JPH05346116A - Roll bearing device - Google Patents

Abstract

PURPOSE:To obtain a roll bearing device which can resist large thrust force applied to a roll and is easily maintained and managed. CONSTITUTION:A radial bearing 6 is installed on a roll shaft 1a. A piston 9 is projectingly formed adjacently to the radial bearing 6. The piston 9 is slidably fitted to and held by an inner surface of a shaft box 8. A pressure chamber 11 is formed inside the shaft box 8 for applying a fluid pressure to an outer surface of the piston 9. The pressure chamber 11 functions as a thrust bearing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a roll bearing device for use in a rolling mill or the like in which a large thrust force acts on a roll such as a rolling mill in which rolls are arranged in a horizontal plane parallel to the plate to roll the plate. It is about.

[0002]

2. Description of the Related Art In recent years, the requirements for the thickness accuracy of rolled products in the plate width direction have become more and more strict. Generally, the hot coil has a middle height in the plate width direction, so in order to correct the thickness distribution to cancel this, a method of attaching an initial crown to the work roll in advance, or a method of bending the work roll, etc. It has been known.

However, in the case of a method in which the work rolls are provided with crowns, the number of rolls corresponding to the rolling conditions such as the plate width and thickness of the plate material is held, and the crowns are different each time the rolling conditions change. Therefore, there is a problem that the operation rate is lowered, and in the case of the method of bending the work roll, it may be added to the work roll due to the strength of the roll neck of the work roll. Since the bending force is limited, there is a problem that it is not possible to obtain sufficient thickness distribution correction ability in the plate width direction.

In order to solve these problems, as shown in FIG. 4, as an example, the upper work roll 1 and the upper backup roll 3 and the lower work roll 2 and the lower backup roll 4 are kept parallel to each other with their axes kept horizontal. A roll-cross type rolling machine has been developed in which the upper and lower pair rolls are arranged to form the upper pair roll and the lower pair roll, respectively, and the plate material 5 is rolled in a state where the axes of the upper and lower pair rolls intersect in a horizontal plane. 55-64908). In this rolling mill, the thickness distribution in the width direction of the plate material 5 can be controlled by adjusting the intersection angle (cross angle) of the upper and lower pair rolls, and the product can be rolled into a uniform plate thickness. However, there is a problem in that an excessive thrust force is generated in the roll because the roll is tilted in the horizontal plane for rolling.

Therefore, in a rolling mill in which a thrust force is generated in a work roll such as the above-mentioned roll-cross type rolling mill, a work roll in which a thrust force is generated (in the figure, the upper work roll 1 is shown in FIG. 5). The radial bearing 6 and the thrust bearing 7 are mounted side by side in the axial direction on the roll shaft 1a (showing the case), and these bearings 6 and 7 are held by the axle box 8 to support the roll shaft 1a (special feature). (Kaisho 60-255207).

[0006]

However, as described above, the structure in which the radial bearing 6 and the thrust bearing 7 are simply incorporated in the shaft box 8 has a problem that the load capacity with respect to the thrust force is low. That is, it has been confirmed that, in the roll-cross type rolling mill, a thrust force of about 10% of the rolling load acts on the work rolls, and since this excessive thrust force acts on the thrust bearing 7, wear etc. As a result, the life of the thrust bearing 7 is very short, and therefore the thrust bearing 7 is frequently replaced, which makes maintenance management difficult.

Therefore, the present invention is not limited to the roll-cross type rolling mill as described above, but is easy to maintain and manage even in a rolling mill in which a large thrust force is generated in the roll, and a large thrust force acting on the roll is also applied. An object of the present invention is to provide a roll bearing device that can endure.

[0008]

According to the present invention, in order to solve the above-mentioned problems, a roll shaft is supported by a radial bearing housed in a shaft box and is adjacent to the radial bearing on the roll shaft. At the position, a piston having an outer diameter adapted to be inscribed in the inner surface of the shaft box is projected, and a pressure chamber for exerting a fluid pressure on the outer surface of the piston is formed in the shaft box. To do.

The roll shaft is supported by a radial bearing housed in a shaft box, and the roll shaft is inscribed in the inner surface of the shaft box at a position adjacent to the radial bearing. The projecting piston of, the inside by the piston,
A pressure chamber that is partitioned into an outer pressure chamber portion is formed in the shaft box, and fluid introduction paths for supplying fluid to the pressure chamber parts are provided in the shaft box, respectively. A fluid metering device for metering the fluid is connected to the fluid introduction path, and further, at a position facing the neutral position of the piston of the shaft box, at a moving position in the roll axial direction of the piston. Accordingly, a configuration may be provided in which a fluid discharge path is provided to discharge the fluid from the inside of one of the pressure chambers to the outside.

Further, the shaft of the roll is supported by a radial bearing housed in a shaft box, and an outer diameter of the roll shaft is inscribed in a position adjacent to the radial bearing on the inner surface of the shaft box. A plurality of pressure chambers formed by projecting pistons and partitioned into inner and outer pressure chambers by the pistons are formed in the axial direction in the shaft box, and the pressure chambers on the same side of each pressure chamber are formed. It is also possible to adopt a configuration in which the fluid pressure can be simultaneously applied to the parts.

Furthermore, a flow rate control valve for controlling the amount of fluid supplied to the pressure chamber, a displacement meter for detecting the relative position of the roll shaft and the shaft box in the axial direction of the roll axis, and a detected value by the displacement meter. It is preferable that a position control device including a controller that sends a control command to the flow control valve by comparing it with a position set value is provided.

[0012]

When the thrust force acts on the roll, the piston protruding from the roll shaft can be opposed by the pressure of the fluid in the pressure chamber.

Further, by forming a pressure chamber which is divided into two pressure chamber portions by the piston, it is possible to cope with the thrust force acting in any of the roll axial directions.

Furthermore, since a fluid pressure is simultaneously applied to the pressure chamber portion on the same side of the plurality of pressure chambers formed, it becomes possible to receive a larger thrust force.

Furthermore, by providing the position control device, the relative position of the roll and the axle box is controlled, so that the position shift of the roll is prevented.

[0016]

Embodiments of the present invention will be described below with reference to the drawings.

FIG. 1 shows an embodiment of the present invention. For convenience of explanation, only one end side of the upper work roll 1 of the upper and lower work rolls is shown. Roll shaft 1 of upper work roll 1
a is rotatably supported by a radial bearing 6 housed in a shaft box 8, and a piston 9 is integrally projected at an adjacent position outside the radial bearing 6 portion on the roll shaft 1a, The piston 9 is slidably fitted to the inner peripheral surface of the shaft box 8 through the seal material 10 in the roll axial direction,
Further, a pressure chamber 11 is formed in the shaft box 8 so that a pressure of a fluid such as a hydraulic pressure supplied through a pipe 25 acts on the outer surface of the piston 9, and an arrow acting on the upper work roll 1 is formed. The thrust force in the A direction is applied to the pressure chamber 11
The position control device 12 controls the position of the upper work roll 1 in the roll axis direction.

The position control device 12 is a servo valve 1 as a flow control valve for controlling the amount of fluid supplied to the pressure chamber 11.
3 and a displacement gauge 14 mounted between the end of the roll shaft 1a and the end of the shaft box 8 to detect relative displacement of the roll shaft 1a and the shaft box 8 in the roll axis direction, Displacement meter 14
And a servo amplifier 16 as a controller for sending a control command to the servo valve 13 by comparing the value of the detection signal from the position set value by the setter 15. The displacement gauge 14 may be of a type such as a gap sensor.

In the figure, 17 is a closing member attached to the outer end of the shaft box 8 to form the pressure chamber 11, 18 is a sealing material provided on the inner peripheral portion of the closing member 17, and 19 is the pressure chamber 11.
A pump for supplying a fluid to, and 20 a tank of the fluid.

When the upper and lower work rolls are arranged in a cross shape as shown in FIG. 4 and horizontal cross rolling is performed, a large thrust force in the direction of arrow A acts on the upper work roll 1, but the large thrust force is applied. The force can be received in the pressure chamber 11 formed in the axle box 8. That is,
Due to the structure in which the pressure of the fluid introduced into the pressure chamber 11 acts on the outer surface of the piston 9 protruding from the roll shaft 1a, the piston 9 and the pressure chamber 11 function as a thrust bearing. Can receive a large thrust force. At this time, when the upper work roll 1 is displaced in the roll axial direction by the thrust force in the direction of the arrow A,
The relative position between the roll shaft 1a and the shaft box 8 is detected by the displacement gauge 14 mounted between the roll shaft 1a and the end of the shaft box 8, and the value of the detection signal and the position set value by the setter 15 are servo-controlled. The servo amplifier 1 is compared and calculated by the amplifier 16.
Since the control command is sent from 6 to the servo valve 13, the supply amount of the fluid to the pressure chamber 11 is controlled, so that the upper work roll 1 is returned to the original regular position, and the positional deviation is prevented.

In the above description, the piston 9 and the pressure chamber 11 functioning as a thrust bearing have a structure like a so-called fluid pressure cylinder, so the thrust bearing 7 shown in FIG.
Maintenance is not required due to its short durability as in the case of using, and a large thrust force can be received due to the use of fluid pressure. Further, since the piston 9 is integrated with the roll shaft 1a, it is also advantageous for holding the roll shaft center during rotation of the upper work roll 1.

Next, FIG. 2 shows another embodiment of the present invention. Like the embodiment of FIG. 1, the radial bearing in which the roll shaft 1a of the upper work roll 1 is housed in the axle box 8 is shown. In a structure in which the roll shaft 6 is rotatably supported, two internal and external pressures are provided by a piston 9 integrally projecting on the roll shaft 1a at an outer position adjacent to the radial bearing 6 in the shaft box 8. The pressure chamber 21 partitioned by the chamber portions 21a and 21b is formed by the partition wall 8a and the closing member 17, and fluid introduction paths 22a and 22b for introducing the fluid into the pressure chamber portions 21a and 21b are provided. , Provided on the axle box 8 and provided with the respective fluid introduction paths 22a, 22b.
In addition, for example, a flow control valve, an orifice, a fixed amount fluid feeder 23a, 23b such as a capillary tube is connected to the pipe 25.
a and 25b, and each of the fluid constant quantity feeders 2 is connected.
3a and 23b through the pipes 25a and 25b and the fluid introduction paths 22a and 22b, the pressure chambers 21a inside and outside,
21b so that a fixed amount of fluid can be supplied to the pressure chamber 21b, and one of the pressure chambers is located at a position facing the neutral position of the piston 9 of the shaft box 8 depending on the moving position of the piston 9 in the roll axial direction. A fluid discharge path 24 is provided so as to discharge the fluid from the inside of 21a or 21b to the outside.

In the case of the embodiment shown in FIG. 2, when the thrust force is not acting on the upper work roll 1, the fluid is introduced into the fluid introduction passages 22a, 2b by the fluid constant quantity feeders 23a, 23b.
2b through each pressure chamber portion 21a of the pressure chamber 21,
After being constantly fed into the tank 21b in a fixed amount, the state of being discharged from the fluid discharge path 24 and returned to the tank 20 is maintained. In this state, for example, when the piston 9 moves to the position shown by the chain double-dashed line due to the thrust force acting in the direction of arrow A, the movement of the piston 9 closes the pressure chamber 21b. The fluid in 21a is discharged from the fluid discharge path 24 as shown by the double-dashed line arrow, but the pressure chamber 21b
By increasing the fluid pressure inside, the thrust force in the direction of arrow A can be received. On the other hand, upper work roll 1
When the thrust force acts in the direction opposite to the arrow A, the fluid pressure in the pressure chamber portion 21a of the pressure chamber 21 is increased contrary to the above, so that the thrust force in the direction opposite to the arrow A can be received. Therefore, it is particularly advantageous when performing reversible operation or when changing the cross arrangement of the rolling rolls up and down.

FIG. 3 shows still another embodiment of the present invention. Similar to that shown in FIG. 2, the roll shaft 1a of the upper work roll 1 is mounted on a radial bearing 6 housed in a shaft box 8. A pressure chamber 21 that is rotatably supported and is partitioned into two inner and outer pressure chamber portions 21a and 21b by a piston 9 integrally provided on the roll shaft 1a at a position adjacent to the radial bearing 6. In the structure in which the shaft box 8 is provided with fluid introduction passages 22a, 22b formed by the partition wall 8a and the closing member 17 and for introducing the fluid into the pressure chamber portions 21a, 21b, the pressure chamber 21 Next to the pressure chamber 21, two pressure chamber portions 21a, 21a are formed by the piston 9 integrally provided on the roll shaft 1a, similarly to the pressure chamber 21.
The pressure chamber 21 'is formed so as to be partitioned into b, and the fluid introduction paths 22a of the two pressure chambers 21 and 21' are formed.
The pipes 25a and 25b for supplying and discharging the fluid are respectively branched to and connected to 22b, and the position control device 12 similar to that shown in FIG. 1 is further provided to each pressure chamber portion on the same side of the two pressure chambers. The fluid can be simultaneously supplied to 21a or 21b.

In the case of the embodiment shown in FIG. 3, two pressure chambers 21 and 21 'are formed coaxially side by side, and each pressure chamber portion 2 on the same side is formed.
Since the fluid pressure can be applied to 1a or 21b at the same time, the thrust force can be further increased as compared with the case of the above-described embodiment, and, as in the case of the embodiment of FIG. The thrust force in the A direction can also be received, and even if the upper work roll 1 is displaced in the roll axial direction by the position control device 12 as in the embodiment of FIG. Can be returned to the normal position to prevent displacement.

In the above embodiment, the upper work roll 1
However, the other rolls to which the thrust force acts have the same structure, and the pressure chamber is formed at the outer position adjacent to the radial bearing 6 on the roll shaft 1a. Although it may be formed on the inside or on both sides, and in the embodiment of FIG. 3, the case where two pressure chambers 21 and 21 'are provided is shown.
Of course, the number may be one or more, and various changes may be made without departing from the scope of the present invention.

[0027]

As described above, according to the roll bearing device of the present invention, the following excellent effects are exhibited. (1) On the roll shaft of the roll, a piston is provided so as to be adjacent to the radial bearing, the piston is slidably fitted on the inner peripheral surface of the shaft box, and fluid pressure is applied to the outer surface of the piston. Since a pressure chamber adapted to act on is formed in the shaft box and the pressure chamber is made to function as a thrust bearing,
It can receive a large thrust force that acts on the roll and is less likely to wear as compared to a bearing type thrust bearing, so maintenance is easy and the life of the bearing can be extended. Since the piston provided on the shaft is incorporated in the shaft box, it is easy to handle. (2) A piston protruding from the roll shaft forms a pressure chamber partitioned into two pressure chambers, and a constant amount of fluid can be constantly fed to each pressure chamber, so that the pressure in any of the roll axial directions can be improved. It is also possible to deal with the thrust force acting in the direction of, and therefore, it is particularly advantageous when performing reversible operation or when changing the cross direction of the roll up and down. (3) Plural pressure chambers that are partitioned into two pressure chambers by pistons protruding from the roll shaft are formed coaxially so that fluid pressure can be applied simultaneously to the pressure chambers on the same side of each pressure chamber. By doing so, the force against the thrust force can be further increased. (4) In the device of item (1) or (3) above, by providing a position control device based on the relative displacement of the roll shaft and the axle box, it is possible to prevent the position shift of the roll due to the action of thrust force. can do.

[Brief description of drawings]

FIG. 1 is a schematic view showing an embodiment of a roll bearing device of the present invention.

FIG. 2 is a partial view showing another embodiment of the present invention.

FIG. 3 is a partial view showing still another embodiment of the present invention.

FIG. 4 is a schematic view showing an example of a conventional roll-cross type rolling mill.

FIG. 5 is a schematic view showing an example of a conventional bearing mechanism.

[Explanation of symbols]

 1 Upper Work Roll (Roll) 1a Roll Axis 6 Radial Bearing 8 Axle Box 9 Piston 11 Pressure Chamber 12 Position Control Device 13 Servo Valve (Flow Control Valve) 14 Displacement Meter 16 Servo Amplifier (Controller) 21, 21 'Pressure Chamber 21a , 21b Pressure chamber portions 22a, 22b Fluid introduction passages 23a, 23b Fluid constant amount feeder 24 Fluid discharge passages

Claims (4)

[Claims] 1. An outer diameter in which a roll shaft is supported by a radial bearing housed in a shaft box, and is inscribed in an inner surface of the shaft box at a position adjacent to the radial bearing on the roll shaft. 2. A roll bearing device, comprising: a piston, the pressure chamber of which is formed in a protruding manner, and a pressure chamber for exerting a fluid pressure on the outer surface of the piston. 2. An outer diameter in which a roll shaft is supported by a radial bearing housed in a shaft box and is inscribed on the inner surface of the shaft box at a position adjacent to the radial bearing on the roll shaft. Of the piston, the pressure chamber partitioned by the piston into inner and outer pressure chambers is formed in the shaft box, and a fluid introduction path for supplying fluid to each of the pressure chambers. Is provided in each of the axle boxes, and each of the fluid introduction paths is connected to a fluid constant quantity feed device adapted to quantitatively feed the fluid, and further, a position facing the neutral position of the piston of the axle box. A roll bearing device, characterized in that a fluid discharge path is provided for discharging fluid from the inside of one of the pressure chambers to the outside according to the position of movement of the piston in the axial direction of the roll axis. 3. A roll bearing having an outer diameter supported by a radial bearing housed in an axle box and inscribed in an inner surface of the axle box at a position adjacent to the radial bearing on the roll axis. A plurality of pressure chambers formed by projecting pistons and partitioned into inner and outer pressure chambers by the pistons are formed in the axial direction in the shaft box, and the pressure chambers on the same side of each pressure chamber are formed. A roll bearing device characterized in that a fluid pressure is simultaneously applied to the parts. 4. A flow control valve for controlling the amount of fluid supplied to the pressure chamber, a displacement meter for detecting the relative position of the roll shaft and the shaft box in the roll axis direction, and a detected value and position by the displacement meter. The roll bearing device according to claim 1 or 3, further comprising a position control device including a controller that compares a set value and sends a control command to the flow control valve.