JP2001340907A - Roll chock clamping device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a roll chock clamping device suitably clamping a roll chock without any influence on AGC system. SOLUTION: Upon the roll chock clamping device of a rolling mill having a work roll and a back-up roll supporting the work roll, the device is composed of a fixed plate 22 arranged at a housing side of the rolling mill and a movable plate 23. The device is further provided with a housing liner 21 forming a cylinder 24 and a piston 25 on these plates, a pressure mechanism 27, in which the mechanism is uniformly arranged in a circumferential direction at a periphery of the cylinder 24, giving pressure onto the piston 25 and also giving braking force to the motion of the piston, and a hydraulic pressure supply means 40 enclosing liquid in the cylinder 24, in which supply of hydraulic pressure is stopped when the housing liner 21 is brought into contact with the roll chock or the housing liner is moved by a predetermined width (thickness), while moving the piston 25 by supplying hydraulic pressure into the cylinder 24.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a rolling mill provided with a work roll (work roll), a backup roll, and a roll chock (bearing box) for a work roll, and more particularly to a roll for adjusting a gap between the roll chock and a housing of the rolling mill. Regarding the structure of the liner.

[0002]

2. Description of the Related Art A rolling mill that rolls a steel sheet between hot and cold rolls includes a pair of work rolls and a backup roll that supports the work rolls and transmits a rolling force. Each roll is supported on the housing of the rolling mill via a roll chock (bearing box), but a slight gap (play) is provided between the work roll and the housing for roll exchange. Due to this gap, the rolls move horizontally during rolling, and the amount of crossing between the upper roll and the lower roll changes. In some cases, a difference may occur in the rolling force at both ends of the work roll. These behaviors cause the meandering of the plate and the quality deterioration.

FIGS. 9 (A) and 9 (B) are views showing the details of the periphery of a rolling mill and its work rolls. A backup roll 11 is provided on each of the pair of work rolls 10, and a shaft of the work roll 10 is supported by a roll chock 12. A chock liner 13 is attached to the roll chock 12 and the housing 1
4, a housing liner 15 is attached,
These are arranged facing each other. As shown in the drawing, there is a gap of about 1 mm to 2 mm in the rolling direction between the housing liner 15 and the chock liner 13, and the work roll 1
When 0 moves in the rolling direction, the work roll 10 is no longer restrained by the backup roll 11.

In order to solve such roll rattling, a mechanism for securing a gap between the roll chock and the housing when the roll is replaced, and mechanically restraining the roll chock by a hydraulic cylinder or the like during rolling, for example, is known. JP 6
These are proposed in, for example, Japanese Patent Application Laid-Open No. 1-129208 and Japanese Patent Application Laid-Open No. 8-174409. Also, Japanese Utility Model Application Laid-Open 63-80006
Japanese Patent Application Laid-Open Publication No. H11-163873 proposes a structure in which the gap between the roll chock and the housing is reduced by hydraulically varying the thickness of the liner attached to the roll chock, that is, a liner-type roll chock gap restraining device.

[0005]

[Problem to be Solved by the Invention] (Problem 1) Shokai 63
The liner-type roll chock gap restraint device proposed in Japanese Patent Publication No. -80006 has a structure in which a hydraulic cylinder and a piston are built in a thin liner. In this device, a method is employed in which the thickness of the liner is changed by projecting a piston by supplying oil by a pump. In this device, the piston stroke is extremely small compared to the hydraulic cylinder diameter because the need to output a certain restraining force to restrain the roll chocks and the hydraulic cylinder etc. are built in the thin liner. It has become. When oil is supplied to such a hydraulic cylinder, there is a problem that a piston having an extremely large diameter as compared with a stroke does not rise evenly and is easily inclined (see FIG. 8 (B)). The property is easily impaired.

(Problem 2) JP-A-61-129208, JP-A-8-174409 and JP-A-63-8
The device proposed in Japanese Unexamined Patent Publication No. 0006 is a device for restraining the behavior of a work roll or the like during rolling, and presses a roll chock at a constant pressure by a hydraulic cylinder or the like provided on a housing side. During rolling, the AGC constantly and delicately controls the rolling force of the roll, the tension of the sheet, the rolling speed, etc. so that the sheet thickness becomes a predetermined value during rolling.
(Auto gain control) System is operating. For this reason, the work roll and the backup roll that supports the work roll always vertically and slightly move vertically. In such a situation, aggressive pressing of the roll chock by the hydraulic cylinder has a bad influence on the AGC system. In addition, there is a problem that the liner on the roll chock side is greatly worn by constantly pressing with a constant pressing force.

SUMMARY OF THE INVENTION The present invention has been made to solve the above-mentioned problem by a simple method, and provides a roll-chock clamping device capable of appropriately clamping a roll-chock without affecting an AGC system. Is to do.

[0008]

(1) A roll-chock clamping device according to the present invention comprises a fixed plate and a movable plate provided on a housing side of a rolling mill.
A housing liner in which a cylinder and a piston are formed on these plates, a pressurizing mechanism for uniformly applying pressure to the piston around the cylinder of the housing liner, and applying a hydraulic pressure to the cylinder. Hydraulic pressure supply means for supplying and moving the piston, stopping the supply of the hydraulic pressure when the housing liner is in contact with the roll chock or when the housing liner has a predetermined width (thickness), and sealing the liquid in the cylinder; It is provided with.

In the present invention, the movable plate is moved by supplying hydraulic pressure to the cylinder. At this time, the pressurizing mechanism applies the pressurized pressure evenly around the piston to apply the braking force, so that the piston is evenly lifted. For this reason, the hydraulic sealing performance of the piston portion is not impaired. Then, when the movable plate comes into contact with the roll chock (or when the housing plate has a predetermined width), the supply of the liquid pressure is stopped to seal the liquid in the cylinder. The width of the housing liner is fixed by the liquid confined in the cylinder. In this state, even if the roll chock attempts to move, it cannot move because the distance from the housing liner is almost zero (a state close to or near zero). For this reason, a rolling machine with high lateral rigidity is realized. Further, the housing liner does not positively press the roll chock, but touches (contacts) the roll chock, so that the influence of the work roll on the AGC system can be minimized. Further, even in the case where the liner is provided on the roll chock side, since a mechanism for pressing the roll chock with a predetermined pressing force is not employed, the wear of the liner can be reduced.

(2) The roll-chock clamp device according to the present invention is the roll-chock clamp device according to the above (1), wherein the stopper mechanism is disposed evenly around the cylinder of the housing liner in the circumferential direction, and regulates the amount of movement of the cylinder. Is further provided. In the present invention, since the amount of movement of the piston is limited by the stopper mechanism, the movement distance of the piston can be limited as appropriate, and for example, the movable plate can be fixed at a position immediately before the movable plate touches the roll chock. Further, even when the fluid pressure in the cylinder rises due to the thermal expansion of the entire apparatus and an unnecessary pressing force may be applied to the roll chock due to a change in the width of the movable plate, the width of the movable plate may be reduced by the stopper mechanism. It is possible to prevent change.

(3) The roll-chock clamping device according to the present invention is the roll-chock clamping device according to the above (1) or (2), wherein the hydraulic supply means comprises: a hydraulic pump for supplying hydraulic pressure to the cylinder; A detecting means for detecting that the ground or the movable plate has reached a predetermined width; and a switching means for sealing the liquid in the cylinder by detection by the detecting means.
In the present invention, the hydraulic pressure is supplied to the cylinder by the hydraulic pump, and when the movable plate is grounded to the roll chock or the housing plate has a predetermined width, the liquid in the cylinder is sealed by the switching means.

[0012]

FIG. 1 is a front view, a left side view, and a bottom view (including a partial cross section) of a housing liner constituting a part of a roll-chock lamp device according to a first embodiment of the present invention. FIGS. 2A, 2B and 2C are explanatory views conceptually showing the housing liner. The roll chock device 20 includes a housing liner 21 whose width (thickness) is adjusted. The housing liner 21 includes a fixed plate 22 and a movable plate 23. A hydraulic cylinder 24 is formed on the fixed plate 22, and a hydraulic cylinder 24 is formed on the movable plate 23.
The piston 25 which moves in the inside is formed. And
An O-ring 26 is attached to the piston 25 to seal oil in the hydraulic cylinder 24. Also,
The fixed plate 22 and the movable plate 23 have a pressurizing mechanism 2
7 and the stopper mechanism 28 are respectively
Are arranged at equal intervals in the circumferential direction. In addition,
The housing liner 21 and a hydraulic system 4 described later
Reference numeral 0 denotes a single-acting hydraulic system, which is mounted on the housing 14 on the plate-entering side of the rolling mill.

FIG. 3 is an explanatory view of the pressurizing mechanism 27, and FIG.
The (C) pressurizing mechanism 27 is shown in an enlarged manner. As the pressurizing mechanism 27, a recess 30 is formed in the fixed plate 22, and a through hole 31 is formed at the bottom of the recess 30. An elastic body 32 is provided in the recess 30 and the through hole 31.
The special bolt 33 is disposed through the base plate, and the tip of the special bolt 33 is T-shaped and engages with the movable plate 23. In the initial state, the elastic body 3
2 is in a state where a slight force is applied, and is in a slightly contracted state. Next, when the piston 25 moves in the direction away from the fixed plate 22 and protrudes, the head of the special bolt 33 also moves in the recess 30 with it, and the elastic body 32 is further compressed by the special bolt 33. Become. For this reason, the elastic body 32 further contracts, and acts as a braking force when oil is supplied to the hydraulic cylinder 24.
When there is no oil (the piston is opened), a force is generated to return the piston 25 to the initial state.

FIG. 4 is an explanatory view of the stopper mechanism, and shows the stopper mechanism 28 of FIG. 1C in an enlarged manner. As the stopper mechanism 28, the movable plate 23
Is provided with a recess 35, and a through hole 36 is provided at the bottom of the recess 35. Special bolts 37 are disposed in the recesses 35 and the through holes 36, and the tips of the special bolts 37 are fixed to the fixing plate 22. In the initial state, the head of the special bolt 37 is located farthest from the fixing plate 22. Next, when the piston 25 moves away from the fixed plate 22 and protrudes, the special bolt 37 moves relatively in the axial direction in the recess 35, and the head of the special bolt 37 is placed at the bottom of the recess 35. When the time comes, the operation of the piston 25 is restricted, and the movement of the piston 25 is restricted. FIG. 4 shows a state in which the movement of the piston 25 is restricted.

FIG. 5 is a view showing the overall configuration of the roll choke clamp device 20. As shown in FIG. The roll chock clamp device 20 controls a piston 25 and a hydraulic cylinder 24 in addition to the housing liner 21.
It has a hydraulic system 40 for sealing the oil inside. The hydraulic system 40 includes a hydraulic pump 41 for supplying hydraulic pressure, and a sheet type 2 for shutting off a hydraulic supply pipe 42.
A position 3 port electromagnetic switching valve (hereinafter referred to as an electromagnetic switching valve) 43 and a pressure sensor 44 provided on a path of a hydraulic supply pipe 42 to the hydraulic cylinder 24 and measuring a pressure on a secondary side of the electromagnetic switching valve 43 in the path. And a sensor 45 with a pressure switch, a flow regulating valve 46 for arbitrarily setting the amount of oil supply to the hydraulic cylinder 24, and a relief for preventing the pressure rise in the passage of the hydraulic supply pipe 42 from exceeding a predetermined pressure. And a valve 47.

The gap between the roll chock 12 of the rolling mill and the housing 14 is 0.5 mm to 2 mm on one side. Assuming that the work roll 10 is shifted toward the exit side of the rolling mill during regular rolling, the maximum gap is considered to be 4 mm. However, since the work rolls 10 are rearranged for each fixed production amount, the gap changes for each roll and is not always the same value.

The housing liner generally has a thickness of only about 20 mm to 30 mm in hot rolling, but the play (gap) of the roll chock is 2 mm as described above.
Therefore, the required amount of protrusion of the piston can be reduced. Therefore, the roll chock clamp mechanism, which is structurally composed of the hydraulic cylinder and the piston, can be integrated in the housing liner. By using the liner-type roll-chock clamp device 20, it is possible to easily incorporate the roll-chock device into an existing rolling mill without the roll-chock clamp device, simply by replacing the liner currently used. However, since the roll chock clamp needs to secure several tons or more, the piston diameter / piston protrusion amount becomes 50 times or more. For this reason, unless the method of supplying oil to the hydraulic cylinder is equalized, the pressure distribution in the large-diameter hydraulic cylinder becomes uneven, and it is difficult to raise the piston in parallel. The pressure mechanism 27 and the stopper mechanism 28 address such inconveniences.

Next, the operation of the roll chock clamp device 20 of the present embodiment will be described. (1) Before the operation starts, the piston 25 is
4 and a gap exists between the housing liner 21 and the roll chock 12 as shown in FIG. (2) The hydraulic pump 41 is started by a control signal of a hydraulic supply start command from the outside, and the electromagnetic switching valve 43 is
The oil is supplied to the hydraulic cylinder 24 at a flow rate set in advance by the flow control valve 46. At this time, a uniform braking force is generated around the operation of the piston 25 by the pressurizing mechanism 27 provided around the hydraulic cylinder 24, and the pressure distribution in the hydraulic cylinder 24 and the pressurizing mechanism 27
And the load of the piston 25 is balanced.

(3) The flow rate at this time is 4 liters /
min or less. With such a supply amount, the pressure in the path of the hydraulic supply pipe 42 and the pressure in the hydraulic cylinder 24 of the housing liner 21 show the same value, and the pressure in the pressurizing mechanism 27 and the hydraulic cylinder 24 are balanced. 25 can be raised evenly.

FIG. 7 shows the pressure distribution in the hydraulic cylinder 24. However, this distribution shows that the oil is
Shows the state of the initial stage when it comes into the hydraulic cylinder 24 via the, and after a predetermined time has elapsed, the pressure distribution becomes uniform. In the present embodiment, since the pressurizing mechanism 27 is provided as described above, the piston 25 is uniformly pressurized around the piston 25, and a braking force is generated.
As shown in FIG. 8A, the piston 25 rises up evenly. On the other hand, when the pressurizing mechanism 27 is not provided, as shown in FIG.
May move with inclination.

(4) When the oil starts to be supplied into the hydraulic cylinder 24, the width (thickness) of the housing liner 21 increases because the movable plate 23 protrudes little by little by the hydraulic pressure of the piston 25. FIG. 6B shows the state at this time. (5) At this time, the elastic body (urethane rubber, disc spring) 32 of the pressurizing mechanism 27 is further compressed when the movable plate 23 is separated from the fixed plate 22. (6) When the movable plate 23 contacts (contacts) the roll chock 12, the pressure in the hydraulic cylinder 24 increases. However, if the supply amount is set to a small amount, the pressure does not increase suddenly even at the time of contact with the ground.

(7) When the oil pressure in the oil supply pipe 42 becomes equal to the oil supply resistance plus a pressure of about 0.1 MPa, the electromagnetic switching valve 32 is closed by a signal from the pressure sensor 44 (or the pressure switch 45). Then, the hydraulic pump 41 is stopped. (8) At this time, the movable plate 23 is
2, the roll chock 12 is not positively pressed with a constant pressure. (9) The piston 25 is supported by the oil enclosed in the hydraulic cylinder 24. In other words, the oil is not supplied because of the deadline, but the position of the piston 25 is fixed. In this case, the pressure of the contained oil is not always kept constant. (10) Even if the roll chock 12 tries to move in this state, the movable plate 23 and the roll chock 12
Since the gap between the two is infinitely zero, you cannot move.

(11) When the roll chock 12 presses the movable plate 23, the oil is sealed,
The pressure in the hydraulic cylinder 24 increases. Hydraulic system 4
The position of the movable plate 23 is fixed only by increasing the pressure up to the set pressure of the relief valve 47 on the 0 side. When the pressure exceeds the set pressure of the relief valve 47, the oil in the hydraulic cylinder 24 is released to the tank 48 of the hydraulic pump 41 through the relief valve 47 for safety, so that the position of the piston 25 is reduced. It contracts by the amount removed from the relief valve 47. (12) Also, the oil is compressible, and when pressed by the roll chock 12, the oil contracts due to the compressibility. By setting the area of the hydraulic cylinder 24 such that the shrinkage due to the compressibility calculated from the bulk modulus and the oil amount in the hydraulic cylinder 24 can be ignored,
The effect of oil compressibility can be reduced.

(13) To open the gap between the roll chock 12 and the movable plate 23 again, the electromagnetic switching valve 3 is operated to transfer the oil in the hydraulic cylinder 24 of the roll chock clamp device 20 to the tank 48 which is an atmospheric pressure. Open. (14) Although the hydraulic pressure in the hydraulic cylinder 24 is instantaneously released to the atmosphere, the movable plate 23 does not return to the original state only by releasing the pressure in the hydraulic cylinder 24. (15) Here, the elastic body 32 of the pressurizing mechanism 27 compressed when the movable plate 23 protrudes is pressed by the force to return to the original state due to the oil pressure in the hydraulic cylinder 24 being released to the atmosphere. 23 returns to its original state, the thickness of the housing liner 21 also returns, and a gap is formed between the roll chock 12 and the housing liner 21.
At this time, the elastic body 32 only returns to the initial state.

(16) Also, when the movable plate 23 is in contact with the roll chock 11, even if the force is of the order of contact, the hydraulic pressure in the hydraulic cylinder 24 increases due to the thermal expansion of the entire apparatus, and an unnecessary pressing force is generated. If there is a possibility that the movable plate 23 will be in contact with the roll chock 12, the protrusion of the piston 25 is limited by a stopper mechanism 28 provided on the movable plate 23 and the fixed plate 22 without directly contacting the movable plate 23 with the roll chock 12. The effect on the AGC system can be minimized. (17) When an eccentric load is applied, the movable plate 23 tends to tilt. However, the stopper mechanism 28 acts in a direction to cancel the tilt, and the tilt of the piston 25 in the hydraulic cylinder 24 can be prevented.

Before the piston 25 comes into contact with the roll chock 12 by the stopper mechanism 28, the piston 2
In a case where the stop of the hydraulic pump 41 is performed, the electromagnetic switching valve 43 is switched and the hydraulic pump 41 is stopped.

[Brief description of the drawings]

FIG. 1 is a front view, a left side view, and a bottom view of a housing liner that constitutes a part of a roll chock clamp device according to a first embodiment of the present invention.

FIG. 2 is an explanatory view conceptually showing the housing liner of FIG. 1;

FIG. 3 is an explanatory diagram of a pressurizing mechanism of FIG. 1;

FIG. 4 is an explanatory view of the stopper mechanism of FIG. 1;

FIG. 5 is a view showing the overall configuration of the roll choke clamp device according to the first embodiment.

FIG. 6 is a diagram showing a relationship between a housing liner and a roll chock according to the first embodiment.

FIG. 7 is an explanatory diagram of a pressure distribution in the hydraulic cylinder of the fixed plate of FIG.

FIG. 8 is an explanatory view showing the operation of the housing liner.

FIG. 9 is an explanatory diagram of a rolling mill and a work roll thereof.

[Explanation of symbols]

 DESCRIPTION OF SYMBOLS 10 Work roll 11 Backup roll 20 Roll chock clamp device 21 Housing liner 22 Fixed plate 23 Movable plate 24 Hydraulic cylinder 25 Piston 27 Pressurizing mechanism 28 Stopper mechanism 40 Hydraulic system

Claims (3)

[Claims] 1. A roll-chock clamping device for a rolling mill provided with a work roll, a backup roll, and a roll chock for a work roll, comprising a fixed plate and a movable plate provided on a housing side of the rolling mill. A housing liner in which a cylinder and a piston are formed, a pressurizing mechanism that is uniformly arranged in the circumferential direction around the cylinder of the housing liner, and applies a pressure to the piston; and supplies a hydraulic pressure to the cylinder. Hydraulic supply means for moving the piston to stop the supply of hydraulic pressure when the housing liner touches the roll chock or reaches a predetermined width to seal the liquid in the cylinder. Roll chock clamp device. 2. The roll-chock clamp device according to claim 1, further comprising: a stopper mechanism that is arranged around the cylinder of the housing liner in a circumferential direction thereof and that regulates a movement amount of the cylinder. 3. A hydraulic pump for supplying hydraulic pressure to the cylinder, a hydraulic pump for supplying hydraulic pressure to the cylinder, a detecting means for detecting that the ground of the piston to the roll chock or a movable plate has a predetermined width, and 3. The roll-chock clamp device according to claim 1, further comprising a switching unit configured to seal the liquid in the cylinder by detection by the unit.