JPH0270307A - Roll stand for three way rolling - Google Patents

Abstract

PURPOSE:To bring roll draft adjusting amounts to be large by supporting a supporting intermediate shaft of an intermediate gear by a 1st arm freely rockable around to center the rotation shaft of a rolling roll and a 2nd arm freely rockable around to center the rotation shaft of a driving side gear. CONSTITUTION:When a rotation shaft is shifted in a radial direction for position adjustment of a rolling roll 2 in a radial direction, a follwer side gear 14 is shifted in a radial direction and a distance between the rotation centers of the gear 14 and a driving side gear 16 is changed. An intermediate gear 15 is shifted in a radial direction by change of the above center-to-center distance. That is, meshing condition of the gear 15 with the gears 14 and 16 is kept to properly transmit a rotating power in a constant condition even if the rotation shaft is shifted in a radial direction.

Description

Detailed Description of the Invention (Field of Industrial Application) The present invention relates to a roll stand used for rolling wire rods and steel bars, which comprises three rolling rolls arranged at three positions on the outer periphery of a rolling material pass line. related to things.

(Prior art) In a three-way rolling roll stand, each rolling roll is driven to rotate and needs to be moved in the radial direction for adjusting the rolling reduction, so the rotating shaft of the rolling roll is interlocked and connected to a drive source. , it is necessary to be able to move and position freely in the radial direction. This kind of three-way rolling roll stand was developed in 1976-346.
It is disclosed in Publication No. 9.

In this case, there is no problem if the three roll rotation shafts are respectively linked to separate drive sources, but a problem occurs when the three rolls are rotated by a single drive source.

That is, in the one disclosed in the above publication, as shown in FIG. 4, a bevel gear 30° is provided and meshed with the rotating shaft 3′ of each rolling roll 2′, and one rotating shaft 3′ is directly connected to the drive source M. ing. Further, the rotating shaft 3' is supported via an eccentric bearing (not shown) whose rotation can be freely adjusted, so that it can be moved and positioned in the radial direction. In this way, when the rotating shafts are interlocked and connected via the bevel gear 30'', if the bevel gear 30'' is fixed to the rotating shaft 3'', when the radial position of the rotating shaft 3'' changes, the bevel gear 30'' The meshing condition of the gears becomes inappropriate. Therefore, each bevel gear 30'' is moved in the axial direction via a screw mechanism (not shown) as the rotating shaft 3'' moves in the radial direction, and a proper meshing state of the bevel gear 30'' can be maintained. It is said that

The above-mentioned publication also discloses a structure shown in FIG. 5. That is, a bevel gear 30'' is provided and meshed with the rotation shaft 3'' of each rolling roll 2'', and one rotation shaft 3'' is connected to a drive source M7.The rotation of the rotation shaft 3'' is freely adjustable. By being supported via an eccentric bearing (not shown), it is possible to move and position the gear in the radial direction.A sun internal gear 31'' is formed on the inner periphery of each bevel gear 30', and a sun internal gear 31'' is formed on the inner periphery of each bevel gear 30'. It meshes with the planetary gear 32'' on the outer periphery, so that even if the rotating shaft moves 3 degrees in the radial direction, the planetary gear 32'' revolves around the sun internal gear 31'',
It is assumed that each bevel gear 30° does not need to move in the radial direction, and a proper meshing state of the bevel gears 30° can be maintained.

(Problem to be Solved by the Invention) As in the past, when the bevel gear 30' is moved in the axial direction as the rotating shaft 3' is moved in the radial direction, it is difficult to arrange the three rolling rolls at equal intervals in the circumferential direction. Since the tip cone angle of the bevel gear 30 is 60 degrees, the amount of radial movement of the rotating shaft 3' is equal to l/f3 of the amount of axial movement of the bevel gear 30'. Furthermore, the amount of axial movement of the bevel gear 30'' is limited by an eccentric bearing, etc. between the roll 2'' and the bevel gear 30''. Therefore, there is a problem that the adjustment amount of the rolling reduction of the roll 2' becomes small.

Furthermore, in the case of a conventional structure in which a sun internal gear 31' is formed on the inner periphery of the bevel gear 30'' and a planetary gear 32' is formed on the rotating shaft, the amount of radial movement of the rotating shaft 3' is
It is determined by the difference in pitch diameter between the sun internal gear 31'' and the planetary gear 32''.However, since the sun internal gear 31'' is located on the circumference of the bevel gear 30'', its diameter is restricted, and the planetary gear 32'' is
2" also needs to be at least approximately the same diameter as the rotating shaft 3" from the viewpoint of strength, etc., and the difference in pinch circle diameter is too large (it cannot be done. Therefore, the amount of rolling adjustment of roll 2" will be small. There is a problem.

SUMMARY OF THE INVENTION An object of the present invention is to provide a three-way rolling stand that can drive three rolling rolls that can be moved and positioned in the radial direction by a single drive source without causing the problems of the prior art described above. .

(Means for Solving the Problems) The present invention is characterized by a three-way rolling roll stand equipped with three rolling rolls 2 arranged at three positions on the outer periphery of a rolling material pass line, each rolling roll 2 is provided with a rotating shaft 3 that is orthogonal to the pass line direction and is movable and positionable in the radial direction, and a driven gear 14 that is interlocked and connected to a single drive source is provided on the rotating shaft 3. An intermediate gear 15 is meshed with the side gear 14 , a drive side gear 16 is meshed with the intermediate gear 15 , and an intermediate shaft 19 for supporting the intermediate gear 15 is a first arm that is swingable around the rotation axis of the rolling roll 2 . 21 and a second arm 22 that is swingable about the rotation axis of the drive side gear 16.

(Function) When the rotating shaft 3 is moved in the radial direction to adjust the radial position of the rolling roll 2, the driven gear 14 is also moved in the radial direction.
The distance between the rotation centers of the driven gear 14 and the driving gear 16 also changes. As the center-to-center distance changes, the first arm 21 and the second arm 22 swing, and the intermediate gear 15 moves in the radial direction. That is, the meshing state of the intermediate gear 15 with the driven gear 14 and the driving gear 16 is always maintained in a constant state even when the rotating shaft 3 moves in the radial direction, and rotational power is properly transmitted.

(Example) Embodiments of the present invention will be described below based on the drawings.

1 to 3 relate to a three-way rolling roll stand, which is equipped with three rolling rolls 2 arranged in a casing 1 at three positions on the outer periphery of a rolling material pass line.

A rotating shaft 3 that is perpendicular to the pass line direction is fitted and fixed to each rolling roll 2 . In this embodiment, the rotary shaft 3 is hollow, and a support shaft 4 is fitted to the inner periphery of the rotary shaft 3 via a bearing 5 so as to be relatively rotatable.

The support shaft 4 is rotatably supported by the casing 1 via a bearing 6. The support shaft 4 has an intermediate portion 4a offset from both end portions 4b, 4b by an amount e, and the intermediate portion 4a is fitted concentrically to the rotating shaft 3 via the bearing 5. Here, the support shaft 4 relative to the casing 1
The center of rotation of is coincident with the axis of both end portions 4b.

A spur gear 7 is provided at one end of one of the upper support shafts 4 in FIG. The center of rotation of this spur gear 7 is aligned with the center of both end portions 4b of the support shaft. Further, a spur gear 8 meshing with the spur gear 7 is provided at one end of a reduction transmission shaft 9 rotatably supported by the casing 1. As shown in FIG. 3, a worm wheel 10 is provided at the other end of the reduction transmission shaft 9, and a worm 11 that meshes with the worm wheel 10 is provided on the reduction adjustment shaft 12. This reduction adjusting shaft 12 is rotatably supported by the casing 1 via a bearing 29.

Further, bevel gears 13 are provided at the other end of the upper support shaft 4 in FIG. 1, at both ends of the left support shaft 4, and at the lower end of the right support shaft 4, respectively, and mesh with the adjacent gears.

The center of rotation of each bevel gear 13 is aligned with the axis of both ends 4b of the support shaft. Thereby, when the reduction adjustment shaft 12 is rotated, the rotation is transmitted to each support shaft 4 via the reduction transmission shaft 9, and each support shaft 4 rotates about the axis of its both ends 4b. Then, since the intermediate portion 4a of each support shaft 4 is eccentric with respect to both end portions 4b, each rotating shaft 3 that is fitted concentrically to the intermediate portion 4a moves in the radial direction, and the radial position of each rolling roll 2 changes. Adjustments are made.

Power is transmitted from a drive source (not shown) to each rolling roll 2 through a driven gear 14 provided on the outer periphery of each rotating shaft 3,
This is accomplished through an intermediate gear 15 that meshes with the driven gear 14, a drive gear 16 that meshes with the intermediate gear 15, and an interlocking connection mechanism of each of the drive gears 16.

Each driving gear 16 is rotatably supported by the casing l via a transmission shaft 17 and a bearing 18.

Each intermediate gear 15 is supported by an intermediate shaft 19 via a bearing 20 so as to be relatively rotatable. This intermediate shaft 19 is
It is supported by a first arm 21 and a second arm 22.

A pair of first arms 21 are provided for each intermediate shaft 19,
One end thereof is fitted to the support shaft 4 so as to be swingable. Here, the center of swing at one end of the first arm 21 coincides with the center of the rotation axis of the rolling roll 2, that is, the axis of the rotation shaft 3. Further, the other end of the first arm 21 is fitted to the intermediate shaft 19 concentrically and relatively rotatably.

A pair of second arms 22 are provided for each intermediate shaft 19,
One end thereof is fitted to the transmission shaft 17 via a bearing 23, so that it can swing freely around the rotation axis of the drive side gear 16. The other end of the second arm 22 is fitted to the intermediate shaft 19 concentrically and relatively rotatably.

Spur gears 24 are provided at one end of each of the upper and right transmission shafts 17 in FIG. 1, and at both ends of the left transmission shaft 17.
An interlocking shaft 26 is rotatably attached to the casing 1 via a bearing 27, and has a spur gear 25 at one end that meshes with each of the four gears. A bevel gear 28 is provided at the other end of each interlocking shaft 26, and adjacent gears are meshed with each other. The extension portion 26 of the interlocking shaft 26 at the top in FIG.
Rotational power is input to a from a drive source.

According to the above configuration, rotational power from a single drive source is transmitted to each rolling roll 2 via the driving gear 16, the intermediate gear 15, and the driven gear 14.

Then, when the radial position of each rolling roll 2 is adjusted,
As the rotating shaft 3 moves in the radial direction, the driven gear 14 also moves in the radial direction, and the distance between the rotation centers of the driven gear 14 and the driving gear 16 changes. As this center-to-center distance changes,
The first arm 21 and the second arm 22 swing, and the intermediate gear 15 moves in the radial direction.

As a result, the meshing state of the intermediate gear 15 with the driven gear 14 and the driving gear 16 can simply be maintained in a constant state even if the radial position of the rolling roll 2 is adjusted, which may impede the transmission of rotational power. Never.

(Effects of the Invention) According to the present invention, the radial movement of the roll rotation axis does not require consideration of the meshing state of the bevel gear mechanism or planetary gear mechanism as in the past, and it is possible to increase the roll reduction adjustment amount of the roll. can.

[Brief explanation of the drawing]

1 to 3 relate to embodiments of the present invention, FIG. 1 is a front cross-sectional view of a three-way rolling stand, and FIG. 2 is an A of FIG. 1.
-A sectional view, FIG. 3 is a view taken along arrow B in FIG. 1, and FIGS. 4 and 5 are schematic configuration diagrams of three-way rolling roll stands according to different conventional examples. 2... Rolling roll, 3... Rotating shaft, 14... Driven side gear, 15... Intermediate gear, 16... Drive side gear,
19... Intermediate shaft, 21... First arm, 22...
Second arm. Patent applicant: Kobe Steel, Ltd. No. 23

Claims (1)

[Claims] (1) A three-way rolling roll stand equipped with three rolling rolls (2) arranged at three positions on the outer periphery of the rolling material pass line, each rolling roll (2) being orthogonal to the pass line direction and radially A rotary shaft (3) that can be freely moved and positioned, and a driven gear (14) that is interlocked and connected to a single drive source is provided on the rotary shaft (3),
An intermediate gear (15) is meshed with the driven gear (14), a driving gear (16) is meshed with the intermediate gear (15),
The supporting intermediate shaft (19) of the intermediate gear (15) is a first arm (21) that is swingable around the rotation axis of the rolling roll (2).
and a second arm (22) that is swingable around the rotation axis of the drive side gear (16).