RU1776211C - Pinion stand of rolling mill main drive - Google Patents

Abstract

Usage: construction of gear stands of the main drive of a rolling mill for the production of batch rolling. SUMMARY OF THE INVENTION: Two parallel output shafts 1.2 are provided with helical rims 3, 4 and rotate in opposite directions. One input shaft 5, equipped with a helical rim 6, is engaged with the helical rim 3 of the first of the output shafts 1. The cage is equipped with an intermediate shaft 7 and a movable block 9 mounted on it, consisting of two helically connected helical rims 10, 11 with different directions of the tooth line, one of which is engaged with the crown 6 of the input 5, and the second with the crown 14 of the second output shaft 2. The width B of the crowns 6, 4 of the input 5 and the second output shaft 2 is made of a larger width Be of each of the crowns 10, 11 of the intermediate shaft 7 on the value of the axial stroke of block 9, which is regulated by a mathematical expression. Also, the number of teeth and rim modules are interconnected by certain relationships. The movable unit is provided with an axial displacement device together with the countershaft. The invention improves the accuracy of rolled products by allowing one of the output shafts to rotate relative to the second. 2 s.p. f-ly, 3 ill. V4 XJ OK O. 0 S fug. g

Description

The invention relates to mechanical engineering and relates to gear manufacturing, and more particularly relates to gear stands of a main drive of rolling mills for producing rolled products with a section periodically varying in length.

During the rolling process, the rotation of the rolls of the working stand of such a mill should be strictly synchronized, which is ensured by the engagement of the gear rims mounted on the output shafts of the gear stand of the main drive. On the other hand, in the process of setting up the working stand, the rolls should rotate smoothly relative to each other, ensuring that the calibres applied to them coincide. The elimination of the contradiction between these requirements constitutes the main task to which the alleged invention is directed.

The solution should ensure the accuracy of the roll settings and thereby the accuracy of the rolled products, as well as reducing labor costs during the setup process and simplifying the design of the drive of the rolling mill.

A known gear stand of the main drive of a rolling mill, mainly of periodic rolling, comprising two parallel output shafts provided with helical or chevron ring gears and rotating in opposite directions with equal rotational speeds.

In the known construction, the gear rims of the output shafts are engaged directly with each other, which ensures strict synchronization of the rotation of the gear rolls during the rolling process and, at the same time, excludes the possibility of their relative rotation during adjustment.

When using such a stand in mills intended for the production of rolled products with a section periodically varying in length, between the working and gear rolls it is necessary to install some kind of connecting device that allows the work roll to rotate relative to the gear.

Such a device can be made, for example, in the form of an adjusting clutch, mainly, the main line of the rolling mill. The device comprises gear wheels mounted on the connected pallets, a composite gear ring coaxial with them, half hollows of which are kinematically connected to the gears by means of two groups of spurious gears with carrier rings, as well as a self-braking drive for mutual angular adjustment of the shafts and an intermediate self-aligning link, a self-braking drive toothed

semi-holders, and a self-aligning link - drove.

The disadvantage of the known stand design is primarily the complexity of the connecting device containing

a large number of spurious elements, which leads to insufficient reliability and rigidity of the drive as a whole, the great complexity of its manufacture, the complexity of the settings and ultimately

insufficient accuracy of rolled products.

. Of the known gear stands of the main drive of the rolling mill, mainly periodic rolling, the most

similar in technical essence is a stand containing two parallel output shafts provided with helical crowns and rotating in opposite directions with equal rotational speeds, and

one input shaft provided with a helical rim engaged with a helical rim of the first of the output shafts.

Worm wheels are installed in the cage body with the possibility of movement in the direction of the axis of the worm, and the movement mechanism, made in the form of a frame, interacts with the cylindrical surfaces of the cushions of the worm wheels by means of U-shaped bores and is mounted with

the ability to rotate on the axle x placed on the housing of the gear stand.

The axes of rotation of the frames are placed in the plane of the axles of the worm wheels and between the latter at equal distances x from them, and one

of the cushions of the worm wheels is equipped with a device for its fixation relative to the housing of the gear stand. Adjustable braking devices mounted on roll pads.

A disadvantage of the known design of the gear stand is the complexity of the design, combining a large number of initial links, which greatly complicates the manufacture and assembly, reduces the productivity of the mill due to the longer setup time. In addition, there is a limited transmission torque due to the low bearing capacity compared to gears

worm gears.

The aim of the invention is to increase the accuracy of rolled products by allowing rotation of one of the output shafts relative to the second.

This goal is achieved by the fact that the gear unit of the main drive of the rolling mill is predominantly periodic rolling, containing two parallel output shafts equipped with helical gears and rotating in opposite directions with equal rotational speeds, and one input shaft equipped with a helical gear engaged with according to the invention, the helical rim of the first of the output shafts is provided with an intermediate shaft and a movable unit mounted thereon, consisting of two obliquely rigidly interconnected tooth crowns with different directions of the tooth line, one of which is meshed with the crown of the input shaft and the second with the crown of the second output shaft, the width B of the crowns of the input and second output shaft having a larger width B0 of each of the crowns of the intermediate shaft by the amount of axial displacement block sin / 3-i, sin

S 0.5 D (Y GP1 Z21 GP2 Z22

where is the required angle of relative rotation of the output shafts;

Z21, Z22, GL1, GP2,, fo. NUMBER of Zubiev,

normal modules, and the angle of inclination of the teeth of the helical gears of the first and second output shafts, respectively, and the number of teeth zoi, Z02, respectively, of the first and second crowns of the intermediate shaft are determined

FROM CONDITIONS ZQ1 Z22 Z02 Z21.

Moreover, the number of teeth and rim modules are interconnected by the dependences Z21 ZQ1

Z1 + Z21 / mi / COS (ZQ2 + Z22) rfi2 / COS /%,

where zi is the number of teeth of the input shaft crown.

In addition, the movable block is equipped with an axial displacement device made in the form of a screw rigidly fixed to the end of the intermediate shaft, a nut rigidly mounted on the stand body, and a lock nut, and the gear ring set is mounted on rolling bearings and is fixed from axial displacement relative to the intermediate shaft.

Such a structural embodiment of the gear stand of the main drive of the rolling mill, mainly periodic rolling, improves the accuracy of the rolled products by allowing angular adjustment of the rolls of the working stand when one of the output shafts is rotated relative to the second.

In addition, simplification of the mill drive design is achieved by eliminating a number of kinematic links in the drive circuit,

Such structural design of the stand also allows to increase the productivity of the mill by reducing labor costs when setting it to a predetermined size.

In FIG. 1 shows the gear stand of the main drive of the rolling mill

periodic rolling; in FIG. 2 is a section AA of FIG. 1; in FIG. 3 is a section BB of FIG. 1.

The gear stand of the main drive of the rolling mill of the periodic rolling mill contains two parallel output shafts

1,2, equipped with helical rims 3, 4 and rotating in opposite directions with equal speeds, and one input shaft 5, equipped with a helical rim 6, engaged helical

crown 3 of the first of the output shafts 1. An intermediate shaft 7 is installed in the cage, equipped with a movable block 9 located on the rolling bearings 8 of two helically rigidly connected to each other

crowns 10, 11, one of which is engaged with crown 5 of input 5, and the second with crown 4 of second output shaft 2. The cage also contains axial displacement devices of block 9, including a screw

12, rigidly fixed to the end of the intermediate shaft 7, a nut 13, rigidly mounted on the casing 14 and the lock nut 15. The movable unit 9 is fixed from axial movement relative to the intermediate shaft by means of a nut 16.

The width B of the crowns 6, 4 of the input 5 and the second output shaft 2 is made larger than the width W of each of the crowns 10, 11, the intermediate shaft 7 by the value of the axial displacement of the block 9, determined from the ratio

S 0.5 (

sin ffisin / fo

+

)

GL1 Z21GP2 Z22

where the required angle of relative 5 rotation of the output shafts;

Z21, 222. PL1, GP2,, 2 NUMBER ZuOvp,

normal modules and the angle of inclination of the teeth of the helical gears of the first and second output shafts, respectively, and the number of teeth zoi, 0 202, respectively, of the first 10 and second 11 crowns of the intermediate shaft 7 are defined

FROM CONDITIONS ZQ1 Z22 ZQ2 Z21, Where 201, ZQ2

the number of teeth. of the helical rims of the gear unit of the intermediate shaft. 5 For structural reasons, the axes of all four shafts should be located at the vertices of the rectangle.

In this case, the distance between the axes of the intermediate 7 and second output shafts 2 should be equal to the interaxial distance aw of the input and first output shafts

aw (21 + Z2i) m i / 2cos (zo2 +

+ Z22) / 1TI2 / 2COS jh.

In addition, in order to increase the load capacity of the stand, this distance must be made large by the design of the distance mill between the axes of the output shafts and equal to the distance between the axes of the distance between the axes of the input and intermediate shafts:

a (21 + zoi) mi / 2cos / i Comparing this expression with the expression

FOR 3W, COME TO THE CONDITION Z21 Z01

(zi + Z2l} mi / COS Pi (Z02H Z22) / m2 / COS / 2,

where 21 is the number of teeth of the crown of the input shaft.

The device operates as follows.

When adjusting the working stand to the specified parameters in the gear stand, the lock nut 15 on the screw 12, rigidly connected to the intermediate shaft 7, loosens. Rotating the screw 12, we move the shaft 7 about the axial direction by a certain stroke S. At the same time, gear block 9 moves along with breaking 7. with helical gears 10, 11, turning in their movement through the helical gears 3, 4 both output shafts 1, 2. Correspondingly, the work rolls of the stand are kinematically connected to the output shafts.

When the axial movement of the block by the value of S, the second output shaft 2 rotates relative to the intermediate shaft 7 at an angle

S tg /% 2 S sin /%

G22GP2 Z22

P 22

where Г22 0.5 rri2Z22 / cos (h is the dividing radius of the crown 4.

At the same time, the input shaft 5 rotates in relation to the shaft 7

2Ssin / 3i side by angle p

While the first output shaft 1 is rotated by an angle

g 2 S

221 mi 221

# 21 P

Thus, the output shafts 1 and 2 are rotated relative to each other at an angle

 P p21 X

x (+ sln #

 GP1 Z21GL2 Z22

From here, at a given value (p, we find the required movement of the intermediate shaft

 sinffi

fifty,(

mi 221

+

GL2 Z22

)

0

5

0

Upon completion of adjustment, the lock nut 15 locks the shaft 7 against axial movement.

During the rolling process, the input shaft 5 rotates with an angular speed w and drives the output shaft 1 with an angular speed UJ21 O) 1

At the same time, the intermediate shaft 7 is driven into rotation with an angular velocity (oh, / gm1, and the output shaft is 2nd angular speed

202 ,, Z1 Z02

5

0

5

0

5

0

5

0) 22 0) about

and)

Z 22Z 01 Z 22

The angular velocity of the output shafts should be equal in absolute value. This implies the relationship between the number of teeth of the crowns of the intermediate and output shafts

201 Z22 221 Z02

The proposed gear stand compared to the known ones allows to simplify the design of the drive of the rolling mill by eliminating a number of kinematic links, as well as to increase the productivity of the mill by reducing labor costs when setting it and reducing downtime.

Claims (3)

SUMMARY OF THE INVENTION 1. A gear stand of a main drive of a rolling mill, preferably of periodic rolling, comprising two parallel output shafts provided with helical gears, and one input shaft provided with a helical gear, engaged with the helical gear of the first of the output shafts, characterized in that , in order to improve the accuracy of the rolled products by ensuring the rotation of one of the output shafts relative to the second, the stand is equipped with an intermediate shaft mounted with the possibility of axial movement and and the bearing block, consisting of two hard-wired helical crowns with different directions of the tooth line, one of which is engaged with the input crown, and the second with the second output shaft crown, the width B of the input and second output crowns the bar is made of a larger width In each of the crowns of the intermediate shaft by the value of the axial displacement of the block slnffi, sirij 5Ao5 / (h GP1 Z21 GP2 Z22 where the required angle of relative rotation of the output shafts 221, 222, mi, 012, / 5i, {h, respectively, the number of teeth, normal modules and the angle of inclination of the teeth of the helical gears, respectively, of the first and second output shafts, and the number of teeth zci, 202, respectively, of the first and second crowns of the intermediate shaft are determined from the condition Z01 222 202 Z21 2. A cage according to claim 1, characterized in that the number of teeth and crown modules are interconnected by dependencies Z21 zoi; (Z1 + Z2l) m 1 / COS / 3l () т2 / С08 $ 2, where zi is the number of teeth of the input shaft crown. 3. A crate according to claim 1, characterized in that. that the movable unit is provided with a helical axial displacement device, and the gear set is rotatably mounted and secured against axial displacement relative to the countershaft. & g. / Lg 22.GPg. Fi1 Fig.Z