial direction.

[0127] Moreover, in consideration of extraordinary moments when unexpected excessive thrust resistance occurs, overflow valves 811 and 812 are provided between the hydraulic control check valves 821 and 822 and the operating side displacement cylinders 715A and 715B and the driving side displacement cylinders 715C and 715D, so that the pressure increase in the piping is limited to the mechanically allowable pressure.

[0128] also, Figure 7 The hydraulic system shown is only a part for explaining the present invention, and a flow regulating valve, a check valve, etc. can be appropriately added as necessary.

[0129] Figure 8 The structure around the displacement cylinder on the operating side and the driving side is shown. Figure 8 In the figure, only the piping of the piston rod side close to the plate on the operating side and the piston rod side away from the plate on the driving side is connected to illustrate the effect, but it can be said that the same is true for other piping connection parts.

[0130] exist Figure 8 In the figure, the center position of the distance between the support position on the operating side and the drive side is shown by line M, and F sde is the force of the drive side inlet displacement cylinder 715D supporting the upper drive side bearing box 712B, F swe is the force of the operating side entry displacement cylinder 715A supporting the upper operating side bearing box 712A, L a is the distance between the support positions on the operating side and the drive side, F tr It is the thrust acting on the upper work roll 710. Here, it is assumed that the thrust is acting in the operating side direction.

[0131] exist Figure 8 In the state, F swe and F sde F tr / 4, although not shown in the figure, the operating side displacement cylinder 715B on the output side supports the force F of the upper operating side bearing box 712A swd The force F of the drive side bearing box 712B supported by the drive side displacement cylinder 715C sdd Also F tr / 4, the sum of the four is F tr , support thrust F tr .

[0132] Fig. 9 exist Figure 8 The following moment is assumed: during the rolling process, the upper working roll 710 is heated by the rolled material 5, and the radial bearings 790A and 790B generate heat while rotating under the load. In addition, due to changes in the surrounding temperature, the distance La between the support positions on the operating side and the driving side becomes extended to a state of ΔLa.

[0133] like Fig. 9 As shown, if the distance La between the support positions on the operating side and the driving side changes by ΔLa, the support position on the driving side moves away from the plate by ΔLa / 2, and the working oil flows from the driving side displacement cylinders 715C and 715D away from the plate to the operating side displacement cylinders 715A and 715B close to the plate, and the support position on the operating side moves away from the plate by ΔLa / 2.

[0134] That is, in the hydraulic circuit of the present embodiment, even if the distance La between the support positions on the operating side and the driving side changes by ΔLa, the amount of oil in the pressure pipes 805, 806, 807, and 808 on the outlet sides of the hydraulically controlled one-way valves 821 and 822 will not change. Therefore, the supporting force of the upper working roller 710 based on the operating side displacement cylinders 715A and 715B and the supporting force of the upper working roller 710 based on the driving side displacement cylinders 715C and 715D can be maintained to be the same, and therefore the balance of the total supporting force will not change.

[0135] Therefore, even if La changes by ΔLa, the line M, which is the center position of the distance between the support positions on the operating side and the driving side, is still the center position of the distance between the support positions on the operating side and the driving side. That is, since the line M is close to the center position of the rolled material 5, even if there is thermal expansion, the axial slip between the upper work roll 710 and the rolled material 5 is extremely small, and rolling is not hindered.

[0136] Although the case where thermal expansion occurs is shown here, the supporting force does not change and the position of the line M does not change in the same manner when thermal contraction occurs.

[0137] Next, use Fig.10 A modification of this embodiment will be described. Fig.10 This is a plan view illustrating details of an upper work roll portion in a rolling mill according to a modified example of the first embodiment.

[0138] Fig.10 This is an example of a structure in which a displacement block 712A1 having upper working roll bending cylinders 740 and 741 built therein is connected to the operating side displacement cylinders 715A and 715B on the operating side, and a displacement block 712B1 having upper working roll bending cylinders 740 and 741 built therein is connected to the driving side displacement cylinders 715C and 715D on the driving side.

[0139] When such displacement blocks 712A1 and 712B1 are used, the bending cylinders 740 and 741 are built into the inlet fixing member 702 and the outlet fixing member 703. Figure 7 Similarly to the case of the structure of the above, the thrust reaction force can be made equal on the operating side and the driving side.

[0140] In addition, by adopting Figure 7The structure is provided with a pressure measuring device on the secondary side of the hydraulically controlled one-way valves 821 and 822, so that the thrust acting on the roller can be measured with high precision.

[0141] Next, the effects of this embodiment will be described.

[0142] According to the rolling mill of the first embodiment of the present invention described above, after the hydraulic circuit maintains the axial position of the upper working roll 710, when the hydraulic cylinder of only one of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B applies axial force to the upper working roll 710 due to the external force applied to the upper working roll 710, the hydraulic cylinder of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B moves in the opposite direction of the hydraulic cylinder of one side.

[0143] After maintaining the axial position of the rolling roller, when the direction of the axial external force acting on the rolling roller changes, even if the gap between the operating side hydraulic cylinder and the driving side hydraulic cylinder disappears first, when the hydraulic cylinder on one side is pushed and no longer supported and moves, the hydraulic cylinder on the other side will move the same amount in the opposite direction of the hydraulic cylinder on one side, and this action will be repeated continuously. Soon the remaining gap disappears, and the hydraulic cylinder on the other side also provides support. Therefore, it is possible to avoid a large axial external force acting on one hydraulic cylinder until the gap in the other hydraulic cylinder disappears.

[0144] That is, even if the direction of thermal expansion or thrust resistance changes and there is a gap along the axial direction of the roller between the bearing box and the bearing, inside the bearing, between the bearing and the roller, between the bearing box and the displacement device, etc., as long as there is no excessive thrust resistance, the thrust reaction force of the operating side displacement cylinder 715A, 715B and the drive side displacement cylinder 715C, 715D can be set to be the same, and the pressure in the hydraulic cylinder can be prevented from rising to a pressure higher than the set pressure of the relief valves 811, 812. Therefore, there will be no excessive load on the supporting parts such as the operating side bearing and the drive side bearing of the rolling roller, and the service life can be improved. For example, if the bearing life is set to Lh and the load is set to Pl, in the case of roller bearings, due to the existence of Lh∝(1 / Pl) 10 / 3 , so if 1 / 2 is substituted into Pl, it becomes Lh=10. Therefore, the life of the bearing can be extended by 10 times compared with the case where the thrust is maintained on one side.

[0145] In addition, in the previous structure, if the pressure is increased to a pressure higher than the set pressure of the relief valve, the working oil flows out from the secondary side of the hydraulic control check valve, thereby causing a displacement position deviation, which requires frequent displacement position adjustment. However, in the structure of this embodiment, since the pressure increase above the set pressure of the relief valves 811 and 812 can be suppressed, the effect of not needing to frequently adjust the displacement position is also obtained. That is, there is no need for the complicated pressure measuring device and the inflow and outflow oil amount adjustment unit as in the past, and a simple device structure can be achieved. On this basis, since there is no complicated control device and it can be achieved only under the ON / OFF control of the electromagnetic switching valve 810, the device structure of the control system can also be simplified.

[0146] In the case of Patent Document 1, for example, the thrust is sometimes supported on one side or on both sides, and the state of the thrust support changes before and after the relief valve is operated. In addition, the working pressure of the relief valve affects the pressure on the secondary side of the hydraulic control check valve, but the working pressure of the relief valve changes according to the flow rate, so it is difficult to judge whether the thrust is supported on one side or on both sides based on the pressure measurement result on the secondary side of the hydraulic control check valve. Therefore, even if a pressure measuring device is provided on the secondary side of the hydraulic control check valve and the pressure is measured, since the thrust is obtained by multiplying the area of ​​the two pressure chambers of the cylinder, it is still unclear whether the cylinder supporting the thrust is on one side or on both sides, and it is known that there is a concern that the thrust is difficult to obtain with high accuracy.

[0147] However, the structure of this embodiment also includes the situation where an abnormal thrust acts and the relief valves 811 and 812 work, and the thrust can always be supported on both sides, so the thrust can be calculated with high accuracy from the pressure measurement results on the secondary side of the hydraulic control check valves 821 and 822.

[0148] In addition, the rolling mill that tilts the upper and lower rolls in opposite directions to form a cross state has a high plate convex / plate shape control capability, but a large thrust acts between the rolled material 5 and the upper working roll 710, so the load capacity has a limit depending on the strength of the bearings and roll ends that bear the thrust.

[0149] In particular, when the load conditions are severe, grease cannot be used as bearing lubrication, and oil lubrication such as circulating oiling must be used. However, when oil lubrication such as circulating oiling is used, the equipment is complicated and the equipment cost is high.

[0150] In contrast, by adopting the structure of the present embodiment described above, if the load applied can be halved, a simple grease lubrication can be adopted as a mechanical device, and there is an advantage that the equipment cost and the operation cost can also be suppressed to a low level. In addition, if the load applied can be halved, the diameter of the upper working roll 710 can be reduced, and therefore, since it can involve a reduction in rolling load, it can also be applied to the rolling of hard materials.

[0151] In the above description, the case where the bearing bears both bending force and thrust force is described, but there is also a case where a radial bearing that bears bending force and a thrust bearing that bears thrust force are provided separately. The structure of the bearing can be appropriately selected, and in their structures, by adopting the structure of this embodiment, the load acting can be halved, thereby extending the life of the roller support parts such as the bearing.

[0152] Moreover, the resistance in the vertical direction of the thrust receiving part affects the rolling load measurement value. In the case where the thrust support device is only on one side, it also becomes a cause of differential load. By adopting the structure of this embodiment, the thrust can be made the same on the operating side and the driving side. Therefore, although it also depends on the friction coefficient of the thrust receiving part, the differential load can be minimized.

[0153] Therefore, by adopting the structure of this embodiment, it is possible to achieve a structure that reduces the movement resistance of the thrust receiving portion in the rolling direction. Thus, it is possible to reduce the resistance when the inclination changes during the rolling process.

[0154] In addition, with regard to the hydraulic circuit, since the driving side output plate side working oil chamber 923a is connected to the operating side output side counter-plate side working oil chamber 925b by pressure pipes 807 and 808, and the driving side output side counter-plate side working oil chamber 923b is connected to the operating side output side plate side working oil chamber 925a by pressure pipes 805 and 806, the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B each apply force to the upper working roller 710 in the same direction, thereby being able to be constructed so that the amount of working oil moving in the piping does not change.

[0155] Moreover, the hydraulic circuit is constructed so that when the hydraulic cylinder of one of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B moves with a specified stroke, the amount of oil in the connected pressure pipes 805, 806, 807, 808 is not changed, and the hydraulic cylinder of the other of the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B also moves in the opposite direction with a specified stroke. As a result, the driving side and the operating side can move in the same manner with the same stroke, and the pressure in the piping will not become such a high pressure that exceeds the set pressure of the relief valves 811, 812. Therefore, force can be applied to the rolling rollers in the same direction on both the driving side and the operating side to support the thrust.

[0156] In addition, the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B are double-rod cylinders, and the driving side outlet plate side working oil chamber 923a and the driving side outlet side counter-plate side working oil chamber 923b have the same cross-sectional area in the direction of the force applied to the working oil, and the operating side outlet plate side working oil chamber 925a and the operating side outlet side counter-plate side working oil chamber 925b have the same cross-sectional area in the direction of the force applied to the working oil, and the driving side outlet plate side working oil chamber 923a and the operating side outlet side counter-plate side working oil chamber 925b The pressure pipes 807 and 808 are connected, and the working oil chamber 923b on the output side of the driving side and the working oil chamber 925a on the output side of the operating side are connected with the pressure pipes 805 and 806, thereby obtaining the following effects: the force supporting the thrust in the direction of the operating side acting on the rolling roller can be equal to the force supporting the thrust in the direction of the driving side, and the life of the bearing and other supporting parts can be maximized when the bearings on the operating side and the driving side of the rolling roller are of the same specification, and the damage to each part caused by the load can be reduced. In addition, by setting it as a double rod, the bearing box connection part of the hydraulic cylinder on the driving side and the hydraulic cylinder on the operating side can be set close to the plate, so that the structure around the bearing box connection part can be symmetrical on the driving side and the operating side, and the structure can be common, which can be a simple device compared with other embodiments described later.

[0157] Moreover, the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B are respectively arranged on the entry side and the exit side of the rolling mill, and are equipped with pressure pipes 805, 806, 807, 808 that connect the corresponding working oil chambers to each other on the entry side and the exit side. As a result, the supporting forces on the entry side and the exit side of the hydraulic cylinder can be made the same, so that the torque does not act on the bearing box, thereby preventing the rolling roller from rotating in the horizontal plane, and the supporting forces on the entry side and the exit side of the rolled material 5 can be made equal with a simple structure.

[0158] In addition, the control device 80 is configured to control the driving of multiple hydraulic cylinders. The control device 80 drives the driving side displacement cylinders 715C, 715D and the operating side displacement cylinders 715A, 715B, and can cause the upper working roll 710 to be displaced axially, thereby automatically performing the axial displacement of the rolling roll.

[0159] Furthermore, a horizontal actuator is provided for adjusting the angle of each roller in the horizontal direction. If the rolling roller is set at an arbitrary tilt angle relative to the plate, the thrust acting on the rolling roller becomes larger, but the large thrust is supported by half on the operating side and the driving side respectively, and the supporting force on the inlet side and the outlet side is equalized with a simple structure, so that the moment does not act on the bearing box, and thus the supporting force of each hydraulic cylinder can be reduced to 1 / 4.

[0160] Furthermore, in a single hydraulic cylinder having a double rod, the diameters of the two piston rods can be changed, that is, the cross-sectional areas of the two hydraulic oil chambers can be made different.

[0161] In this case, the cross-sectional areas of the working oil chambers on the driving side close to the plate and on the operating side far from the plate are combined and connected by piping. In addition, the cross-sectional areas of the driving side far from the plate and on the operating side close to the plate are combined and connected by piping. As a result, the driving side far from the plate and the operating side close to the plate, as well as the driving side close to the plate and the operating side far from the plate, are respectively given the same force as thrust reaction force, thereby reducing the thrust reaction force by half, allowing the driving side and the operating side to be set to the same supporting force, and maximizing the life of the roller supporting parts such as bearings.

[0162] In addition, when it is desired to selectively increase the force of the supporting thrust in the direction of the operating side, it is possible to choose to set a diameter difference in the piston rod diameter in such a way that the cross-sectional area of ​​the working oil chamber on the operating side away from the plate and the driving side close to the plate is larger than the cross-sectional area of ​​the working oil chamber on the operating side close to the plate and the driving side away from the plate.

[0163] <Example 2>

[0164] use Fig.11 A rolling mill and a rolling method according to a second embodiment of the present invention will be described. Fig.11 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 2.

[0165] exist Fig.11 In the rolling mill of the present embodiment shown, the driving side exit displacement cylinder 715C1, the driving side entry displacement cylinder 715D1, the operating side entry displacement cylinder 715A1 and the operating side exit displacement cylinder 715B1 are all single-rod cylinders, and the single rods 923c1, 925c1 (both sides are only shown) of any cylinder are oriented in the same direction and are arranged on the operating side.

[0166] Therefore, the operating side entry displacement cylinder 715A1 is connected to the operating side arm 714A and the upper operating side bearing box 712A via the transmission component 715A2, and the operating side exit displacement cylinder 715B1 is connected to the operating side arm 714B and the upper operating side bearing box 712A via the transmission component 715B2, thereby supporting the upper working roller 710.

[0167] Moreover, the driving side outlet plate side working oil chamber 923a1 is connected to the operating side outlet side counter-plate side working oil chamber 925b1 by the driving side plate side pressure pipe 807A, 807B, and the cross-sectional area in the direction of the force applied to the working oil (the area of ​​piston 923d1 and piston 925d1) is the same, and the driving side outlet side counter-plate side working oil chamber 923b1 is connected to the operating side outlet side plate side working oil chamber 925a1 by the pressure pipe 805A, 805B and the operating side plate side pressure pipe 806, and the cross-sectional area in the direction of the force applied to the working oil (the area of ​​piston 923d1 and piston 925d1) is the same.

[0168] According to this structure, it is also the same as that described in Example 1. Figure 7 Similarly, even in the case of thermal deformation of ΔLa, the driving side and the operating side can be supported with equal force by moving to opposite sides by ΔLa / 2 via the wire M.

[0169] That is, the roller group 710A is moved toward the driving side while receiving the thrust resistance in the operating side direction from the roller group 710A. After the position of the roller group 710A is set, the thrust resistance in the driving side direction acts on the roller group 710A according to changes in conditions such as the rotation of the rollers of the rolling mill, and when only the roller group 710A moves toward the driving side, the thrust resistance can be evenly supported on both the driving side and the operating side, so the pressure will not rise above the set pressure of the relief valves 811 and 812.

[0170] In this case as well, relief valves 811 and 812 may be provided on the secondary sides of the hydraulic control check valves 821 and 822 in consideration of an emergency moment when an unexpected excessive thrust resistance acts.

[0171] The other structures and operations are substantially the same as those of the rolling mill and rolling method of the aforementioned first embodiment, and the details are omitted.

[0172] In the rolling mill and the rolling method according to the second embodiment of the present invention, substantially the same results as those of the rolling mill and the rolling method according to the first embodiment described above were obtained.

[0173] In addition, in this embodiment, the same hydraulic cylinder can be used on the operating side and the driving side, but the mechanical devices such as the displacement device around the cylinder can be configured differently on the operating side and the driving side. Therefore, although the equipment becomes complicated, the protrusion amount of the displacement device including the displacement cylinder from the frame on the operating side can be made smaller than that of the structure of the first embodiment, so it is a structure suitable for use when it is difficult to increase the displacement device in coordination with the arrangement device on the operating side.

[0174] Specifically, the roll assembling device on the operating side can be arranged close to the rolling mill side, which is similar to the case where only the displacement cylinder is provided on the operating side for work roll displacement. Therefore, there is no need to expand the space on the operating side, which can save space.

[0175] In addition, if there is space limitation on the driving side of the device, the rodless chamber side of the operating side displacement cylinders 715A1 and 715B1 can be set to be far from the plate side, and the rodless chamber side of the driving side displacement cylinders 715C1 and 715D1 can be set to be close to the plate side.

[0176] When ensuring space on the operation side regardless of hot rolling or cold rolling, the structure of this embodiment is preferable.

[0177] In addition, the structure of the single-rod cylinder in this embodiment is not limited to Fig.11 In the embodiment shown in the figure, the drive side exit displacement cylinder 715C1 and the drive side entry displacement cylinder 715D1 can also support the drive side arms 714C and 714D via a transmission member in the same manner as the operation side entry displacement cylinder 715A1 and the operation side exit displacement cylinder 715B1, so that the single rod faces the axial outer side. In this case, as described later, Fig.14 In that way, an intermediate cylinder is further provided.

[0178] If the displacement cylinder is arranged in such a manner that the piston rod faces outward, the rolling mill becomes compact. The space for the roll group can be ensured on the operation side, and the drive side can also be made compact, so that space can be ensured. In addition, since the structure of the drive side and the structure of the operation side can be made symmetrical, the structure can be made common, and the device structure can be simplified.

[0179] <Example 3>

[0180] use Fig.12 and Fig.13 A rolling mill and a rolling method according to a third embodiment of the present invention will be described. Fig.12 and Fig.13 It is a top view illustrating details of the upper work roll portion in the rolling mill of Example 3.

[0181] exist Fig.12 and Fig.13 In the rolling mill of the present embodiment shown, the pressure pipe 805B1 branched from the pressure pipe 803 is connected to the driving side entry side counter-plate side working oil chamber 833b of the driving side entry side displacement cylinder 833 of the double rod, and the pressure pipe 805B2 branched from the pressure pipe 803 is connected to the operating side entry side plate side working oil chamber 830a of the operating side entry side displacement cylinder 830 of the double rod.

[0182] Moreover, the driving side inlet side counter-plate side working oil chamber 833b is connected to the driving side outlet side counter-plate side working oil chamber 832b of the double-rod driving side outlet side displacement cylinder 832 by a pressure pipe 823, the driving side outlet side counter-plate side working oil chamber 832b is connected to the operating side outlet side plate side working oil chamber 831a of the operating side outlet side displacement cylinder 831 of the double-rod by a pressure pipe 824, and the operating side outlet side plate side working oil chamber 831a is connected to the operating side inlet side plate side working oil chamber 830a by a pressure pipe 825.

[0183] In addition, in order to illustrate the function, only the piping connection between the piston rod side of the operating side close to the plate and the piston rod side of the driving side away from the plate is explained, but the piston rod side of the operating side away from the plate (operating side inlet side anti-plate side working oil chamber 830b, operating side outlet side anti-plate side working oil chamber 831b) and the piston rod side of the driving side close to the plate (driving side inlet side plate side working oil chamber 833a, driving side outlet side plate side working oil chamber 832a) are also connected in the same way through piping.

[0184] exist Fig.12 and Fig.13 Also in Figure 8 Similarly, it is assumed that a thrust acts in the operating side direction.

[0185] Fig.13 Shown in Fig.12 The middle and upper working rolls 710 have an arbitrary tilt angle relative to the rolled material 5. The center of the plate width at the plate passing position is set to be substantially the same position as the center of the rolling mill, and the tilt angle θ is set around the center position of the plate width direction of the rolling mill. c Set counterclockwise.

[0186] exist Fig.13 In the rolling process, the tilt angle θ is set when the hydraulic control check valves 821 and 822 are in effect. c When the distance from the center position of the rolling mill to the thrust acting position is the same on the operating side and the driving side, the support position on the entry side of the operating side moves closer to the plate by ΔL we , In addition, the support position of the exit side of the operating side moves away from the plate by ΔL wd Moreover, the support position on the inlet side of the driving side moves away from the plate by ΔL de , In addition, the support position of the output side of the drive side moves closer to the plate ΔL dd .

[0187] Due to these movements, the hydraulic oil moves in the pressure pipes 805B1 , 805B2 , 823 , 824 , and 825 , but the total amount of the hydraulic oil on the outlet side (secondary side) of the hydraulic control check valves 821 and 822 does not change.

[0188] The piston rod side of the operating side away from the plate and the piston rod side of the driving side close to the plate are similarly connected by a pressure pipe, so the total amount of working oil on the outlet side (secondary side) of the hydraulic control check valves 821 and 822 does not change.

[0189] On the other hand, the upper work roll 710 may be displaced to take various positions, and even when not displaced, the distance from the center of the rolling mill to the thrust action position may be different between the operating side and the driving side.

[0190] In this case, the distance between the support positions on the operating side and the driving side changes slightly due to the inclination of the upper working roll 710. In response to this change, the flow of working oil occurs between the operating side and the driving side, just as when the distance between the support positions on the operating side and the driving side changes due to thermal expansion of the upper working roll 710. However, ΔL we , ΔL wd , ΔL de , ΔL dd The values ​​of , with the inclination of the upper working roll 710, do not change significantly, although they are slightly offset from the position of action of the thrust force obtained geometrically.

[0191] In this way, in a rolling mill that moves the working rolls, when the upper working roll 710 is tilted during the rolling process, the displacement position does not change significantly. In addition, it can be tilted without applying an excessive load that rises to above the set pressure of the overflow valves 811 and 812 during the tilting process.

[0192] Furthermore, when tilting, only a slight deviation is accompanied with the line M as the center, so the upper work roll 710 can be tilted in a state where there is almost no slip between the rolled material 5 and the upper work roll 710 .

[0193] After the displacement position of the upper working roller 710 is determined, or even if there is no displacement in the rolling mill, after the axial position of the upper working roller 710 is determined using the structure of this embodiment, even if the inclination angle is changed during the rolling process, even if the hydraulically controlled one-way valves 821 and 822 are still in a state of function, no inappropriate force will be applied to the displacement device.

[0194] The axial deviation of the roll accompanying the change of the tilt angle is minimized because the deviation between the center of the distance between the support positions and the center of the tilt (the center position of the rolling mill) is small. When this minimal deviation occurs, the total amount of the working oil on the secondary side of the hydraulic control check valves 821 and 822 does not change.

[0195] In addition, Fig.11In other embodiments of the present invention, even if the rollers are tilted relative to the rolled material 5 during the rolling process, as long as the total amount of working oil on the secondary side of the hydraulically controlled one-way valves 821 and 822 does not change, the supporting force on the operating side and the driving side of each cylinder can be made equal.

[0196] The other structures and operations are substantially the same as those of the rolling mill and rolling method of the aforementioned first embodiment, and the details are omitted.

[0197] In the rolling mill and the rolling method according to the third embodiment of the present invention, substantially the same effects as those of the rolling mill and the rolling method according to the first embodiment described above can be obtained.

[0198] <Example 4>

[0199] use Fig.14 A rolling mill and a rolling method according to a fourth embodiment of the present invention will be described. Fig.14 1 is a top view illustrating details of the upper working roll portion in the rolling mill of Example 4. Fig.14 Only the exit side is shown, but the entry side has the same structure and the details are omitted.

[0200] Fig.14 In the rolling mill of the present embodiment shown, the drive side delivery side displacement cylinder 935C and the operating side delivery side displacement cylinder 935B are single rod cylinders. The piston rod 943c of the drive side delivery side displacement cylinder 935C and the piston rod 945c of the operating side delivery side displacement cylinder 935B are oriented in opposite directions and are respectively arranged on the rolling material 5 side.

[0201] Furthermore, there are two single-rod first intermediate cylinders 971 and second intermediate cylinders 973. These first intermediate cylinders 971 and second intermediate cylinders 973 are dummy cylinders, and there is no particular pressing object.

[0202] On this basis, the driving side output side piston rod side working oil chamber 943a of the driving side output side displacement cylinder 935C is connected to the piston rod side working oil chamber 971b of the first intermediate cylinder 971 by the intermediate piston rod pressure pipeline 807C2, and the driving side output side rodless cavity side working oil chamber 943b is connected to the rodless cavity side working oil chamber 973a of the second intermediate cylinder 973 by the intermediate piston rod pressure pipeline 805C2.

[0203] Moreover, the operating side output side piston rod side working oil chamber 945a of the operating side output side displacement cylinder 935B is connected to the piston rod side working oil chamber 973b of the second intermediate cylinder 973 by an intermediate piston rod pressure pipeline 805C1, and the operating side output side rodless cavity side working oil chamber 945b is connected to the rodless cavity side working oil chamber 971a of the first intermediate cylinder 971 by an intermediate piston rod pressure pipeline 807C1.

[0204] In addition, the ratio of the cross-sectional areas of the driving side outlet piston rod side working oil chamber 943a and the driving side outlet rodless chamber side working oil chamber 943b, the ratio of the cross-sectional areas of the operating side outlet piston rod side working oil chamber 945a and the operating side outlet rodless chamber side working oil chamber 945b, the ratio of the cross-sectional areas of the piston rod side working oil chamber 971b and the rodless chamber side working oil chamber 971a, and the ratio of the cross-sectional areas of the piston rod side working oil chamber 973b and the rodless chamber side working oil chamber 973a are the same in all cylinders.

[0205] In this case as well, if the driving arm 714C moves toward the driving side by half of the remaining clearance, the operating arm 714B moves toward the operating side by half of the remaining clearance, and the amount of hydraulic oil on the secondary side of the hydraulic control check valves 821 and 822 does not change.

[0206] In addition, the cross-sectional area of ​​the hydraulic oil in the operating side displacement cylinder 935B and the driving side displacement cylinder 935C is A. wr dh , pressure is p wr >p dh , becoming A wr ×p wr =A dh ×p dh , so the supporting forces of the driving side arm 714C and the operating side arm 714B become the same.

[0207] Similarly, when a thrust in the operating side direction is applied to the roller group 710A, since a thrust reaction force of the same force is generated on the piston rod side of the driving side and the rodless chamber side of the operating side, in the structure of this embodiment, the supporting force of the thrust on the operating side and the driving side can be divided into half each.

[0208] The other structures and operations are substantially the same as those of the rolling mill and rolling method of the aforementioned first embodiment, and the details are omitted.

[0209] In the rolling mill and the rolling method according to the fourth embodiment of the present invention, substantially the same effects as those of the rolling mill and the rolling method according to the first embodiment described above can be obtained.

[0210] In addition, in the structure of the present embodiment 4, the bearing box connecting part of the hydraulic cylinder on the driving side and the bearing box connecting part of the hydraulic cylinder on the operating side can be set close to the rolled material 5, so that the structure around the bearing box connecting part can be made symmetrical on the driving side and the operating side, the structure can be commonalized, and a simple device can be achieved.

[0211] ​In addition, since the length of the hydraulic cylinder is shorter than that of the double-rod structure as in the first embodiment, the protrusion of the operating side of the displacement device can be reduced, and space for the roll arranging device can be ensured.

[0212] In addition, the piston 973d of the second intermediate cylinder 973 and the piston 943d of the drive side output displacement cylinder 935C, the piston 945d of the operating side output displacement cylinder 935B, and the piston 971d of the first intermediate cylinder 971 can be made to have the same cross-sectional area, but they do not need to be the same, as long as the ratio of the cross-sectional area of ​​the rodless chamber side / piston rod side of the piston of each cylinder is the same.

[0213] <Others>

[0214] In addition, the present invention is not limited to the above-described embodiments, and various modifications are possible. The above-described embodiments are described in detail to explain the present invention in an easily understandable manner, but the present invention is not limited to having all the described configurations.

[0215] In addition, a part of the structure of a certain embodiment can be replaced with the structure of another embodiment, and a structure of another embodiment can be added to a structure of a certain embodiment. In addition, other structures can be added, deleted, or replaced with a part of the structure of each embodiment.

[0216] For example, a rolling mill in which the rolling rolls are displaced in the roll axial direction has been described as an example, but a rolling mill having a hydraulic cylinder for fixing the axial position, that is, a rolling mill that does not displace in the axial direction, is also an object of the present invention.

[0217] Description of Reference Numerals

[0218] 1…Rolling equipment

[0219] 5…Rolled materials

[0220] 30…1st stand (rolling mill)

[0221] 40…2nd stand (rolling mill)

[0222] 50…3rd stand (rolling mill)

[0223] 60…4th stand (rolling mill)

[0224] 70…5th stand (rolling mill)

[0225] 80…Control device

[0226] 90…Hydraulic device

[0227] 700… rack

[0228] 702…Entry side fixing parts

[0229] 703…Exit side fixing parts

[0230] 705A, 705B, 705E, 705F, 706C, 706D…Hydraulic cylinder (horizontal actuator)

[0231] 710...Upper working roll (rolling roll)

[0232] 710A...Roller Group

[0233] 711…Lower working roll (rolling roll)

[0234] 712…Upper working roll bearing box

[0235] 712A…Upper operating side bearing box

[0236] 712A1…Displacement Block

[0237] 712B…Upper drive side bearing housing

[0238] 712B1…Displacement Block

[0239] 713…Lower working roll bearing box

[0240] 713A, 713B…Bearing box

[0241] 714A, 714B…operating side arm

[0242] 714C, 714D...Drive side arm

[0243] 715…Displacement cylinder (hydraulic cylinder)

[0244] 715A, 715A1, 830... Operation side entry side displacement cylinder (hydraulic cylinder, operation side hydraulic cylinder)

[0245] 715A2, 715B2…Transmission components

[0246] 715B, 715B1, 831, 935B…Operation side displacement cylinder (hydraulic cylinder, operation side hydraulic cylinder)

[0247] 715C, 715C1, 832, 935C…Drive side output displacement cylinder (hydraulic cylinder, drive side hydraulic cylinder)

[0248] 715D, 715D1, 833...Drive side entry displacement cylinder (hydraulic cylinder, drive side hydraulic cylinder)

[0249] 716…Position sensor

[0250] 717…Displacement cylinder (hydraulic cylinder)

[0251] 720...Upper middle roller (rolling roller)

[0252] 721…Lower intermediate roller (rolling roller)

[0253] 722…Upper intermediate roller bearing box

[0254] 723…Lower intermediate roller bearing box

[0255] 730... Upper reinforcement roller (rolling roller)

[0256] 731…Lower reinforcing roller (rolling roller)

[0257] 732… Upper reinforced roller bearing box

[0258] 733… Lower reinforced roller bearing box

[0259] 740, 741, 742, 743... Upper working roll bending cylinder

[0260] 744, 745, 746, 747… lower working roll bending cylinder

[0261] 750, 751…Upper middle roll bending cylinder

[0262] 752, 753…lower middle roll bending cylinder

[0263] 760... Upper working roll bearing box loosening elimination cylinder

[0264] 762…Looseness elimination cylinder for lower working roll bearing box

[0265] 771…Upper intermediate roll bearing box loosening elimination cylinder

[0266] 773…Lower intermediate roll bearing box loosening elimination cylinder

[0267] 780… Upper reinforced roller bearing box loosening elimination cylinder

[0268] 782…Lower reinforced roller bearing box loosening elimination cylinder

[0269] 790A, 790B…Radial bearings

[0270] 800A, 801…pressure pipe

[0271] 800B, 802…Oil tank pipe

[0272] 803, 804…pressure pipe

[0273] 805…Drive side counter plate side pressure pipe (piping)

[0274] 805A, 805B, 805B1, 805B2, 823, 824, 825…pressure pipes (piping)

[0275] 805C1, 805C2…Intermediate piston rod pressure pipe (piping)

[0276] 806…Operation side panel side pressure pipeline (piping)

[0277] 807…Drive side plate side pressure pipe (piping)

[0278] 807A, 807B…Drive side plate side pressure pipe

[0279] 807C1, 807C2…Intermediate piston rod pressure pipe

[0280] 808…Operation side reverse plate side pressure pipeline (piping)

[0281] 810…Solenoid switching valve

[0282] 811, 812…Relief valve

[0283] 821, 822…Hydraulic control check valve

[0284] 830a…Operation side inlet side plate side working oil chamber

[0285] 830b…Operation side, inlet side, reverse plate side, working oil chamber

[0286] 831a…Operation side outlet plate side working oil chamber

[0287] 831b…Operation side, output side, reverse plate side, working oil chamber

[0288] 833a…Drive side inlet plate side working oil chamber

[0289] 833b…Drive side, inlet side, reverse plate side, working oil chamber

[0290] 832a, 923a, 923a1…Drive side outlet plate side working oil chamber (drive side plate side working oil chamber)

[0291] 832b, 923b, 923b1…Drive side output side counter plate side working oil chamber (drive side counter plate side working oil chamber)

[0292] 923c, 925c…piston rod

[0293] 923c1...Single rod (driving side hydraulic cylinder piston rod)

[0294] 923d, 923d1, 925d, 925d1, 943d, 945d, 971d, 973d… piston

[0295] 924a…Drive side inlet plate side working oil chamber (drive side plate side working oil chamber)

[0296] 924b…Drive side inlet side counter plate side working oil chamber (drive side counter plate side working oil chamber)

[0297] 925a, 925a1…Operation side outlet plate side working oil chamber (Operation side plate side working oil chamber)

[0298] 925b, 925b1…Operation side, output side, reverse plate side, working oil chamber (Operation side, reverse plate side, working oil chamber)

[0299] 925c1...Single rod (operating side hydraulic cylinder piston rod)

[0300] 926a…Operation side inlet plate side working oil chamber (operation side plate side working oil chamber)

[0301] 926b…Operation side inlet side counter plate side working oil chamber (Operation side counter plate side working oil chamber)

[0302] 943a…Drive side outlet side piston rod side working oil chamber (drive side plate side working oil chamber)

[0303] 943b…Drive side output side rodless chamber side working oil chamber (drive side counter plate side working oil chamber)

[0304] 943c...Piston rod (piston rod of the hydraulic cylinder on the driving side)

[0305] 945a…Operation side outlet side piston rod side working oil chamber (operation side plate side working oil chamber)

[0306] 945b…Operation side output side rodless chamber side working oil chamber (operation side counter plate side working oil chamber)

[0307] 945c...Piston rod (piston rod of hydraulic cylinder on the operating side)

[0308] 971…1st intermediate cylinder

[0309] 971a…Rodless cavity side working oil chamber

[0310] 971b… Piston rod side working oil chamber

[0311] 973…Second intermediate cylinder

[0312] 973a…Rodless cavity side working oil chamber

[0313] 973b…Working oil chamber on the piston rod side.

Claims

1. A rolling mill comprising: rolling rollers; A plurality of hydraulic cylinders, including a driving side hydraulic cylinder configured to impart an axial force to the rolling roller and provided on a driving side of the rolling roller, and an operating side hydraulic cylinder configured to impart the axial force to the rolling roller and provided on an operating side of the rolling roller; and The hydraulic circuit is configured to deliver hydraulic oil to the plurality of hydraulic cylinders so that the driving side hydraulic cylinder and the operating side hydraulic cylinder move in the axial direction to maintain the position of the rolling roll in the axial direction. The hydraulic circuit is constructed such that, after the hydraulic circuit maintains the axial position of the rolling roller, when the state is reached where only one of the driving side hydraulic cylinder and the operating side hydraulic cylinder applies the axial force to the rolling roller due to the external force applied to the rolling roller, the other of the driving side hydraulic cylinder and the operating side hydraulic cylinder moves in the opposite direction of the one of the hydraulic cylinders.

2. The rolling mill according to claim 1, wherein: The hydraulic circuit connects the working oil chamber on the driving side plate side with the working oil chamber on the operating side counter-plate side by piping, and connects the working oil chamber on the driving side counter-plate side with the working oil chamber on the operating side plate side by piping, so that the driving side hydraulic cylinder and the operating side hydraulic cylinder each apply force to the rolling roller in the same direction.

3. The rolling mill according to claim 2, wherein: The hydraulic circuit is constructed so that when one of the driving side hydraulic cylinder and the operating side hydraulic cylinder moves with a specified stroke, the amount of oil in the connected piping is not changed, and the other of the driving side hydraulic cylinder and the operating side hydraulic cylinder also moves in the opposite direction with the specified stroke.

4. The rolling mill according to claim 1, wherein: The driving side hydraulic cylinder and the operating side hydraulic cylinder are double-rod cylinders. The driving side plate side working oil chamber and the driving side counter plate side working oil chamber have the same cross-sectional area in the direction in which the force applied to the working oil is applied. The cross-sectional areas of the operating side plate side working oil chamber and the operating side counter plate side working oil chamber in the direction of the force applied to the working oil are the same. The driving side plate side working oil chamber and the operating side counter plate side working oil chamber are connected by piping, and the driving side counter plate side working oil chamber and the operating side plate side working oil chamber are connected by piping.

5. The rolling mill according to claim 1, wherein: The driving side hydraulic cylinder and the operating side hydraulic cylinder are single-rod cylinders. The piston rod of the driving side hydraulic cylinder and the piston rod of the operating side hydraulic cylinder are oriented in the same direction. The driving side plate side working oil chamber and the operating side counter plate side working oil chamber are connected by piping, and the cross-sectional area in the direction of the force applied to the working oil is the same. The driving side counter-plate side working oil chamber and the operating side plate side working oil chamber are connected by piping, and have the same cross-sectional area in the direction of the force applied to the working oil.

6. The rolling mill according to claim 1, wherein: The driving side hydraulic cylinder and the operating side hydraulic cylinder are single-rod cylinders. The piston rod of the driving side hydraulic cylinder and the piston rod of the operating side hydraulic cylinder are in opposite directions. An intermediate cylinder with two or more single rods, The working oil chamber on the driving side piston rod side is connected to the working oil chamber on the first intermediate cylinder piston rod side by piping. The driving side rodless chamber side working oil chamber and the second intermediate cylinder rodless chamber side working oil chamber are connected by piping. The operating side piston rod side working oil chamber and the second intermediate cylinder piston rod side working oil chamber are connected by piping. The operating side rodless chamber side working oil chamber and the first intermediate cylinder rodless chamber side working oil chamber are connected by piping. The ratio of the cross-sectional areas of the driving side piston rod side working oil chamber and the driving side rodless chamber side working oil chamber in the direction of the force applied to the working oil, the ratio of the cross-sectional areas of the operating side piston rod side working oil chamber and the operating side rodless chamber side working oil chamber in the direction of the force applied to the working oil, the ratio of the cross-sectional areas of the first intermediate cylinder piston rod side working oil chamber and the first intermediate cylinder rodless chamber side working oil chamber in the direction of the force applied to the working oil, and the ratio of the cross-sectional areas of the second intermediate cylinder piston rod side working oil chamber and the second intermediate cylinder rodless chamber side working oil chamber in the direction of the force applied to the working oil are the same.

7. The rolling mill according to claim 6, wherein: The driving-side hydraulic cylinder piston rod and the operating-side hydraulic cylinder piston rod are configured to face outward in the axial direction.

8. The rolling mill according to any one of claims 1 to 7, wherein: The driving side hydraulic cylinder and the operating side hydraulic cylinder are respectively arranged on the entry side and the exit side of the rolling mill. The inlet side and the outlet side are provided with pipes for connecting the corresponding working oil chambers to each other.

9. The rolling mill according to any one of claims 1 to 7, wherein: A control device for controlling the driving of the plurality of hydraulic cylinders is provided, The control device is configured to drive the driving-side hydraulic cylinder and the operating-side hydraulic cylinder to displace the rolling roll in the axial direction.

10. The rolling mill according to any one of claims 1 to 7, wherein: A horizontal actuator is provided for adjusting the angle of the rolling roll in the horizontal direction.

11. A rolling method, which is a rolling method for a rolling material performed by a rolling mill, the rolling mill comprising: rolling rollers; A plurality of hydraulic cylinders, including a driving side hydraulic cylinder configured to impart an axial force to the rolling roller and provided on a driving side of the rolling roller, and an operating side hydraulic cylinder configured to impart the axial force to the rolling roller and provided on an operating side of the rolling roller; and The hydraulic circuit is configured to deliver hydraulic oil to the plurality of hydraulic cylinders so that the driving side hydraulic cylinder and the operating side hydraulic cylinder move in the axial direction to maintain the position of the rolling roll in the axial direction. In the rolling method, The hydraulic circuit is constructed so that after the hydraulic circuit maintains the axial position of the rolling roller, when the rolling roller is subjected to an external force and only one of the driving side hydraulic cylinder and the operating side hydraulic cylinder applies the axial force to the rolling roller, the other of the driving side hydraulic cylinder and the operating side hydraulic cylinder moves in the opposite direction of the one of the hydraulic cylinders, thereby rolling the rolled material.

12. The rolling method according to claim 11, wherein: The hydraulic circuit is constructed by connecting the working oil chamber on the driving side plate side and the working oil chamber on the operating side counter-plate side by piping, and connecting the working oil chamber on the driving side counter-plate side and the working oil chamber on the operating side plate side by piping, so that the driving side hydraulic cylinder and the operating side hydraulic cylinder each apply force to the rolling roller in the same direction, thereby rolling the rolled material.

13. The rolling method according to claim 12, wherein: The hydraulic circuit is constructed so that when the hydraulic cylinder of one of the driving side hydraulic cylinder and the operating side hydraulic cylinder moves with a specified stroke, the amount of oil in the connected piping is not changed, and the hydraulic cylinder of the other of the driving side hydraulic cylinder and the operating side hydraulic cylinder also moves in the opposite direction with the specified stroke, thereby rolling the rolled material.

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