JPH0534085B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a roll for a rolling mill and a rolling mill.

In a rolling mill, in particular, uniformity in thickness of rolled material is strongly required. However, due to the unique structure of the rolling mill where the bearings at both ends of the rolls receive the rolling load, the axes of the upper and lower rolls are curved into a bulge between the bearings. There is a problem when it gets thicker.

Therefore, in order to compensate for such curvature of the roll axis, a method of providing the roll with a crown has conventionally been adopted. One method is to fit a sleeve 2 around the outer periphery of a roll arbor 1, form a hydraulic chamber R in the center of the roll arbor 1, and apply hydraulic pressure into the hydraulic chamber R, as shown in FIG. A method is known in which the crown of the roll is controlled by forcibly inflating the sleeve 2. However, in the case of such a roll, as shown in FIG. 2, the part of the sleeve 2 in contact with the other roll 3 is locally bent, and high stress is applied to the starting point P of the bending part. , it was not suitable for high-load rolling applications such as hot strip mills and plate mills.

This invention was made in consideration of the above-mentioned circumstances, and is a roll for a rolling mill that has high rigidity and large pressure-receiving capacity, and has excellent crown control ability by controlling the crown through a mechanical configuration. and a rolling mill.

Hereinafter, this invention will be explained based on FIGS. 3 to 13.

3 to 6 illustrate an embodiment of a roll for a rolling mill according to the present invention. In the figure, reference numeral 4 denotes a roll arbor, both ends of which are rotatably held in an axle box 6 by bearings 5. A right sleeve 7, a ring-shaped piston 8, and a ring-shaped cylinder (hydraulic cylinder) 9 are fitted into the right half region of the circumferential surface of the roll arbor 4 in order from the center to the right end of the roll arbor 4. On the other hand, symmetrically to this, a left sleeve 7, a ring-shaped piston 8, and a ring-shaped cylinder (hydraulic cylinder) 9 are fitted into the left half of the roll arbor 4. Therefore, the configuration of the right half of the roll will be described below as a representative example.

The mating surfaces of the roll arbor 4 and the sleeve 7 are tapered surfaces (slanted surfaces) 4a and 7 that correspond to each other.
It is said to be a. Tapered surface 4 on roll arbor 4 side
A is formed so that the diameter of the roll arbor 4 gradually decreases from the center to the ends, and a tapered surface 7a on the sleeve 7 side is formed to correspond to this. Tapered surface 4 of the roll arbor 4
a is set such that the angle of inclination of the roll arbor 4 with respect to the axis is greatest at the center of the roll arbor 4. The sleeve 7 is forcibly movable left and right along the axial direction of the roll arbor 4.

The ring-shaped piston 8 and the ring-shaped cylinder 9 are
It constitutes a hydraulic moving mechanism for moving the sleeve 7. First, the piston 8 has a protrusion 8a on its left outer peripheral surface, and this protrusion 8a is attached to the sleeve 7.
It is connected to the sleeve 7 by fitting into the annular groove 7b on the right inner circumferential surface of the sleeve 7. A plurality of notches 7d are formed in the right side wall 7c forming the groove 7b of the sleeve 7 at predetermined intervals in the circumferential direction of the sleeve 7. Further, a plurality of protrusions 8a of the piston 8 are formed on the same circumference of the piston 8 at predetermined intervals, and a notch 8b is formed between the protrusions 8a. When connecting the sleeve 7 and the piston 8, first, the notch 7d of the former is made to face the protrusion 8a of the latter, and the notch 8b of the latter is made to face the wall 7b of the former. After abutting the two against each other and positioning the protrusion 8a of the latter in the groove 7b of the former, both are rotated by a predetermined angle. As a result, both are first connected in the axial direction of the roll arbor 4. Next, as shown in FIG. 4, for the space where both notches 7d and 8b coincide,
A piece 10 as shown in FIG. 6 is inserted from the right side in the figure. This piece 10 has a curved U-shape, and its notch 10a faces the cylinder 9 side.
Then, it is fixed to the sleeve 7 side by bolts (not shown) passing through holes 10b on both sides thereof. In this way, the sleeve 7 and the piston 8 are integrally connected.

On the other hand, the cylinder 9 has its right side sandwiched between the stepped portion 4b of the roll arbor 4 and the bearing 5,
It is laterally connected to the roll arbor 4 by means of a key 11. The left side portion of the cylinder 9 together with the circumferential surface of the roll arbor 4 constitutes a cylinder chamber. Inside this cylinder chamber, a right side portion of the piston 8 is provided so as to be movable in the left and right direction in a liquid-tight manner, and cylinder chambers R ₁ and R ₂ are formed on the left and right sides thereof. Inside these left and right cylinder chambers R ₁ and R ₂ ,
Hydraulic pressure is introduced from the outside through oil passages L ₁ and L ₂ of the roll arbor 4. cylinder 9
A leftward extending portion 9a is formed in a part of the left side portion of the piece 10, which extends from the notch 1 of the piece 10 described above.
It fits into 0a.

Further, in the tapered surface 4a of the roll arbor 4, a large number of annular grooves 4c (two grooves are omitted in the figure) are formed over the entire area, and hydraulic pressure is applied from the outside through an oil passage _L3 . is being introduced.

In addition, 12 in the figure is a sealing member.

Next, the operation of the roll configured in this way will be explained. Here again, the action on the right half of the roll will be explained as a representative.

The movement mechanism for the sleeve 7 moves the sleeve 7 to the right together with the piston 8, as shown by the upper half of the roll in FIG. ₃ , when hydraulic pressure is introduced into the left cylinder chamber R1. On the other hand, when hydraulic pressure is introduced into the cylinder chamber _R2 on the right side, the sleeve 7 is forcibly moved to the left together with the piston 8, as shown by the lower half of the roll in FIG. When the sleeve 7 is moved from side to side, hydraulic pressure is introduced into the groove 4c of the roll arbor 4 to apply an expanding force to the sleeve 7, thereby reducing its movement resistance.

With this movement of the sleeve 7, the outer diameter of the roll, particularly in its middle portion, changes significantly. That is, when the sleeve 7 moves to the left, the sleeve 7 expands along the tapered surface 4a of the roll arbor 4, and the degree of expansion is such that the angle of inclination of the tapered surface 4a with respect to the axis of the roll arbor 4 is greatest at the center of the roll arbor 4. Therefore, the part corresponding to the center of the roll is larger than the part corresponding to the end of the roll. In this way, the outer diameter of the roll smoothly and reliably expands (bulges) in the axial direction according to the amount of movement of the sleeve 7, and the extent of the bulge is maximum at the center of the roll arbor 4. . Moreover, the rolling force is reliably received by the roll arbor 4 via the sleeve 7.

By the way, the sleeve 7 on the left side of the roll is moved toward and away from each other at the same time as the sleeve 7 on the right side, for example, as shown in FIG. In such a case, left-right symmetry of the roll outer diameter can be obtained. However, if necessary, the left and right sleeves 7 may be moved individually.

Note that the hydraulic pressure introduced into the groove 4c of the roll arbor 4 generates a component force in the sleeve 7 that moves it toward the end of the roll, so this component force is used to return the sleeve 7 toward the end of the roll. In this case, a moving mechanism section for moving the sleeve 7 in the return direction is unnecessary. Further, the number of sleeves 7 may be one or more and may be provided asymmetrically (an example in which one sleeve is provided will be described below as another embodiment).

7 to 9 show other embodiments of the rolling mill roll according to the present invention.

In this embodiment, the left and right sleeves 7 in the above-mentioned embodiment are integrated into one, and the mating surfaces of the integrated sleeve 7 and the roll arbor 4 have the following tapered surfaces 4a and 7a. has been done. That is, as shown in FIG. 8, the twill line of the tapered surface 4a on the side of the roll arbor 4 has an amplitude of the radial difference T between the left end of the roll arbor 4, which has a small diameter, and the right end, which has a large diameter. It is assumed that a sine curve is drawn in the axial direction of
The sine curve has a phase angle θ = 0° at the midpoint P ₀ in the axial direction of the roll arbor 4, a point P ₁ at the right end of the roll arbor 4 at a phase angle θ = +90°, and a point P ₂ at the left end of the roll arbor 4. is the phase angle θ=-90°. Therefore, the tapered surface 4a is formed such that the left side of the roll arbor 4 has a small diameter and the right side has a large diameter, and its inclination changes steplessly. In addition, since the ridge line of the tapered surface 4a forms a sine curve as described above, the inclination angle of the tapered surface 4a, which changes steplessly, is the same as that of the central portion of the roll arbor 4.
Maximum at P ₀ . A tapered surface 7a on the sleeve 7 side is formed to correspond to such a tapered surface 4a.

Thus, the sleeve 7 is slid left and right by left and right ring-shaped pistons 8 similar to those of the embodiment described above. Then, depending on the sliding position, the diameter of the sleeve 7 expands to a large extent at the middle part of the roll, and the diameter of the roll changes symmetrically. Specific examples thereof are shown in FIGS. 9 and 10. FIG. 9 shows the curve of the ridgeline of the tapered surface 4a in the axial direction of the roll, and FIG. 10 shows the amount of expansion of the roll diameter in the axial direction of the roll, which changes depending on the sliding amount of the sleeve 7. Curves A, B, C, D, E, F, G, H in Figure 10
The sliding amount of sleeve 7 is 4mm and 8, respectively.
It shows the change in roll diameter when it is mm, 12mm, 16mm, 20mm, 24mm, 28mm, and 32mm. By the way, the single sleeve 7 can be slid by only one of the moving means provided at either of its left and right ends.

FIG. 11 shows another example of forming the tapered surfaces 4a, 7a of the roll arbor 4 and sleeve 7. The tapered surface 4a in this example is a point a predetermined distance away from the right end point P ₁ of the large diameter of the roll arbor 4 and the left end point P ₂ of the small diameter toward the middle of the roll.
The tapered surface forms a straight ridgeline between P ₃ and P ₄ . The angle of inclination of this tapered surface 4a with respect to the axis of the roll arbor 4 is such that the central part of the roll arbor 4, that is, the part of line segment P ₃ - P ₄ is
It is larger than the P ₁ −P ₃ and P ₄ −P ₂ parts. The tapered surface 7a on the sleeve 7 side is formed to correspond to the tapered surface 4a on the roll arbor 4 side. As in this example, the tapered surfaces 4a, 7
Even in the case where the sleeve 7 is formed, the sleeve 7 expands in diameter so as to bulge largely at the middle portion of the roll depending on the sliding position of the sleeve 7, and the roll diameter changes symmetrically. In this way, the tapered surfaces 4a, 7a
may be tapered to approximate the shape shown in FIG.

Figures 12 and 13 are similar to Figures 7 and 8.
A different example is shown in which the roll shown in the figure is actually installed in a rolling mill. In the case of Fig. 12, the rolls shown in Figs. 7 and 8 are incorporated as the upper and lower backing rolls R ₃ and R ₃ , and in the case of Fig. 13, the upper work roll R ₁ and the backing roll are incorporated. It is incorporated as an intermediate roll between _R3 and _R2 . Alternatively, it may be incorporated as work role _R1 . That is, it can be appropriately incorporated into at least one of the work roll R ₁ , the intermediate roll R ₂ , and the backup roll R ₃ . In the rolling mill constructed in this manner, the rolled material W is adjusted according to the sliding of the sleeve 7.
The plate thickness control can be performed accurately with high rigidity. The same applies when a roll as shown in FIG. 3 is incorporated.

As explained above, according to the present invention, a hydraulic cylinder for moving the sleeve in the axial direction of the roll arbor is provided at the end of the roll arbor, and the outer circumferential surface of the roll arbor into which the sleeve is fitted becomes the insertion side of the sleeve. The outer diameter of the end portion is smaller than the outer diameter of the center portion, and the angle of inclination of this slope with respect to the axis of the roll arbor is the largest at the center of the roll arbor. When the sleeve is moved from the insertion side of the roll arbor toward the center by a hydraulic cylinder, the sleeve moves along the slope of the roll arbor and bulges out to expand its diameter, and the amount of bulge becomes maximum at the center of the roll arbor. In other words, the crown can be controlled by the mechanical configuration (slanted surface formed on the roll arbor).
It has high rigidity, large pressure receiving capacity, and excellent crown control ability.

[Brief explanation of the drawing]

FIG. 1 is a schematic diagram of a conventional roll, FIG. 2 is an explanatory diagram of how the roll is used, FIGS. 3 to 6 show an embodiment of the rolling mill roll of the present invention, and FIG. 4 is an enlarged view of the circular part in Fig. 3, Fig. 5 is an enlarged view of the V-circular part in Fig. 3, Fig. 6 is a perspective view of the piece, and Figs. 7 to 10 are Another embodiment of the roll for a rolling mill according to the invention is shown, FIG. 7 is a longitudinal sectional view, FIG. 8 is an enlarged explanatory view of the main part, and FIGS. 9 and 10 show the setting amount of the arbor outer diameter and the roll expansion. A graph showing a specific example of the amount, FIG. 11 is an enlarged view of the main part showing still another embodiment of the roll for a rolling mill of the present invention, and FIGS. 12 and 13 are respectively different implementations of the rolling mill of the present invention. It is a roll schematic arrangement diagram which shows an example. 4... Roll arbor, 4a... Tapered surface, 7...
...Sleeve, 7a...Tapered surface, 8...Piston, 9...Cylinder, _R1 ...Work roll, _R2 ...
...Intermediate roll, R ₃ ...Waiting roll.

Claims (1)

[Claims] 1. A cylindrical sleeve fitted into a roll arbor, a hydraulic cylinder provided at an end of the roll arbor for moving the sleeve in the axial direction of the roll arbor, and a roll arbor into which the sleeve is fitted. The outer circumferential surface of is an inclined surface such that the outer diameter of the end on which the sleeve is inserted is smaller than the outer diameter of the center, and the angle of inclination of this inclined surface with respect to the axis of the roll arbor is greatest at the center of the roll arbor. A roll for a rolling mill characterized by: 2. The rolling mill roll according to claim 1, wherein a plurality of sleeves are provided.