JP4742857B2 - Metal rolling mill and rolling method - Google Patents

Description

  The present invention relates to a rolling mill for continuously rolling a metal material such as a steel strip while suppressing meandering, and a rolling method of the metal material using the rolling mill.

  In recent years, in the field of hot continuous rolling, various crown control mills such as HC-MILL have been put into practical use, and as a result, it has become possible to stably produce a flat hot rolled steel strip without a plate crown. However, the steel strip is more likely to meander during rolling as much as the plate crown becomes smaller, especially when the tail end of the hot-rolled steel strip falls out, it collides with the side guide and falls down, so-called narrowing. There is a new problem that occurs. Improving the platenability of the tail end of the hot-rolled steel strip in a hot finish rolling mill is a very important issue in order to improve the operation rate and roll basic unit.

  FIG. 9 shows an outline of an HC-MILL rolling mill as an example of a general 6Hi rolling mill. As shown in the figure, in general, rolling mill deformation during rolling is (1) housing deformation, (2) roll deflection (same as axial displacement), (3) flat deformation of roll (compression by rolling load) Elastic deformation of the roll received), (4) shrinkage of the reduction screw (elastic deformation of the reduction screw subjected to compression by the rolling load), (5) deformation of the bearing, change in oil film thickness, (6) rocker plate , Deformation of other members, (7) deformation of the reduction cylinder and deformation of the oil column thickness. According to actual measurement and calculation, the ratio of each part in the amount of change in the roll gap is 40 to 70% for deformation of the roll part, 10 to 16% for deformation of the housing, and 4 to 20% for deformation of the rolling screw. It is known that the ratio of roll deformation is overwhelmingly large (see Non-Patent Document 1, for example).

  During rolling, deformation corresponding to the rolling load occurs in various places, and in the roll gap part that actually determines the thickness of the hot-rolled steel strip after rolling, the roll gap is opened by the sum of the deformation amount. Means that In other words, the rolling mill can be considered as a model in which springs having different spring constants are connected in series. In general, the relationship between the rolling load and the total deformation amount of the rolling mill is called a mill constant, which is a value of about 300 to 800 tons / mm in a hot rolling mill.

  The meandering phenomenon of a hot-rolled steel strip in a rolling mill is generally said to have a second-order integral characteristic. FIG. 10 shows the physical interpretation, and FIG. 10 (A) is a view of the moment when the tail end of the hot-rolled steel strip passes through the work roll as viewed from above. For example, when the hot-rolled steel strip meanders, the rolling load on the side where the steel strip has approached becomes higher than one as shown in FIG. Naturally, since the narrow side of the roll gap is rolled thinner than the other, it is elongated longer in the rolling direction, and the sheet passing speed is slower than the other. For this reason, as shown in FIG. 10 (A), the steel strip bends in a dogleg shape with the rolling part as a boundary. Once the steel strip is bent in this way, the amount of meandering from there increases with time. Accordingly, when the plate path is removed from the roll center as shown in FIG. 10 (B), the mill elongation in the direction in which the steel strip is bent (rightward in FIG. 10 (B)) increases, and the roll gap is opened. As shown in FIG. 10C, the deflection is further promoted to generate a meandering amount proportional to the square of time.

  Further, meandering is more likely to occur as the thickness of the material to be rolled becomes thinner. Since the mass of the steel strip entering the rolling mill and the mass of the steel strip rolled and exiting from the rolling mill are preserved, the following equation (i) holds from the relationship of mass conservation of the material to be rolled. Ψ shown in the right term of the equation (i) represents the rotational speed of the material to be rolled. As Ψ increases, the bending of the steel strip described in FIG. 10C increases and the amount of meander increases. On the other hand, the left term increases as the plate thickness h at the center of the plate width of the material to be rolled, which is the denominator of the left term in equation (i), decreases. That is, as the plate thickness of the material to be rolled is thinner, meandering is more likely to occur.

Where B is the sheet width of the material to be rolled, h is the sheet thickness at the center of the sheet width of the material to be rolled, h _df is the difference between the sheet thicknesses of the material to be rolled, v is the speed of the material to be rolled, and Ψ is the material to be rolled. Indicates the rotation speed. In addition, as for a subscript, 1 shows a rolling mill entrance side, and 0 shows a rolling mill exit side.

  Conventionally, several proposals have been made as a meandering control technique for hot-rolled steel strips to avoid such problems.

  One of them is meandering control (parallel stiffness control) in which the leveling correction amount SL is moved by proportional control so as to cancel out the left-right roll opening difference Sdf generated by the left-right difference Pdf of the rolling load of the rolling mill as shown in FIG. It is. In FIG. 11, α is a control gain (0 to 1), and M is a parallel stiffness. This meandering control technique is a method (generally referred to as leveling operation) for controlling the leveling correction amount SL of a rolling mill reduction device (screw, hydraulic cylinder, etc.) in a direction to suppress meandering according to the following equation (ii). . In the following formulas (ii) to (iv), α is a control gain, Pdf is a left-right difference in rolling load, M is parallel rigidity or left-right rigidity, L is a distance between left and right reduction devices, and yc is a width of a hot rolling line. The meandering amount at the center of the width of the hot-rolled steel strip relative to the center of the direction (hereinafter simply referred to as “meandering amount yc”) is shown. The parallel stiffness or the left / right stiffness M is represented by the ratio of the rolling load left / right difference Pdf and the left / right roll opening difference Sdf at the reduction device position, as shown in the following formula (iii). Further, the relationship between the meandering amount yc and the left-right difference in rolling load is expressed by the following equation (iv). That is, in a rolling mill with a high parallel rigidity M, the left-right difference Pdf of the rolling load or the left-right roll opening difference Sdf due to the meandering amount yc hardly occurs, and as a result, the meandering amount yc does not easily increase with time. . In this proposal, as the time from the tail end of the hot-rolled steel strip passes through the stand immediately before the stand, or the distance from the stand immediately before the stand at the tail end of the hot-rolled steel strip increases, By changing the control gain α shown in the following formula (ii) to be small, it is possible to prevent narrowing when the tail end portion of the hot-rolled steel strip falls out (see, for example, Patent Document 1). ).

SL = −α (Pdf / M) (ii)
M = Pdf / Sdf (iii)
yc = (Pdf · L) / 2P = (Sdf · L) / (2P · M) (iv)
Here, P represents the total rolling load.

Another one of the proposals is a method of controlling the left and right bender force difference of the rolling mill in a direction to suppress meandering. This method controls the parallel rigidity M of the rolling mill by measuring the left-right difference Pdf of the rolling load in the rolling roll and adjusting the left-right bender pressure difference in the rolling roll according to the left-right difference Pdf of the rolling load. And meandering is suppressed (see, for example, Patent Document 2).
JP 9-38710 A Japanese Patent Laid-Open No. 9-248614 Japanese Patent Laid-Open No. 10-267021 Edited by Japan Iron and Steel Institute, “Theory and Practice of Sheet Rolling”, Japan Iron and Steel Institute, September 1, 1984, p.224. The meandering control technique is based on the concept of rigidity control. Patent Document 1 is characterized in that the position of the reduction device is used, and Patent Document 2 is characterized in that the vendor force is the control means.

  The meandering amount yc of the metal material to be rolled (hereinafter simply referred to as the material to be rolled) has a property of increasing as the plate thickness of the material to be rolled decreases. On the other hand, in recent years, there has been an increasing demand from customers for thin objects (generally 2 mm or less in thickness), and it is considered that this trend will further advance in the future. Furthermore, since the sheet feeding speed is increased more than before by reducing the thickness of the rolled material, the current parallel rigidity control according to the above-described difference Pdf in the rolling load of the stand described above allows the response (that is, the control cycle) to pass. There is a problem that the plate speed is insufficient and the meandering cannot be sufficiently followed. Further, from the relationship of mass conservation between the steel strip entering the rolling mill and the steel strip rolled and exiting the rolling mill, meandering is more likely to occur as the plate thickness of the material to be rolled becomes thinner.

  Furthermore, in the control method for adjusting the left and right roll opening difference Sdf shown in Patent Document 1, the roll-down position on the side where the hot-rolled steel strip meanders is lowered, and the roll opening degree is controlled to be narrowed. The rolling load on the side becomes high, that is, the left-right asymmetry such as elastic deformation of the roll and elongation of the housing is increased. For this reason, in order to counteract the rolling asymmetry factor in addition to the reduction tightening amount necessary for preventing meandering, it is necessary to further reduce the reduction position and narrow the roll opening, resulting in a control response speed. It acts in a disadvantageous direction. For the above reasons, even in the rolling mill using the parallel stiffness control as shown in Patent Document 1, the current drawing troubles are caused by meandering.

  In addition, the meandering control using the vendor force difference in Patent Document 2 is also responsive even when the servo-hydraulic actuator boasting high output and high response among the existing technologies is used as the drive source, as in Patent Document 1. Is not enough.

  Accordingly, the object of the present invention is to solve the problems of the current parallel rigidity control that cannot cope with the thinning of the material to be rolled, to obtain a good rolled material shape, and to perform stable meander control, An object of the present invention is to provide a rolling mill and a rolling method for a metal material that can stably produce a metal material such as a hot-rolled steel strip without causing trouble.

  In order to solve the above-mentioned problems, the present inventors pay attention to the fact that the parallel rigidity M in a general rolling mill is dominated by elastic deformation between the work roll and the backup roll, that is, the left-right roll flatness difference. Between the roll chock of the roll and the roll chock of the intermediate roll (hereinafter referred to as between the work chock and the roll chock of the intermediate roll) and / or between the roll chock of the intermediate roll and the backup roll (hereinafter referred to as the intermediate roll and the backup roll). By sandwiching a rigid member as a tensioning means between the roll chock), it is possible to suppress the occurrence of left-right roll flatness due to the meandering amount yc of the rolled material without special control, and to meander the rolled material It was found that can be effectively prevented.

  However, the gap between the roll chock of the actual work roll and the roll chock of the intermediate roll and the gap between the roll chock of the intermediate roll and the roll chock of the backup roll change depending on the roll diameter, so every two to three hours on a general hot rolling line It is necessary to adjust the height (vertical direction) dimension of the rigid member every time the regular roll is changed. Furthermore, even during rolling with the same roll, the gap between roll chocks changes depending on the operating conditions such as the dimensions of the material to be rolled, the rolling load, the bender force, etc. In addition, even during the rolling of a single steel strip, the operating conditions are from moment to moment. And change. For this reason, interposing a rigid body of constant dimensions between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll is a disturbance of various controls carried out in the operation. Thus, there is a possibility of causing defects such as shape defects, and further troubles such as perforation and plate breakage. Therefore, as a result of studying the configuration of a rigid member that does not cause such a problem, a wedge laminated block in which a plurality of wedge bodies can be slidably overlapped to adjust the height is suitable for the gap fluctuation between roll chocks. It has been found that this is the most suitable means for forming a high-strength stretch between the roll chock.

The present invention has been made based on such findings, and the features thereof are as follows.
[1] have a roll chock between the holding device having an actuator following wedge laminated block and the following (a) (b), said actuator and wedge stacked blocks, with is installed in the holding frame, wherein the actuator The at least one wedge body of the wedge laminated block fixed to the holding frame is slidable in a horizontal direction with respect to the surface of the holding frame to which the actuator is fixed by the actuator, and the holding frame is A metal rolling mill characterized by being fixed to a roll chock of an intermediate roll .
(A) It is arranged between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll, so that it functions as a tensioning means between the roll chocks and the wedge tip side is reversed. Wedge stacking block comprising a plurality of wedge bodies that are slidably stacked so that their inclined surfaces are slidable in the gradient direction of the inclined surface, and at least one wedge body slidingly moves relative to the other wedge bodies .
(B) An actuator for slidably moving at least one wedge body constituting the wedge laminated block with respect to another wedge body and holding it at an arbitrary slide position.
[2] have a roll chock between the holding device having an actuator wedge laminated block and the following (b) below (a), the actuator and wedge laminated blocks consisting of two wedge is installed in the holding frame The actuator is fixed to the holding frame, and one wedge body of the wedge stacking block is slidably installed on the surface of the holding frame to which the actuator is fixed by the actuator. A metal material rolling machine fixed to a roll chock of an intermediate roll .
(A) It is arranged between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll, so that it functions as a tensioning means between the roll chocks and the wedge tip side is reversed. Wedge stacking block comprising a plurality of wedge bodies that are slidably stacked so that their inclined surfaces are slidable in the gradient direction of the inclined surface, and at least one wedge body slidingly moves relative to the other wedge bodies .
(B) An actuator for slidably moving at least one wedge body constituting the wedge laminated block with respect to another wedge body and holding it at an arbitrary slide position.
[3] A rolling mill for a metal material according to the above [1] or [2] , which is a rolling mill for producing a hot-rolled steel strip.
[4] A method of rolling a metal material using the rolling mill according to any one of [1] to [3 ] above, between a roll chock of a work roll and an intermediate roll and / or between a roll chock of an intermediate roll and a backup roll. A rolling method for a metal material, characterized in that the wedge laminated block is held at a predetermined height, and the wedge laminated block forms a tension means for increasing the parallel rigidity of the rolling mill during rolling.

  According to the present invention, a wedge laminated block that can function as a stretching means for maintaining a roll chock interval is interposed between the work chock of the rolling mill and the roll chock of the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll. The parallel rigidity of the rolling mill can be effectively increased by causing the rolling mill to function as a stretching means at a predetermined timing. For this reason, generation | occurrence | production of the left-right roll flatness by the meandering amount yc of a to-be-rolled material can be suppressed, without becoming a disturbance factor of the existing rolling control, and the meandering of a to-be-rolled material can be suppressed effectively. In particular, in the production of thin hot-rolled steel strips, it is possible to achieve a good and stable sheeting, and to improve the line operating rate and roll basic unit by suppressing squeezing troubles, while achieving excellent quality hot-rolled steel strips. Can be manufactured stably.

  Further, the rolling mill of the present invention is provided with a roll chock gap holding device between the work roll chock and the roll chock of the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll, and this is installed in a higher control system of the rolling mill itself. Because it is only necessary to control it so that it functions as a stretching means at the timing when it is desired to suppress meandering with a simple control system independent of the rolling device, the rolling device itself does not need to respond quickly and can be easily applied to existing rolling mills. can do. Therefore, even an existing rolling mill having only a control system with a considerably slow control cycle or a rolling device with a slow response can be applied without any problem, and the meandering of the metal material can be effectively suppressed. On the other hand, even when applied to a rolling mill that has a reduction device that has a quick response and has the latest control system with a fast control cycle, the meandering suppression effect can be realized to a higher degree.

  Hereinafter, details and preferred embodiments of the present invention will be described by taking a hot rolling mill and production of a hot-rolled steel strip using the same as an example.

  1 and 2 show an embodiment of the hot rolling mill of the present invention and the rolling situation thereof, and FIG. 1 is a front view of the hot rolling mill. Moreover, FIG. 2 shows the use condition of the holding apparatus between roll chock provided between either one of the right and left roll chock of the upper backup roll and the upper intermediate roll of the hot rolling mill. The basic structure of this hot rolling mill (rolling stand) is the same as that of the conventional apparatus. Upper and lower work rolls 1a and 1b, upper and lower intermediate rolls 21a and 21b for supporting these work rolls in the vertical direction, and these intermediate rolls Upper and lower backup rolls 22a and 22b that are supported on the upper and lower sides, respectively, and a roll support portion 6 (housing) that supports both ends of each roll. The upper and lower work rolls 1a and 1b, the upper and lower intermediate rolls 21a and 21b, and the upper and lower backup rolls 22a and 22b have roll chock 3, 41, 42 (upper work roll chock 3a, lower work roll chock 3b, upper intermediate roll chock 41a). , Lower intermediate roll chock 41b, upper backup roll chock 42a, lower backup roll chock 42b), and roll chocks 3, 41, 42 of these rolls are held in the roll support portion 6 so as to be slidable in the vertical direction.

  Each roll has a structure in which the lower backup roll 22b, the lower intermediate roll 21b, the lower work roll 1b, the upper work roll 1a, the upper intermediate roll 21a, and the upper backup roll 22a are stacked in this order from the lower side of the apparatus (note that the figure is rolled) Since the inner state is shown, a steel strip 17 as a material to be rolled is interposed between the upper and lower work rolls 1a and 1b). In addition, the roll chock 42b of the lower backup roll 22b is supported by the support means 7 on the roll support portion 6 side, while the roll chock 42a of the upper backup roll 22a is moved upward by the reduction device 8 (such as a reduction cylinder) on the roll support portion 6 side. It is restrained and crushed from. Therefore, the rolling load by the rolling means 8 is as follows: upper backup roll chock 42a → upper backup roll 22a → upper intermediate roll 21a → upper work roll 1a → (metal material 17) → lower work roll 1b → lower middle roll 21b → lower backup. It is transmitted along the route of the roll 22b → the lower backup roll chock 42b and is received by the support means 7.

  In addition to such a basic structure, in the hot rolling mill of this embodiment, between the left and right roll chocks 3 and 41 of the upper and lower work rolls 1 and the intermediate roll 21, and between the upper and lower intermediate rolls 21 and the backup roll 22 An inter-roll chock holding device 5 having a tensioning means capable of holding the left and right roll chocks 41 and 42 at an arbitrary interval is provided.

  The inter-roll chock holding device 5 includes a wedge laminated block 9 and an actuator 10. The wedge laminated block 9 is disposed between the left and right roll chocks 3 and 41 of the work roll 1 and the intermediate roll 21 and between the right and left roll chocks 41 and 42 of the intermediate roll 21 and the backup roll 22. It consists of a plurality of wedge bodies functioning as a tension means. The actuator 10 slides at least one wedge body constituting the wedge laminated block 9 with respect to the other wedge bodies and holds it at an arbitrary slide position.

  The wedge laminated block 9 is composed of a plurality of wedge bodies in which the inclined surfaces of the wedges are slidably overlapped with each other so that the front end side of the wedge is reversed, and at least one wedge body is attached to another wedge body. The height (the length in the direction between the roll chocks) is made variable by sliding, and in this embodiment, two wedge bodies 11x and 11y (in FIGS. 2 to 5 and FIG. 11x on the side, 11y on the upper side, and in FIG. 6, 11x on the upper side and 11y on the lower side.

  In FIG. 2, one wedge body 11 x is installed so as to be movable and slidable in the roll axis direction by an actuator, and the other wedge body 11 y is installed so as to be slidable against one wedge body. That is, the height (height dimension) of the wedge laminated block 9 is changed by sliding the wedge body 11y in the inclined surface gradient direction with respect to the wedge body 11x.

  Since the intervals between the roll chocks 3 and 41 and between the roll chocks 41 and 42 also change depending on the roll diameters of the work roll 1, the intermediate roll 21 and the backup roll 22, the wedge laminated block according to the roll exchange performed regularly. Perform zero adjustment of height 9 (height dimension). Specifically, when the roll exchange is completed and rolling is not performed, the gap between the roll chocks 3 and 41 and the wedge laminated block 9 and / or the gap between the roll chocks 41 and 42 and the wedge laminated block 9 are used. Until there is no more, the height (height dimension) of the wedge laminated block 9 is increased and stored as 0 position by an encoder or the like attached to the actuator. Thereafter, the wedge laminated block 9 is set such that the gap between the roll chocks 3 and 41 and the wedge laminated block 9 and / or the gap between the roll chocks 41 and 42 and the wedge laminated block 9 have a predetermined interval (for example, 3 mm). The height (height dimension) is reduced to prepare for rolling.

  In the present embodiment, the actuator 10 is constituted by a hydraulic cylinder provided with a cylinder body 12 and an actuating (driving) rod 13. In the hydraulic cylinder, the operating rod 13 is connected to the wedge body 11x, and the slide body is slid with respect to the wedge body 11y, and the wedge body 11x is held at an arbitrary slide position.

  When the wedge laminated block 9 functions as a tensioning means between the roll chocks, a large compressive load acts. Therefore, the wedge laminated block 9 and the actuator 10 constituting the roll chock holding device 5 can sufficiently withstand the load. It is necessary.

  Usually, the wedge body 11 constituting the wedge laminated block 9 is made of a metal material. The metal material preferably has a predetermined rigidity and is excellent in heat resistance and low thermal expansion. For example, various metal materials such as an aluminum alloy can be used, and among them, particularly from Fe-36 mass% Ni. An invar alloy or the like is desirable. In addition, in order to improve the slipperiness between the inclined surfaces (sliding surfaces) of the wedge body 11, a covering layer (for example, one coated with a fluorine resin or the like) may be provided on the inclined surfaces.

  Further, the actuator 10 needs a holding force (rigidity) for holding the wedge body 11x at a predetermined slide position against the load. Therefore, for example, when the actuator 10 is configured by a hydraulic cylinder such as a hydraulic cylinder device, a normal hydraulic cylinder may be used. In particular, a hydraulic cylinder having a function of locking the cylinder stroke with high rigidity is used. Is preferred. As such a hydraulic cylinder, for example, as shown in Patent Document 3, the cylinder stroke is locked with high rigidity by friction between the inner peripheral surface of the outer member of the hydraulic cylinder and the outer peripheral surface of the inner member. A hydraulic cylinder device having a function may be mentioned. In addition, a hydraulic cylinder having a sealing mechanism (lock mechanism) that can lock the working rod 13 in a predetermined extended state by containing the working fluid in the cylinder body 12 may be used. This sealing mechanism can be constituted by, for example, an electromagnetic gate valve provided in a liquid flow path for supplying a working liquid. The electromagnetic gate valve blocks the fluid flow path, and the working fluid is contained in the cylinder body 12. Thus, the operating rod 12 is locked in a predetermined extended state.

  Moreover, you may use what has a lock mechanism which mechanically locks the operating rod 13 of a hydraulic cylinder. There is no particular limitation on the configuration of the lock mechanism. For example, the engaging rod 13 is mechanically engaged with an engaging portion (for example, a concave portion, a hole, a rack portion, etc.) provided on the operating rod 13, so that the operating rod 13 is moved. Locking means such as engaging means for restraining can be used. In this case, a spring, an actuator, or the like can be used to drive the engagement means.

  In addition, in the hydraulic cylinder in which the cylinder body as described above has a locking function, if the mechanical locking mechanism is used in combination, the tension function between the roll chocks by the hydraulic cylinder is made more reliable. Can do.

  In addition to the hydraulic cylinder, for example, an actuator of an appropriate type such as a screw type actuator having a self-locking function when a load is applied as described later can be used as the actuator 10.

  FIG. 3 shows an embodiment in which a screw-type actuator is used as the actuator 10 of the inter-roll chock holding device 5, and between one of the upper intermediate roll and the upper backup roll (right side in the case of this figure). The use condition of the holding apparatus 5 between roll chocks provided in is shown.

  The screw-type actuator constituting the actuator 10 includes a device main body 14 having a motor and a screw shaft 15 rotatably held by the device main body 14 and rotated by the motor. The screw shaft 15 is the wedge. It is connected to the wedge body 11x by being screwed into a female screw hole (not shown) penetrating the body 11x. Then, by rotating the screw shaft 15, the wedge body 11x is slid with respect to the wedge body 11y, and the wedge body 11x is held at an arbitrary slide position.

  In the rolling mill of the present invention, at least one wedge body 11 x among the plurality of wedge bodies 11 constituting the wedge laminated block 9 is installed so as to be movable and slidable in the roll axis direction by the actuator 10. Is slidably brought into contact with one wedge body. Therefore, the height of the wedge laminated block can be varied by sliding the at least one wedge body relative to the other wedge bodies. Therefore, the inter-roll chock holding device 5 having the wedge laminated block 9 and the actuator 10 may be fixed to any of the roll chock 3 of the work roll 1, the roll chock 41 of the intermediate roll 21, or the roll chock 42 of the backup roll 22. However, in a rolling mill for producing a metal material such as a hot-rolled steel strip, the work roll 1 is frequently replaced, whereas the replacement frequency of the intermediate roll 21 and the backup roll 22 is not so high. Therefore, in consideration of labor and maintainability installed between the roll chocks 3 and 41 and between the roll chocks 41 and 42, the inter-roll chock holding device 5 is preferably fixed to the roll chock 41 of the intermediate roll 21.

  Further, by adopting a structure in which the inter-roll chock holding device 5 is fixed to the roll chock 41 of the intermediate roll 21 as described above, the maintenance of the inter-roll chock holding device 5 can be synchronized with the regular backup roll replacement, Smooth operation is possible without degrading the line operation rate by the detaching work of No. 5. Moreover, since maintenance between the roll chock holding devices 5 can be performed offline together with the used backup rolls, it is possible to avoid a rolling trouble due to failure of the devices.

  Further, the wedge laminated block 9 is constituted by two wedge bodies 11x and 11y, the actuator 10 is fixed to the roll chock, and the lower wedge body 11x is slid by the actuator 10, and the upper wedge body 11y is further moved. When fixed to the roll chock, the height of the connecting portion between the wedge body 11 and the actuator 10 does not fluctuate even if the lower wedge body 11x slides. For this reason, the connection structure of the actuator 10 and the wedge body 11 can be simplified, and a structure excellent in maintainability can be obtained. 4 and 5 show an embodiment of such a structure. FIG. 4 shows a case where a hydraulic cylinder device is used as the actuator 10, and FIG. 5 shows a case where a screw type actuator is used as the actuator 10. Yes. 4 (A) and 5 (A) show the state in which the height of the tensioning block 9 is lowered (front view and AA 'cross-sectional view thereof), FIG. 4 (B) and FIG. 5 (B). Fig. 4 shows a state in which the height of the tensioning block 9 is increased (a front view and a sectional view taken along line AA ').

  4 and 5, the upper wedge body 11y is fixed to the roll chock 42 (upper roll chock 42a), and the actuator 10 (the operating rod 13 or the screw shaft 15) is connected to the lower wedge body 11x. And slide it. In addition, a ridge 110 is formed at the center in the width direction of the inclined surface of the lower wedge body 11x, and the length of the inclined surface is formed in the center of the inclined surface of the upper wedge body 11y in the width direction. A concave groove 111 is formed along the direction, and the inclined surface of the lower wedge body x is slidably brought into contact with the inclined surface of the upper wedge body 11y so that the protrusion 110 is engaged with the concave groove 111. ing.

  Since the work roll 1, the intermediate roll 21 and the backup roll 22 are periodically exchanged together with the roll chocks 3, 41 and 42, the roll chock holding device 5 including at least the wedge laminated block 9 and the actuator 10 is used. It is preferable from the viewpoint of simplification of the apparatus configuration and ease of detachment that the unit is configured as one unit and attached to any one of the roll chocks 3, 41, 42. Further, since the roll replacement frequency is smaller in the intermediate roll 21 and the backup roll 22 than in the work roll 1 as described above, in particular, the roll chock holding device 5 unitized in the roll chock 41 of the intermediate roll 21 is used. Is preferably attached. As a specific structure, a holding frame, an actuator fixed to the holding frame, and a wedge laminated block including two wedge bodies, one of which is held by the actuator and the holding frame. A unit provided with a wedge laminated block 9 that can slide relative to the surface, a roll chock 42 of the backup roll 22, a roll chock 41 of the intermediate roll 21 or a roll chock 3 of the work roll 1 through the holding frame, particularly preferably, The structure fixed to the roll chock 41 of the intermediate roll 21 is preferable.

  6 and 7 show an embodiment of such a structure. FIG. 6 shows an embodiment in which the unitized roll chock holding device 5 is attached to the upper roll chock 41a, and FIG. 7 shows an embodiment in which the unitized roll chock holding device 5 is attached to the lower roll chock 41b. As described above, it is preferable that the unitized roll chock holding device 5 is attached to the roll chock 41 of the intermediate roll 21. Therefore, FIG. 6 shows the gap between the upper work roll 1a and the roll chock 3a, 41a of the intermediate roll 21a. FIG. 7 is applied between the lower work roll 1b and the roll chock 3b, 41b of the intermediate roll 21b. 6 (A) and 7 (A) show a state in which the height of the tension block 9 is lowered (a front view and a cross-sectional view taken along the line A-A 'in FIG. 6 (B) and FIG. 7 (B). The state (front view and AA 'sectional view thereof) in which the height of the block 9 is increased is shown. Moreover, although each embodiment of FIG.6 and FIG.7 has shown the example which applied the screw type actuator as an actuator, appropriate things, such as a hydraulic cylinder apparatus, can be applied as an actuator.

  In FIG. 6, the unitized roll chock holding device 5 includes a holding frame 16, an actuator 10 fixed to the inner upper surface 160 of the holding frame 16 (for example, fixing by bolting), and a wedge laminated block 9. The wedge laminated block 9 has two wedge bodies 11x and 11y. Among the wedge bodies 11, the upper wedge body 11 x is connected to the actuator 10. In this embodiment, the upper roll chock is the roll chock 41 of the intermediate roll 21, and the lower roll chock is the roll chock 3 of the work roll 1, and the holding frame 16 is fixed to the roll chock 41.

  The holding frame 16 is not particularly limited. In the present embodiment, the holding frame 16 has a box shape with an open bottom, and the actuator 10 and the wedge laminated block 9 are accommodated inside the box.

  The upper wedge body 11x is connected to the screw shaft 15 (actuating rod 13 in the case of a hydraulic cylinder device) of the actuator 10, whereby the wedge body 11x is held by the actuator 10. The planar upper surface of the wedge body 11x is in contact with the surface of the holding frame 16 to which the actuator 10 is fixed, that is, the inner upper surface 160 of the holding frame 16 so as to be slidable.

  In addition, a ridge 110 is formed in the width direction center of the inclined surface of the upper wedge body 11x along the inclined surface gradient direction, and both sides of the ridge 110 have the same inclination as the inclined surface. A guide protrusion 112 is provided along the gradient direction of the protrusion 110. On the other hand, a concave groove 111 along the inclined surface gradient direction is formed at the center in the width direction of the inclined surface of the lower wedge body 11y, and the same inclination as the inclined surface is formed on both side surfaces inside the concave groove 111. A guide groove 113 having a groove is formed along the inclined surface gradient direction of the concave groove 111.

  Then, with the inclined surface of the upper wedge body x slidably in contact with the inclined surface of the lower wedge body 11y, the protrusion 110 of the wedge body 11x is fitted in the concave groove 111 of the wedge body 11y. The guide protrusion 112 of the wedge body 11x is slidably fitted (engaged) in the guide groove 113 of the wedge body 11y. By such engagement between the guide protrusion 112 and the guide groove 113, the wedge body 11x can hold the wedge body 11y as shown in FIG.

  The holding frame 16 has stopper portions 162 and 163 facing both ends of the wedge body 11y, and the wedge body 11y is locked (restrained) by the stopper portions 162 and 163 so as not to move in the roll axis direction. Is done. That is, the wedge body 11y is substantially movable only in the vertical direction by engaging the both ends thereof with the stoppers 162 and 163, and the engagement between the guide protrusion 112 and the guide groove 113 as described above. Thus, while being held by the wedge body 11x, the actuator 10 moves up and down as the wedge body 11x slides.

  The unitized roll chock holding device 5 as described above has its holding frame 16 fixed to the upper roll chock 41 (roll chock 41a) with bolts or the like by fixing the outer upper surface 161 to the roll chock 3, 41 (roll chock 3a, 41a). ).

  When the unitized roll chock holding device 5 is attached, the unitized roll chock holding device 5 is fixed to the roll chock 41 of the intermediate roll 2 before being set in the rolling mill when the intermediate roll is replaced. By being incorporated in the rolling mill, the unitized roll chock holding device 5 is installed between the roll chocks 3 and 41.

  Further, the embodiment of FIG. 7 has a structure upside down from the embodiment of FIG. 6, and the unitized roll chock holding device 5 includes a holding frame 16 and an inner side of the holding frame 16. The actuator 10 is fixed to the bottom surface 160 (for example, fixed by bolting), and the wedge laminated block 9 includes two wedge bodies 11x and 11y, and the actuator 10 is connected to the lower wedge body 11x. Yes. In this embodiment, the lower roll chock is the roll chock 41 of the intermediate roll 21, and the upper roll chock is the roll chock 3 of the work roll 1.

  The holding frame 16 is not particularly limited. In the present embodiment, the holding frame 16 has a box shape with an open upper surface, and the actuator 10 and the wedge stacked block 9 are housed inside the box shape.

  A screw shaft 15 (an operating rod in the case of a hydraulic cylinder device) of the actuator 10 is connected to the lower wedge body 11x, and the wedge body 11x is held by the actuator 10. The planar lower surface of the wedge body 11x is in contact with the inner bottom surface 160 of the holding frame 16 so as to be slidable.

  In addition, a ridge 110 is formed along the inclined surface gradient direction at the center of the inclined surface of the lower wedge body 11x in the width direction, and both sides of the ridge 110 have the same inclination as the inclined surface. The guide ridge 112 protrudes along the gradient direction of the ridge 110. On the other hand, a concave groove 111 is formed along the inclined surface gradient direction in the center of the inclined surface of the upper wedge body 11y, and the same inclination as the inclined surface is formed on both side surfaces of the concave groove 111. A holding guide groove 113 is formed along the gradient direction of the concave groove 111.

  Then, with the inclined surface of the lower wedge body x slidably in contact with the inclined surface of the upper wedge body 11y, the protrusion 110 of the wedge body 11x is fitted in the concave groove 111 of the wedge body 11y. The guide protrusion 112 of the wedge body 11x is slidably fitted (engaged) in the guide groove 113 of the wedge body 11y. By the engagement between the guide protrusion 112 and the guide groove 113, the wedge body 11x can hold the wedge body 11y as shown in FIG.

  The holding frame 16 has stopper portions 162 and 163 facing both ends of the wedge body 11y, and the wedge body 11y is locked (restrained) by the stopper portions 62 and 163 so as not to move in the roll axis direction. Is done. That is, the wedge body 11y is substantially movable only in the vertical direction by engaging the both ends thereof with the stoppers 162 and 163, and the engagement between the guide protrusion 112 and the guide groove 113 as described above. Thus, while being held by the wedge body 11x, the actuator 10 moves up and down as the wedge body 11x slides.

  The unitized roll chock holding device 5 is arranged between the roll chocks 3 and 41 and / or between the roll chocks 41 and 42 by fixing the outer bottom surface 161 of the holding frame 16 to the roll chock 41 with bolts or the like. Is done.

  When the unitized roll chock holding device 5 is actually attached, the unitized roll chock holding device 5 is fixed to the roll chock 41 of the intermediate roll 21 before being set in the rolling mill when the intermediate roll is replaced. By incorporating into the rolling mill, the unitized roll chock holding device 5 is installed between the roll chocks 3 and 41 and / or between the roll chocks 41 and 42.

  The holding frame 16 that holds the wedge laminated block 9 and the actuator 10 may be made of any material that has excellent corrosion resistance in consideration of the cooling water used in the surroundings, such as stainless steel. create.

  Further, the shape is a box shape having a rectangular top view and an open top surface (or bottom surface), and two edges in the longitudinal direction of the bottom surface (or top surface) project horizontally. A hole for passing a jig for fixing to the roll chock 3, 41, 42 is provided in the overhanging edge. All the surfaces constituting the rectangular box shape may be covered with the plate of the above-mentioned material, or only the rectangular frame may be used. As long as the wedge laminated block 9 and the actuator 10 are accommodated inside the box shape, the actuator 10 can be fixed, and one of the wedge bodies 11 not connected to the actuator 10 can contact the roll chock. There is no particular limitation. Therefore, the shape shown in FIG. 6 and FIG. 7 is most preferable in view of the ease of manufacture, the ease of fixing to the roll chock, etc.

  The actuator 10 may be fixed to the holding frame 16 as long as the actuator itself is positioned with respect to the reaction force of the actuator, and the fixing method may be bolt fixing to the frame side, A key structure may be provided by providing unevenness on the side, and may be appropriately selected according to the shape of the frame, the shape of the actuator, and the like.

  Since the acting force and reaction force of the actuator as described above are included in the holding frame 16, when the inter-roll chock holding device 5 is fixed to the roll chocks 3, 41, 42, the holding frame 16 is used as a roll chock. Fix it. In the present embodiment shown in FIG. 6 or FIG. 7, the holding frame outer top surface or outer bottom surface 161 is fixed to the roll chock 41 of the intermediate roll 21 using the above-described overhanging edge. This fixing method is not particularly limited, such as bolt tightening or wire fixing, and it is sufficient that the device does not move into and out of the rolling mill due to vibration during rolling or does not function as a tensioning means due to a large positional shift, and can be removed. If possible.

Moreover, the wedge laminated block 9 can also be comprised by three or more wedge bodies. Figure 8 shows an embodiment of a case where the wedge laminated block 9 with three wedge 11, respectively on the upper side of the wedge 11z ₁ is roll chocks 42, wedge member 11z ₂ the lower the roll chocks 41 In addition to being fixed, a central wedge body 11w is slidable with respect to the upper and lower wedge bodies 11z ₁ and 11z ₂ , and the actuator 10 (the operating rod 13 or the screw shaft 15) is connected to the wedge body 11w for sliding movement. Like to do. However, in this case, since the height of the connecting portion between the wedge body 11w and the actuator 10 fluctuates as the wedge body 11w slides, the actuator 10 can be tilted or moved up and down following this, for example, the connecting portion of the actuating member of wedge 11z ₁ and the actuator 10 (actuating rod 13 or the screw shaft 15) and vertically rotatable pivot structure, and the support portion of the actuator 10 is also vertically rotatable pivot Part.

  In the case of the HC-MILL rolling mill shown in FIG. 14, the intermediate roll has a function of controlling the shape of the material to be rolled by changing the position in the roll axis direction. For this reason, the relative position in the roll axis direction between the roll chocks 3 and 41 and the roll chocks 41 and 42 on which the wedge laminated block 9 applies the tensile force is shifted, and in the worst case, the tensile force cannot be exhibited. In this case, when installing the inter-roll chock holding device 5 on the roll chock 41 of the intermediate roll 21, pay attention to the position in the roll axial direction, the number of the roll chock holding devices 5 to be installed, etc. The meandering suppression effect can be exhibited.

  The roll chock holding device 5 is provided between the upper roll chock 3a and 41a, between the upper roll chock 41a and 42a, between the lower roll chock 3b and 41b, and between the lower roll chock 41b and 42b. May be. However, since the effect is reduced by half when it is provided at any of the positions, the roll rolls of the work roll 1, the intermediate roll 21 and the backup roll 22 (ie, 3a) on both the upper and lower sides and the work roll 1, as in this embodiment. And between 41a and 41a, between 3b and 41b, between 41a and 42a, and between 41b and 42b). Similarly, it may be provided between the left and right roll chocks 3 and 41 and between the left and right roll chocks 41 and 42. However, since the effect is reduced by half when it is provided in any of the positions, the roll rolls of the work roll 1, the intermediate roll 21 and the backup roll 22 between the right and left sides and the work roll 1, as in this embodiment (ie, 3 and It is most preferable to provide it between 41 and both sides of 41 and 42. Then, which roll chock holding device 5 is to be operated may be appropriately determined according to the meandering state of the steel strip 17.

Here, in the rolling mill of the present invention, as the means for stretching between the roll chocks 3 and 41 and between the roll chocks 41 and 42 as described above, the inter-roll chock holding device 5 provided with the wedge laminated block 9 is used. The reason is as follows.
(A) The wedge laminated block 9 provides a strong holding force as a means for stretching between the roll chocks 3 and 41 and between the roll chocks 41 and 42, and ensures high parallel rigidity of the rolling mill.
(B) When it is not necessary to hold the gap between the roll chocks 3 and 41 and between the roll chocks 41 and 42 with the tensioning means, the tensioning block 9 increases the height by following the variation in the distance between the roll chocks 3 and 41. By making it change, the operation | movement which does not prevent the fluctuation | variation of the distance between roll chock 3 and 41 and between roll chock 41 and 42 can be performed easily.
(C) Even if the wedge laminated block 9 copes with the change in the distance between the roll chock 3 and 41 and the roll chock 41 and 42 due to the exchange of the work roll, the intermediate roll and the backup roll, it should be handled without any problem. Can do.

  Next, a metal material rolling method using the rolling mill of the present invention as described above will be described. In this rolling method, the wedge laminated blocks 9 provided between the left and right roll chocks 3 and 41 of the work roll 1 and the intermediate roll 21 and between the roll chocks 41 and 42 of the intermediate roll 21 and the backup roll 22 are arranged in a predetermined manner. The wedge laminated block 9 is held at a height, and a stretching means for increasing the parallel rigidity during rolling is formed. Specifically, the wedge body 11 of the wedge laminated block 9 between the left and right roll chocks (that is, between 3a and 41a, between 3b and 41b, between 41a and 42a, and between 41b and 42b) is used as the actuator 10. By sliding and holding at a predetermined position, a stretching means for holding the work roll 1 and the intermediate roll 21 and the intermediate roll 21 and the backup roll 22 in parallel is formed.

  However, the formation of the tensioning means is performed at a predetermined timing for achieving the meandering suppression effect during rolling, and the tensioning means is not formed during the other rolling periods. This is because it is preferable that the roll chock gap changes depending on the operating conditions such as the dimensions of the material to be rolled, the rolling load, the vendor force, and the like so that the change in the roll chock gap due to such factors is not inhibited as much as possible during the rolling of the metal material. It is.

  For example, as shown in FIG. 12 (A), in normal rolling, the width of the steel strip 17 is smaller than the width of the work roll 1, and the work roll 1 is greatly bent at the center of the trunk, thereby causing the steel strip 17 to be convex. It will be rolled into a shape. On the other hand, since it is desired that the steel strip 17 be rolled as flat as possible, a method of controlling the bending of the work roll 1 by applying a vendor force to the work roll chock 3 as shown in FIG. It is used for. On the other hand, since the distance between the roll chocks 3 and 41 and / or the distance between the roll chocks 41 and 42 is constantly changed by the vendor force control, if the tensioning means of the wedge laminated block 9 is always acted during the rolling period, It will inhibit the function.

  For this reason, until the time when it is desired to exert the meandering suppression effect, as shown in FIG. 3A, between the wedge laminated block 9 and the roll chock 3, 41 and / or between the wedge laminated block 9 and the roll chock 41, 42 Wait with a gap between them. Then, the gap between the wedge laminated block 9 and the drive speed in the height (height dimension) is divided by the time before the desired time at which the meandering suppression effect is desired to be in the state shown in FIG. 3B. Control of the device starts from the timing. As described above, this control system may be a separate control system that is independent from the upper control system of the rolling mill itself, and does not need to have a high response speed.

  In using the rolling mill of the present invention, it is necessary to consider the contact surface accuracy between the wedge laminated block 9 and the roll chock 3, 41, 42. For example, since the upper and lower surfaces of the roll chock in a rolling mill provided in a normal hot rolling line are hardly maintained, it is often the case that unevenness due to corrosion, distortion due to repeated load, etc. are generated. For this reason, even when the wedge laminated block 9 is simply sandwiched between the upper and lower roll chocks, it has been confirmed through experiments that a rattling load of about 10 tons is required before sufficient rigidity is obtained. For this reason, it is preferable that the inter-roll chock holding device 5 is operated under the following conditions.

For example, regarding the operation method in the case of using a hydraulic cylinder, particularly a hydraulic cylinder having a function of locking (fixing) the operating rod with high rigidity as the actuator 10 of the inter-roll chock holding device 5, the upper intermediate roll and the upper backup roll It demonstrates using FIG. 2 which shows the use condition of the holding | maintenance apparatus 5 between roll chocks provided between either one of the right and left roll chocks 41 and 42. FIG.
(1) When the roll chock holding device 5 is not used (usually not rolling), the operating rod 13 of the hydraulic cylinder constituting the actuator 10 is retracted to the minimum stroke position as shown in FIG. Keep it. For this reason, a gap exists between the wedge laminated block 9 and the roll chock 42.
(2) As shown in FIG. 2 (B), after the material to be rolled is caught in the rolling mill and until the tail end of the rolling mill exits the rolling mill, And a hydraulic cylinder constituting the actuator 10 is operated at a constant pressure so as to kill the rattle between the wedge laminated block 9 and the roll chock 41, and between the wedge laminated block 9 and the roll chock 42 and the wedge laminated Between the block 9 and the roll chock 41, it is assumed that a certain level of rattle killing force (relatively small tensile force) is applied. In normal hot rolling, the thickness of the work roll 1 and the intermediate roll 21 is reduced even during rolling of one steel strip 17 by controlling the thickness in consideration of a temperature decrease (thermal rundown) in the tail end direction of the material to be rolled. The gaps between the roll chocks 3 and 41 and between the roll chocks 41 and 42 of the intermediate roll 21 and the backup roll 22 change from moment to moment, but the height of the wedge laminated block 9 depends on the action of the hydraulic spring of the hydraulic cylinder. It changes following this gap change.
(3) The lock mechanism of the hydraulic cylinder is operated at the timing when the meandering suppression effect of the material to be rolled by the roll chock holding device 5 is desired. As a result, the gap between the roll chocks 41 and 42 and the wedge laminated block 9 is 0 mm, and the position can be held in a state in which the rattle killing force is applied. In particular, in the case of a hydraulic cylinder having a function of locking the actuating rod 13 with high rigidity, the actuating rod 13 is locked at a predetermined stroke position (for example, locked by a cylinder interference fitting effect).
(4) Thereafter, when the roll chocks 41 and 42 are acted in a direction in which the distance between the roll chocks 41 and 42 is further narrowed by meandering of the material to be rolled, as shown in FIG. Therefore, a stretching means is formed between the roll chocks 41 and 42, and the meandering suppression effect is exhibited.

  In the method using a hydraulic cylinder (particularly, a hydraulic cylinder having a function of locking the operating rod with high rigidity) as the actuator 10 as described above, it is possible to wait in a state where a rattling load is applied, from the standby position. Since it is possible to enter the stretching means forming operation (for example, the locking operation) as it is, the response is fast.

Moreover, about the operation method at the time of using a screw type actuator as the actuator 10 of the holding apparatus 5 between roll chock, the use condition of the holding apparatus 5 between roll chocks provided between the roll chocks 41 and 42 of an upper intermediate roll and an upper backup roll is shown. This will be described with reference to FIG.
(1) When the inter-roll chock holding device 5 is not used (usually during non-rolling), the screw shaft 15 of the screw actuator constituting the actuator 10 is retracted to the minimum stroke position as shown in FIG. Keep it. For this reason, a gap exists between the wedge laminated block 9 and the roll chock 41.
(2) Since the interval between the roll chock 41 and the roll chock 42 also changes depending on the roll diameters of the intermediate roll 21 and the backup roll 22, the height (height dimension) of the wedge laminated block 9 is changed according to the roll exchange performed regularly. ) Zero adjustment is required. For this reason, when the roll replacement is completed and rolling is not performed, the apparatus height (height dimension) is increased until the gap between the roll chocks 41 and 42 and the wedge laminated block 9 disappears, and the roll is attached to the actuator. It is memorized as 0 position by an encoder or the like. Thereafter, the height (height dimension) of the wedge laminated block 9 is lowered so that the gap between the roll chocks 41 and 42 and the wedge laminated block 9 becomes a predetermined interval (for example, 3 mm), and this position is set as the standby position. To do.
(3) A driving speed in the height (height dimension) direction between the roll chocks 41 and 42 and the wedge laminated block 9 so that the state shown in FIG. Until the motor torque corresponding to the rattling force of about 10 ton is generated between the wedge laminated block 9 and the roll chock 41 and between the wedge laminated block 9 and the roll chock 42 from the timing before the time divided by The screw shaft 15 of the screw type actuator 10 is driven to generate a tension force. At this time, the gap between the roll chocks 41 and 42 that was 3 mm at the standby position and the wedge laminated block 9 becomes 0 mm.
(4) After that, even if the drive (motor) is stopped, the screw shaft 15 can be held at the stroke position by the self-lock function by friction between the screw shaft 15 and the wedge bodies 11x and 11y. Thereby, the wedge laminated block 9 can be held at a predetermined height, and the meandering suppression effect at the tail end of the material to be rolled can be exhibited.

  In the system using the screw type actuator as the actuator 10 as described above, it is not possible to wait in a state where a rattling load is applied as in the system using the hydraulic cylinder, but the screw shaft 15 has a self-locking function. Therefore, there is an advantage that the lock operation itself does not require time.

As described above, the timing for forming the tension means by the wedge laminated block 9 between the roll chocks 41 and 42 and between the roll chocks 3 and 41 may include the following, for example.
(1) When a meandering of the steel strip is detected (2) When the steel strip is caught in the rolling mill and the rolling position of the rolling mill starts to be controlled (3) From the rolling mill in front of the rolling mill, the tail of the steel strip When the end is pulled out (4) Other timing The meandering of the steel strip in (1) above (1) to (3) can be detected based on, for example, detection of the edge position by a width meter or detection of the differential load The above (3) can be detected, for example, by detecting the load-off of the preceding rolling mill, and the actuator 10 is operated based on these detection signals, and between the roll chocks 3 and 41 and the roll chocks. A tension means by the wedge laminated block 9 is formed between 41 and 42.

  As described above, the present invention using the inter-roll chock holding device 5 is provided between the work roll 1 of the hot rolling mill and the 21 roll chock of the intermediate roll (that is, between the roll chock 3 and the roll chock 41) and / or the intermediate roll. 21 and the roll chock of the backup roll 22 (that is, between the roll chock 41 and the roll chock 42), a rigid body (wedge laminated block 9) serving as a stretching means can be interposed, and the parallel rigidity of the rolling mill is improved, Without performing special control, it is possible to suppress the horizontal roll flatness due to the meandering amount yc of the hot-rolled steel strip, and to suppress the meandering of the steel strip 17.

  In addition, the present invention can be applied to a rolling mill that has a slow response such as an electric screw of a reduction device and is not suitable for conventional parallel rigidity control.

  The problem of the meandering of the metal material has become a big problem particularly in hot finish rolling for producing a hot-rolled steel strip. Therefore, the present invention provides a hot finish rolling mill for producing a hot-rolled steel strip. And when it is applied to hot finish rolling, it is particularly effective. However, it is not limited to this, for example, a cold rolling mill and a cold rolling for producing a cold rolled steel sheet, a thick plate rolling machine and a thick plate rolling for obtaining a thick steel sheet, and other than the steel sheet The present invention can be applied to various metal rolling mills and rolling, such as a metal rolling mill and rolling.

  Further, when the present invention is applied to a hot finish rolling process for producing a hot-rolled steel strip, it is the rolling mill at the latter stage of the rolling mill group that is particularly likely to meander in the finishing mill group. The present invention is applied to a rolling mill in the latter stage of the number of rolling mill groups of at least the total number of rolling mills / 2 (for example, No. 4 to 7 stands when the number of rolling stands is 7 stands) and its rolling process. Is preferred. Of course, you may apply this invention to all the rolling mills.

In 6Hi of the hot rolling line finish rolling mill final stand having the layout as shown in FIG.
[Invention Example 1] The roll chock holding device 5 is installed between the right and left roll chock of the work roll and the intermediate roll (that is, between the roll chock 3 and 41), and the meandering suppression effect is exhibited.
[Invention Example 2] Roll chock between the left and right roll chock of the work roll and the intermediate roll and between the right and left roll chock of the intermediate roll and the backup roll (that is, between the roll chock 3 and 41 and between the roll chock 41 and 42). A device that has a space holding device 5 and exhibits a meandering suppression effect,
[Comparative example] No wedge laminated block is used.
Rolling was conducted under the three conditions, and the influence on meandering was investigated.

  In this embodiment, the timing for exhibiting the meandering suppression effect is the timing before the meandering expansion becomes significant, so from the end of rolling the stand before the last stand where the device is installed to the end of rolling of the previous stand. Between. The meandering amount is detected by detecting the plate end of the material to be rolled by an x-ray thickness gauge provided on the final stand entry side, and the meandering amount from the meandering amount yc1 immediately before the end of the previous stand rolling to the meandering amount yc2 immediately before the end of the final stand rolling. The enlargement amount Δyc (= yc2−yc1) was set as the evaluation target.

  The object of investigation is a rolling cycle of thin materials that are likely to cause meandering (total number of rolls: 105, final stand rolling mill inlet side thickness h1 = 1.5 to 3.0 mm, outlet side thickness h = 1.2 to 2.0 mm The plate end of the material to be rolled was detected by an x-ray plate thickness meter provided on the final stand entry side, and the tail end meandering amount yc was measured.

In the present invention example 1 and the present invention example 2, as a holding apparatus between roll chocks, a wedge laminated block (size is 200 mm × 300 mm × height is at least 100 mm), an actuator (screw type actuator) and the like shown in FIG. The thing which consists of a holding | maintenance frame for doing was used. The apparatus rigidity obtained from the compressive load-deformation characteristic after the action of the rattling killing load of 5 tons is about 600 tons / mm. This inter-roll chock holding device was installed by fixing the holding frame to the roll chock of the intermediate roll, and then incorporated into the rolling mill together with the intermediate roll when the intermediate roll was periodically replaced. In Invention Example 1 and Invention Example 2, rolling was performed by operating the roll chock holding device as follows.
(1) Since this apparatus is not used until a rolling cycle of a thin material (generally, a product plate thickness of 2.0 mm or less) is started, the height of the wedge laminated block 9 is increased as shown in FIG. The height (height dimension) is set to the minimum position, and it is retracted so that the tension force does not act. The gap between the wedge laminated block and the roll chock of the work roll and / or the gap between the wedge laminated block and the roll chock of the backup roll, which are necessary for evacuation, was about 10 mm in this example.
(2) The gap between the wedge laminated block and the work roll roll chock and / or the wedge laminated block and the backup at the time when rolling is not performed after the work roll 1 for the thin material to be investigated is incorporated. The height (height dimension) of the wedge laminated block was increased until there was no gap between the roll chock of the rolls, and each was stored as zero position by an encoder or the like attached to the actuator (zero adjustment). Thereafter, the height (height dimension) of the wedge laminated block is lowered until the gap between the wedge laminated block and the roll chock of the work roll and / or the gap between the wedge laminated block and the roll chock of the backup roll are each 3 mm. This position was set as a standby position.
(3) Divide the gap between the roll chock of the work roll and the wedge laminated block and / or the gap between the roll chock of the backup roll and the wedge laminated block at a driving speed of 10 mm / s in the height (height dimension) direction. Drive the screw shaft of the screw actuator until the motor torque equivalent to about 10 tons of rattle killing force is generated between the wedge stack block and the roll chock from the timing 0.3 s before the generated time, generating a tensile force I let you. At this time, the gap between the roll chock of the work roll and the wedge laminated block and / or the gap between the roll chock of the backup roll and the wedge laminated block, which were 3 mm each at the standby position, become 0 mm, respectively. It becomes the state of.
(4) Even after the actuator was stopped, the screw shaft was held at its stroke position by the self-lock function by friction between the screw shaft and the wedge body. Thus, the wedge laminated block 9 can be held at a predetermined height, and the meandering suppressing effect at the tail end of the material to be rolled can be exhibited. After the rolling in the final stand is finished, the gap between the roll chock of the work roll and the wedge laminated block and / or the gap between the roll chock of the backup roll and the wedge laminated block is returned to the standby position of 3 mm, respectively. The same operation is repeated at the time of rolling.
(5) Further, for each rolled material, an operation of repeatedly using and not using the roll chock holding device was performed.

  FIG. 15 shows the meandering expansion amount Δyc in the thin object cycle. According to FIG. 15, in the case of the comparative example, the meandering enlargement amount becomes larger as the final stand exit side plate thickness becomes thinner and varies in a range of about ± 25 mm, whereas in the case of the present invention example 1, The meandering expansion amount Δyc could be suppressed to within about ± 15 mm, and in the case of Example 2 of the present invention, the variation was within about ± 5 mm. From this result, it was clarified that the meandering suppressing effect was exhibited by the inter-roll chock holding device, and that the effect was higher when provided between all the roll chocks.

Explanatory drawing which shows the rolling mill in one Embodiment of this invention, and the rolling condition by this. Explanatory drawing which shows the holding apparatus between roll chock in the embodiment of FIG. 1, and its use condition. Explanatory drawing which shows the holding | maintenance apparatus between roll chock in the other embodiment of this invention, and its use condition. Explanatory drawing which shows the holding | maintenance apparatus between roll chock in the other embodiment of this invention, and its use condition. Explanatory drawing which shows the holding | maintenance apparatus between roll chocks and the use condition in other embodiment of this invention. Explanatory drawing which shows the holding | maintenance apparatus between roll chock in the further another embodiment of this invention, and its use condition. Explanatory drawing which shows the holding | maintenance apparatus between roll chock in the further another embodiment of this invention, and its use condition. Explanatory drawing which shows the holding apparatus between roll chock in other embodiment of this invention. Schematic of the general rolling mill for demonstrating the rigid component of a rolling mill. Explanatory drawing which shows the physical interpretation of a meander phenomenon. Explanatory drawing for demonstrating the view of the conventional parallel rigidity control with respect to meandering. Explanatory drawing which shows the fluctuation | variation of the roll chock clearance gap by vendor force provision. Explanatory drawing which shows the layout of a general hot rolling line. Explanatory drawing for demonstrating the optimal apparatus arrangement | positioning which considered the intermediate | middle roll shift in embodiment at the time of applying this invention to HC-Mill. The graph which showed the meandering reduction effect in embodiment of the hot rolling finishing rolling mill by this invention with the comparative example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1, 1a, 1b Work roll 21, 21a, 21b Intermediate roll 22, 22a, 22b Backup roll 3, 3a, 3b, 41a, 41b, 42a, 42b Roll chock 5 Inter-roll chock holding device 6 Roll support part 7 Support means 8 Reduction means 9 wedge laminated block 10 actuator _{11,11x, 11y, 11z 1, 11z} 2, 11w wedge 12 cylinder body 13 actuating rod 14 apparatus main body 15 screw shaft 16 holding frame 160 holding the frame of the inner bottom surface (or top inner surface)
161 Outer bottom surface (or outer top surface) of holding frame
162, 163 Holding frame stopper 17 Steel strip 110 Projection 111 Concave groove 112 Guide projection 113 Guide groove

Claims (4)

Have a roll chock between the holding device having an actuator wedge laminated block and the following (b) below (a),
The actuator and the wedge laminated block are installed on the holding frame,
The actuator is fixed to the holding frame;
At least one wedge body of the wedge laminated block is actuated by the actuator.
The eta is installed so as to be slidable horizontally with respect to the surface of the holding frame to which the eta is fixed,
A metal material rolling machine , wherein the holding frame is fixed to a roll chock of an intermediate roll .
(A) It is arranged between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll, so that it functions as a tensioning means between the roll chocks and the wedge tip side is reversed. Wedge stacking block comprising a plurality of wedge bodies that are slidably stacked so that their inclined surfaces are slidable in the gradient direction of the inclined surface, and at least one wedge body slidingly moves relative to the other wedge bodies .
(B) An actuator for slidably moving at least one wedge body constituting the wedge laminated block with respect to another wedge body and holding it at an arbitrary slide position. Have a roll chock between the holding device having an actuator wedge laminated block and the following (b) below (a),
A wedge laminated block comprising the actuator and two wedge bodies is installed on a holding frame,
The actuator is fixed to the holding frame;
One wedge body of the wedge laminated block is slidably installed on the surface of the holding frame to which the actuator is fixed by the actuator,
A metal material rolling machine , wherein the holding frame is fixed to a roll chock of an intermediate roll .
(A) It is arranged between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll, so that it functions as a tensioning means between the roll chocks and the wedge tip side is reversed. Wedge stacking block comprising a plurality of wedge bodies that are slidably stacked so that their inclined surfaces are slidable in the gradient direction of the inclined surface, and at least one wedge body slidingly moves relative to the other wedge bodies .
(B) An actuator for slidably moving at least one wedge body constituting the wedge laminated block with respect to another wedge body and holding it at an arbitrary slide position. 3. The metal material rolling mill according to claim 1, wherein the rolling mill is used for manufacturing a hot-rolled steel strip. A method of rolling a metal material using the rolling mill according to any one of claims 1 to 3 ,
The wedge laminated block between the roll chock of the work roll and the intermediate roll and / or between the roll chock of the intermediate roll and the backup roll is held at a predetermined height, and the wedge laminated block increases the parallel rigidity of the rolling mill during rolling. A method for rolling a metal material, characterized by forming a stretching means.

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