KR19980070305A - Long Rolling Mill - Google Patents

Abstract

The present invention includes the work of releasing the work roller 8 from the tip of the roll supporting shaft on the pass line P and having a plurality of calibars C ₁ , C ₂ on the outer circumference thereof. To a rolling mill, this operation usually takes a long time and deteriorates the product productivity.

Accordingly, the present invention aims at improving this, in which the axially transportable roller housing 7 is provided separately from the bevel gearbox 6 and the calibar exchange is carried out by transporting the housing 7. In order to absorb more than the axial length of the driving force transmission path by the conveying motion of the housing 7, the passage is provided with an axial protruding / ejecting mechanism such as a spline shaft 25 so that it is not necessary to release the work roller 8 when changing the calibar. The exchange operation is easier and the time required is shortened, thus improving the productivity.

Description

Long Rolling Mill

FIELD OF THE INVENTION The present invention relates to a long product rolling mill of a length in which a working roller is placed in a cantilevered state on the ends of a pair of roll supporting shafts.

As a conventional long mill for a long product, a block mill as shown in FIG. 11 is known, wherein an angle of 45 ° on both sides of the pass line P along the stock to which the wire rod is supplied ( For example, Japanese Patent Laid-Open No. 185101/93) is inclined respectively so that a plurality of roller stands 51, that is, rolling mill stands, are alternately arranged. In each roll stand 51, a pair of working rollers 52, 52 have a caliber of a predetermined type on its outer circumferential surface, and are placed on the pass line P side, and the rotational force from the line shafts 55, 55 Each job is delivered to 52, 52. This line shaft is driven by the drive motor 53 through the rolling mechanism 54.

As in FIG. 12, it demonstrates more concretely. A driving force input member is located on each line shaft 55 at a position located in the associated roller stand 51. Further, within each roll stand 51, a drive bevel gear 56a engaged with the drive bevel gear 55a is arranged to have a drive transmission shaft 56 given at one end side. On the opposite end side of this drive transmission shaft 56, a first spur gear 56b is placed. And the second spur gear 57a is placed on the intermediate transfer shaft 57 shown in FIG. 13 which meshes with the first spur gear 56b. The pinion gears 58a and 58a are placed on the pair of roll supporting shafts 58 and 58 respectively and mesh with the first and second spur gears 56b and 57a. The working rollers 52, 52 are placed in a cantilevered state on the front ends of the roll support shafts 58, 58, as shown in FIG. And rotational force is transmitted from each line shaft 55 to each working roller 52, which is transmitted through a parallel shaft member consisting of a driving support shaft 58, 58 as well as a drive transmission shaft 56 and an intermediate transmission shaft 57.

Although not shown in the drawing, eccentric sleeves with a gap adjusting mechanism connected thereto fit two roll support shafts 58, 58, in which state the roll support shafts are each within a roller stand 51. Supported. The rotation angle position of each eccentric sleeve is varied by the work performed by the gap adjusting mechanism, so that the distance between the axes of the roll support shafts 58, 58 is the pinion gear 58a, 58a and the first and second spur gears 56b, 57a. It is variable while maintaining the state of engagement between them. In this way, gap adjustments between working 52 and 52 are made.

If you use a large number of calibars, ie working balls 52,52 with multiple balls on the surrounding surface, and if there is a roll caliva wear or a change in dimensions after continuous rolling, Instead of a worn Kalibar, a Passbar is exchanged to place another Kalibar in P.

The calibar exchange operation is described in FIG. In this figure, four calibars C ₁ -C ₂ are formed on the outer circumferential surface of the working roller 52, in which the first calibar C ₁ is located on one end face side and fixed to the front end of the roll support shaft 58. It is located on the pass line P.

For example, a calibar change is performed to position the second calibar C ₂ adjacent to the first calibar C ₁ on the passline P, first with a roll fastening cap fitted to the front end of the roll support shaft 58. The clamping cap 60 is removed from the shaft 58 and the next work wheel 52 and spacer 61 are subsequently removed from the roll support shaft 58. Then, the position of the working 52 is opposed to that of the spacer 61. In other words, the work roller 52 and spacer 61 are aligned in this order on the roll support shaft 58 as shown in FIG. 15, and then the roller fastening cap 60 is refitted with the front end of the roll support shaft 58 and fixed thereto. do. The second calibar C ₂ is located at the passline P. In addition, with respect to other working conditions (not shown), the Kalibar exchange is carried out in the same manner as above.

Kalibar exchange, which places the third and fourth calibars C ₃ and C ₄ on the passline P, respectively, is achieved by removing the same roll on the axis and changing the working roller 52, and then in FIG. 14 or 15 Perform work in the assembled state as shown in the figure. Kalibar change operations involving removal of the work roller 55 from the roll support shaft 58 are usually performed on the pass line.

Challenge to solve the problem

However, up to now, considerable time and effort have been required for the calibar exchange operation involving the work rollers (e.g., about 6 minutes for 10 stands). Thus, a problem of significant deterioration of productivity has been raised.

In addition, the result is that the position of the roller's calibar relative to the stand is wrong from the predetermined position, and thus, for example, a difference in path alignment between adjacent stands may occur due to, for example, an assembly error or a mistake in the shape of the roller cal bar. This requires coordination with shim 62, which complicates the calibar exchange.

The present invention has been made in view of the above-mentioned problems, and an object of the present invention is to provide a long product rolling mill capable of easily carrying out a calibar exchange. Accordingly, it is possible to provide a rolling mill that can increase productivity and work efficiency and simplify the overall structure.

Problem solving

According to the long product rolling mill according to claim 1 of the present invention, in order to achieve the above object, a plurality of calibars on the pass line side of the roll stand arranged along the pass line to which the stock is supplied, A pair of working rollers having a bed can be arranged in a cantilevered state, and a movable member in which the long product rolling mill is moved in parallel with each other in accordance with the formation of a space between adjacent calibars is arranged in the axial direction of the working roller. And the working roll is supported to move integrally with the movable member.

Depending on the structure, the calibar exchange is performed by moving the movable member at a distance according to the calibar spacing. In other words, unlike the prior art, there is no need to perform a task involving the removal of each working roller. As a result, the work becomes easier and the time required can be shortened.

In combination with claim 1 according to the long product rolling mill as defined in claim 2, the drive transmission shaft, the intermediate transmission shaft and the pair of roll supporting shafts are located on one end side of the roll stand toward the opposite side. It is arranged in parallel with the other from a driving force input member. And the working roller is coaxially aligned on the front end side of the roll supporting shaft, respectively. The support shaft includes a drive transmission shaft, an intermediate transmission shaft, and a coaxially protrudable / retractable mechanism capable of protruding and retracting while maintaining a peripheral engagement phase in a drive force transmission path extending through the shaft with respect to transmission of rotational drive force. means) are arranged.

Therefore, since the axial protrusion / discharge mechanism is disposed in the drive force transmission passage, the transfer operation of the movable member to the calibar exchange is made while making the position of the drive force input member stationary. For example, even if the driving force is a block mill like structure in which the driving force is distributed from the line shaft to the roll stand, the line shaft is a joint, so-called universal joint, to absorb deviations in the driving force input position for each roll stand. There is no need to. Such high-speed work with high productivity can be made more stable.

Regarding the movable member and the axial protruding / retracting member, for example, as described in claim 3, the roller housing supporting the roller supporting shaft therein can be used as the movable member, and the roller housing surrounds the driving force input member. It is formed separately from the fixed housing. And a spline shaft formed on the intermediate position of the shaft member extending between the fixed housing and the roller housing is used as an axial protruding / extracting mechanism.

As described in claim 4, a gear for transferring a driving force in the interlocked state while causing a shift or deviation in the gear tooth width direction due to the conveying operation of the lower housing is provided on the shaft member supported in the fixed housing. It is installed on the shaft member which is installed and supported in the roll housing, respectively.

According to this structure, it is not necessary to use a separate one such as a shaft coupling such as the spline shaft described above, and thus the overall structure is more simplified.

In this regard, as in claim 5, if the gear on the roller housing side is removably installed in the front end floating of the shaft member protruding from the roller housing toward the fixed housing side, it is more preferable to change gears. Easier

For example, in the above-described block mill, the number of gear teeth in the rotational force transmission path located at each roll stand is arranged so that the rotational speed of the work roller is continuously increased along the passage line. On the other hand, if the roller housing is removed, for example as a replacement for the bearing, the roller housing is replaced with a spare roller housing. In this case, as described above, the preliminary housing can be shared by facilitating installation and removal of the gear which determines the rotational speed of the work roller.

In addition, it is adapted to the structure as described in claim 6, wherein a transport mechanism for transporting the lower housing in the axial direction of the working roller is provided, which is projected axially by the movement of the roller housing. It has an actuating stroke for releasing the engaged state with the surroundings in the ejecting / retracting mechanism, and also an actuating stroke for moving the lower housing to an upwardly hoisted position. According to this structure, maintenance work for the bearing of the above-mentioned roll supporting shaft becomes easy.

More specifically, if the roller housing is moved to a maintenance work area, for example to replace the bearings mentioned above, the roller housing must move out of the fixed housing to a position that does not interfere with the fixed housing before the roller housing is hoisted into the crane. Needs to be. This can be done with a transfer mechanism for transporting the roller housing at the exchange of the calibar. Therefore, it does not require a special moving mechanism and work separately to facilitate the work.

In the long product rolling mill as defined in claim 7, the movable member is fitted with eccentric sleeves that fit snugly on a pair of roll support shafts in order to support the roll support shafts in the roll housing. An axial movement of the eccentric sleeve, which is installed as a mechanism capable of protruding / extracting in the axial direction, comprises a gear and an intermediate transmission shaft for transmitting the driving force in an interlocked state while allowing a deviation occurring in the gear tooth width direction.

With this construction, it is the roll support shaft that needs to be moved during calibar exchange, and the objects to be moved are smaller in size and weight. Thus, as in the case described above, the overall structure becomes small.

In addition, the long-term rolling mill defined in claim 9 is provided with a position sensor for detecting the feeding amount of the movable member.

According to this structure, the timing for performing a stopping operation upon arrival of the movable member at a predetermined position after the start of the movement of the movable member for the calibar exchanger is based on the detection signal given from the position sensor. It can be obtained by. In other words, these tasks are derived by visually checking the axial movement of each task on the pass line. For example, these operations are performed remotely.

EXAMPLE

Example 1

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

In FIG. 4 there are two line shafts 3 and 3 in the mill for long products as an embodiment. This line shaft is driven by the rolling mechanism driving motor 1 through the acceleration mechanism 2. The line shafts 3 and 3 are arranged on both sides in parallel with the rolling pass line P to which a stock such as a wire rod is supplied. Ten roll stands 4 are alternately arranged along the pass line P to form a block mill between the line shafts 3, 3 and the pass line P.

As in FIG. 1, the roll stands 4 are inclined at an angle of 45 degrees with respect to the vertical line Vc passing through the pass line P, and are aligned left-right symmetrically. And along the inclined support surface of the central base 5a and along side bases 5b, 5b located on either side of the central base 5a.

This roller stand 4 is almost the same in structure, and is substantially the same with respect to the roller stands located on the left and right sides of the pass line P. They are just left and right symmetrical and do not differ greatly in structure. Regarding the first degree, therefore, for example, a left-hand roll stand 4 will be described.

The roll stand 4 is composed of a bevel gearbox (fixed housing) 6 installed on the inclined support surface of the side base 5b and a roll housing 7 installed on the inclined support surface of the center base 5a at an angle with respect to the bevel gearbox 6. The bevel gearbox 6 is supported on the line shaft 3, which is passed horizontally through the gearbox, while a pair of working rollers 8, 8 are in the lower housing at the projection from the top surface 7a across the pass line Hc. Mounted on 7.

A drive transmission shaft 10 is provided having a length that reaches both the bevel gearbox 6 and the roller housing 7 to transfer the rotational driving force from the line shaft 3 to the work rollers 8, 8. In the roller housing 7, a total of five shaft members, which are shafts 10, are installed, and the first and second intermediate transfer shafts 11 and 12 and the pair of roll supporting shafts 18 and 18 are located rearward in the drawing with respect to the shafts 11 and 12 do. These shafts are aligned in parallel with each other at an inclination angle of 45 °. These shafts are described in more detail below under the premise that the three sides of the lineshaft are the base and the working rollers 8 and 8 are at the front end.

At the lower end of the bevel gearbox 6, the driven bevel gear 13 is mounted on the drive transmission shaft 10. The driven bevel gear 13 meshes with a driving bevel gear 3a installed as a driving force input member on the line shaft 3, and the first spur gear 14 is driven on the first end side of the same shaft located in the roller housing 7. It is installed on the transmission shaft 10. The first spur gear 14 meshes with the second spur gear 15 located on the base end side of the first intermediate transfer shaft 11. In addition, the first and second pinion gears 16 and 17 have the same number of teeth, are interlocked, and are installed on the front end sides of the first and second intermediate transfer shafts 11 and 12, respectively.

According to this structure, the rotational driving force of the line shaft 3 is first transmitted to the drive transmission shaft by the driving bevel gear 3a and the driven bevel gear 13, and from the next shaft 10, the rotational driving force is applied to the first intermediate transmission shaft 11 to the first and the second. Delivered by the second spur gear 14, 15. In addition, the first and second pinion gears 16 and 17 allow the rotation of the first intermediate transfer shaft 11 to rotate at the same speed or in the opposite direction as the shaft 11.

Also shown in FIG. 2 are a pair of roll supporting shafts 18, 18 which are arranged on the rear side of the figure with respect to the first and second intermediate transfer shafts 11, 12. FIG.

In the same figure, for convenience the shafts 18 and 18 are represented by their axes facing the horizontal direction. The driven pinion gears 19 and 19 have the same number of teeth and are installed on the roll support shafts 18 and 18 respectively at intermediate positions on the shaft. As shown in FIG. 3, the driven pinion gears 19 and 19 are engaged with the first and second piston gears 16 and 17. As shown in FIG. Accordingly, the rotations of the first and second intermediate transfer shafts 11 and 12 are transmitted to the roll support shafts 18 and 18, respectively.

As shown in FIG. 2, the work rollers 8 and 8 are fitted with a roll support shaft 18, which is fitted tightly on a tip portion protruding from the upper surface 7 of the roller housing 7 through the caps 20 and 20. It is fixed at 18.

On the outer circumferential surface of the work rollers 8 and 8, a number of calibars C ₁ and C ₂ ( _two in the figure) are formed in a predetermined space in the axial direction. In the same figure, the first calibar C ₁ located on the base end side is located on the pass line P. FIG.

As shown in the same figure, the eccentric sleeves 21 and 21 are fitted on the roll support shafts 18 and 18 respectively, and the shafts are supported in the roller housing 7 through these eccentric sleeves. A gap adjustment mechanism (not shown) is given on the rear side in the figure with respect to eccentric sleeves 21 and 21. Rotational movement occurs in the eccentric sleeves 21 and 21 through the gap adjusting mechanism by rotating the gap working part 22 protruding outward from the roller housing 7. With this rotational movement, the distance between the axes of the roll supporting shafts 18 and 18 is such that the driven pinion gears 19 and 19 and the first and second pinion gears 16 and 17 mesh with each other on the first and second intermediate transmission shafts 11 and 12. The gap between the working 8 and 8 is thus adjustable as it is variable during operation.

As in FIG. 1, outside of the shaft member described above, the drive transmission shaft 10 extends between the bevel gearbox 6 and the roller housing 7, which is divided into two shaft portions, which are divided into two bevel gearbox 6 and the roller housing. It consists of a driven shaft part 10b supported on seven sides. In this separate position, an axially projecting / retracting shaft coupling (mechanism capable of projecting / extracting axially) 25 is provided, which consists of a spline shaft. In particular, the lower end side of the driven shaft portion 10b protrudes obliquely downward from the lower housing 7, which is formed of a male spline shaft 25a, while the female spline shaft 25b is formed on the upper end portion of the drive shaft portion 10a protruding obliquely upward from the bevel gearbox 6. Is formed. Thus, at the site of the shaft coupling 25, the drive shaft portion 10a and the driven shaft portion 10b are connected for axial mutual movement, respectively, while maintaining peripheral engagement.

On the other hand, the roller housing 7 is slidably slid along the inclined support surface of the center base 5a, and the housing transfer actuator 26 is a hydraulic cylinder such as a sliding cylinder that makes the roller housing 7 move. It is constituted by an inclined support surface of the center base 5a.

In the long product rolling mill, when the rolling mechanism driving motor 1 is operated, the rotational driving force is distributed from the line shafts 3 and 3 to the roller stands 4. In more detail, the rotational driving force is continuously transmitted to the roll support shafts 18 and 18 through the drive transmission shaft 10 and the first and second intermediate transmission shafts. Next, by the work rollers 8 and 8 provided at the front end portions of the roll support shafts 18 and 18, the rolling work of the material such as the wire rod supplied along the pass line P is performed.

On the other hand, the calibar change caused by continuous rolling operation or size difference is performed in the following manner.

Assuming that the first calibar C ₁ is positioned on the passline P at the exchange of the calibar, the housing transfer actuator 26 is beveled by a distance corresponding to the space between the first calibar C ₁ and the second calibar C _2. It is operated to transport the lower housing 7 obliquely downward to the gearbox 6 side. As a result, the second calibars C ₂ and C ₂ simultaneously assume positions on the passlines P on both sides 8, 8, until they are located on the passlines P instead of the first calibars.

Therefore, when the roll housing 7 is conveyed to the bevel gear box side, the axial position of the driven shaft portion 10b of the drive transmission shaft 10 is exchanged with respect to the drive shaft portion 10a. However, it is arranged between the two shaft shaft couplings 25, which are able to protrude and retract axially while maintaining the surrounding engagement, so that the driving force transmission path is maintained from the line shaft 3 to the working shafts 8 and 8. As a result, the calibar exchange is completed only by the previous conveying operation of the roller housing 7, and then it is possible to start rolling soon after the calibar exchange.

In the present embodiment, as described above, the roller housing 7 is provided separately from the bevel gearbox 6, and by carrying the roller housing 7, it is possible to effectively exchange the calibar on the working rollers 8 and 8. Thus, the work required for Kalibar exchange is simplified and short time is sufficient for the same work.

In the following, as described above, the calibar exchange is made by withdrawing each working roller from the associated roller support shaft, which is then passed axially to exchange the spacer insertion position after the roller is fixed. This work has taken much time and labor. For example, ten rolling mill stands took more than six people and took 30 minutes. Due to the high automation and labor saving in the present invention, only one or two people are required for the work area of the block mill during a normal rolling operation. However, in the case of Kalibar exchange, assistance from other working areas is required to shorten the Kalibar exchange time, which increases the workload for workers rather than in the relevant working areas.

In addition, since the working roller is fixed by the internal pressure or the side pressure, respectively, when dust, oil or oil is accumulated on the fixed surface, slip occurs and damage is caused. For this reason, conventional work fixing requires a lot of skill and attention. In addition, the calibar change is performed under adverse conditions, including rolling scale, cooling water, and oil and grease.

On the other hand, in this embodiment, the axially protruding and retractable shaft coupling 25 is installed on the drive transmission shaft 10, and the position of the driven bevel gear 13 does not change even when the roller housing 7 is transported with respect to the calibar exchange. . Thus, the work is made stable at a higher speed.

In particular, in the block mill, a plurality of roller stands 4 are aligned along the pass line P, and the driving force is distributed from the line shafts 3, 3 extending through the roller stands to the roller stands 4. Therefore, when the whole roll stand 4 is replaced with the calibar and the driven bevel gear 13 is replaced, the respective bevel gears move. The engagement between the driven bevel gear and the driven bevel gear is as long as the line shafts are in a straight line. Can't stay over. For this reason, shaft couplings such as universal joints to absorb axial deviations are needed between adjacent stands on each line shaft. However, under high-speed rotation, the use of universal joints is not only expensive, but also uneconomical and technically difficult to produce vibration and noise.

On the other hand, in the present embodiment, the shaft joint 25 is provided on the drive transmission shaft 10 to prevent the positional exchange of the driven bevel gears, so that the same relationship with respect to the line shafts 3 and 3 can be supported by the prior art. Operation can be made stable while bringing high productivity.

Example 2

Another embodiment of the present invention will be described with reference to FIGS. That is, the members having the same function as in the conventional embodiment are denoted by the same reference numerals, and thus description thereof is omitted.

The rolling mill for the long product according to the present embodiment, as shown in FIG. 5, each of the plurality of roll stands 4 is inclined at an angle of 45 °, and is perpendicular to the paper surface constituting the rolling mill as a block mill similar to that shown in FIG. Are arranged in an exchanged manner along a pathline P extending into the.

As in Example 1, each roll stand 4 is provided on the base 5, such as the bevel gearbox 6 and the roll housing 5, the base is inclined at a 45 ° angle to both left and right sides. . As shown in FIG. 6, in the bevel gearbox 6, the drive transmission shaft 10 is supported with a short length, the shaft 10 has a driven bevel gear 13 on the base end and a first spur gear 14 on the tip side. In the same figure, as will also be mentioned later in the other figures, for convenience the axis of the shaft member faces in the horizontal direction.

The first intermediate transfer shaft 11 is formed such that its base end side protrudes to the bevel gearbox 6 side through the wall surface of the roller housing 7. On the protruding end, a second spur gear 15 is provided, for example, to be easily released by oil injection. In the bevel gearbox 6, the second spur gear 15 is engaged with the first spur gear 14 on the drive transmission shaft 10.

On the other hand, the ones installed on the hillside side of the roller housing 7 on the work rollers 8 and 8 form two calibars, the first and second calibars C ₁ and C ₂ , as in Example 1 described above. In FIG. 6 the first calibar C ₁ on the base end side is located on the pass line P. In FIG. In this state, the cap 6 spaced between the opposite end surface of the bevel gearbox 6 and the roller housing 7 corresponds to the axial space between the first and second calibars C ₁ and C ₂ , and the roller housing 7 As will be described later, it is fixed on the base 5 by a clamper 31. In this case, the second spur gear 15 meshes with the first spur gear 14 at a position axially slightly off to the tip side with respect to the first spur gear 14. The toothed numbers of the first and second spur gears 14, 15 are set to allow transmission of rotational driving force from each line shaft 3 in such a staggered state.

The plurality of roller stands 4 having the above structure are arranged in parallel along the pass pine P, so that the finishing rolling of the wire rod is carried out in the same manner as in Example 1 described above through the working rollers 8 and 8 in the roller stands 4.

Kalibar exchange for positioning the second calibar C ₂ on the passpine P instead of the first calibar C ₁ is performed by moving the roller housing 7 in the manner described above. An electric motor 26a is used in this embodiment as a housing shift actuator 26 for inducing this movement movement. Installed on the base 5 is a screw shaft 26b extending in the movement direction. The screwnut 26c is then screwed with the screw shaft 26b and is fitted with a recess formed in the lower end of the flange 7b which is fixed to the roller housing 7. The roller housing 7 is moved by rotating the screw shaft 26b with the electric motor 26a.

As shown in FIG. 5, at the lower side of the roller housing 7, a plurality of clampers 31 are configured to install a hydraulic cylinder for fixing the roller housing 7 to the base 5 before or after the moving operation.

7 shows that the roller housing 7 is moved to the actual close position of the bevel gearbox 6 and its end by operating the electric motor 26a. In other words, in this operation, the second calibar C ₂ is positioned on the passline P by performing a calibar exchange. At this time, the second spur gear 15 of the first intermediate transmission shaft 11 is held in engagement with the first spur gear 14, at which time it is pushed further into the bevel gearbox 6 and slightly axially on the base end side upside down to the case. You get out.

Under such an off-axis engagement, the rotational driving force is transmitted through the first and second spur gears 14 and 15 in the same manner from the line shaft 3 side to the work rollers 8 and 8 side in the same manner.

In this embodiment, as in FIG. 8, the length of the screw shaft 26b is proximal to the leading edge until the position of the roller housing 7 by the so-called housing transfer actuator 26 is such that the second spur gear 15 is completely out of the bevel gearbox 6. The movable stroke is set to be movable.

Thus, in this embodiment, as in the above-described embodiment 1, the calibar exchange is performed by the moving operation of the roller housing 7. For this reason, the axially parallel teeth are formed on the outer periphery of the first spur gear 14 on the drive transmission shaft 10 and on the outer periphery of the second spur gear 15 on the first intermediate transmission shaft 11. Therefore, even if these gears are engaged with each other and an axial deviation occurs at the exchange of the calibar, the axial protruding / ejecting mechanism is constituted. This axial protruding / retracting mechanism eliminates the need for a separate shaft coupling 25 such as the spline shaft used in Example 1 above. Thus the overall structure is simplified.

In the case of shaft couplings, moreover, it is necessary to reserve space for installing the shaft couplings, which leads to an increase in the overall size. In this embodiment, since such a space itself becomes unnecessary, the whole structure is compact and the installation space is made smaller, which is very advantageous for installation.

In addition, plain bearings are inserted between each roll support shaft 18 and the eccentric sleeve 21 fitted thereon, since the bearings are stretchable parts, so the roller housing 7 is frequently maintained when replacing these bearings. It is necessary to carry out the bearing change work by transferring it backwards. In this embodiment, compared to the housing using the shaft coupling, since only one gear 14 is located on the 6 side of the bevel gearbox, the roller housing 7 itself can be made smaller. Therefore, installation or removal is very easy.

In the case of shaft coupling, it is necessary to use the shaft coupling holder for efficient centering when the shaft coupling is released, which makes the shaft coupling more complicated, making it difficult to effectively remove the roller housing. However, in the present embodiment, the removal operation for the roller housing 7 can be effectively done more simply and in particular without the shaft coupling holder.

In addition, in the area of the drive transmission shaft 14, the number of revolutions is 2500rpm, and at such a high speed of rotation, the structure of the present embodiment does not cause a problem such as vibration, and the block mill does not cause a problem such as vibration occurrence under stable conditions. It allows you to work.

According to a structure suitable for this embodiment, the first intermediate transfer shaft 11 protrudes from the lower housing 7 toward the bevel gearbox 6, and the second spur gear 15 is releasably installed on the tip of the shaft, for example, by oil injection. With this structure, the lower housing can be easily taken out of the bevel gearbox 6 and the second spur gear 15 can be replaced with another gear having a different number of teeth.

In other words, the multiple standstands 4 are arranged in a line such that the work roller 8 continuously increases the number of revolutions. Changing the number of revolutions is carried out by changing the number of teeth of the gears engaged with each other. On the other hand, after releasing the roller housing, the roller housing is replaced with a spare roller housing in the atmosphere for bearing replacement or other purposes, and the work then immediately begins. However, the number of such spare roller housings becomes very large when the spare roller housings are prepared for housings having different rotational speeds. For this reason, as described above, if it is possible to easily install and release the second spur gear 15 that determines the rotational speed of each working roller 8, the spare roller housing can be used, thereby simplifying the overall structure.

In the present embodiment, moreover, the roller housing 7 moves along the inclined support surface of the base 5 until the second spur gear 15 is completely pulled out of the bevel gearbox 3, so that, for example, the bearings for the roller support shafts 8, 8 Maintenance work becomes easier.

In carrying out maintenance work, the conveyance work for transporting the roller housing 7 to the crane must be preceded. In this case, it is necessary to lift the roller housing to the crane and guide it to a position that does not interfere with the three sides of the bevel gearbox. Therefore, before lifting to the hoist, it is necessary to withdraw the roller housing 7 from the bevel gearbox 3, and also to move it to be obliquely upward to the position described above. This is done with the housing shift actuator 26 described above. Moving to a crane like this does not require any other special moving mechanism or work, the overall structure is more simplified and the moving work can be easily made.

The present invention is not limited to the above embodiment. In other words, modifications may be made within the scope of the various inventions. For example, in Embodiment 1, the shaft coupling 25 is formed of a spline shaft and installed on the drive transmission shaft 10, as shown in FIG. Here, the first intermediate transfer shaft 11 is divided into two parts (the driving shaft portion 11a and the driven shaft portion 11b). The drive shaft portion 11a is installed thereon as the first spur gear 14, which is applied in the bevel gearbox 6, the female spline shaft 25b is formed at the end face of the drive shaft portion 11a, and the male spline shaft 25a is the driven shaft portion. It is formed at the end face of 11b, which is supported by the roller housing 7, which end protrudes from the housing to the bevel gearbox 6.

In this case, the number of gears is applied in the roller housing 7 and is still small, so that the roller housing 7 can be made small in size so that the roller housing can be easier to install, release, transfer, etc. instead of bearings. do.

In this embodiment, when the movable member is moved when changing the calibar, the roller housing 7 is provided separately from the bevel gearbox 6, which is conveyed on the bases 5, 5a. For example, an eccentric sleeve 21, 21 is suitable for a structure such that it fits on the roll support shafts 18, 18, which is made axially movable in the roll housing 7. And the calibar change is performed by moving the eccentric sleeve.

According to this structure, the object to be operated becomes smaller in size, and the weight of the lower housing 7 is smaller than the weight in the moving structure, so that the structure of the moving mechanism becomes such that the operation is automatically simplified. Manufacturing costs will be reduced.

It is also possible to adapt the structure of the roll supporting shafts 18 and 18 to move axially within the eccentric sleeves 21 and 21, and the change of the calibar is performed by the movement of the shafts 18 and 18. In this case, the object to be moved is smaller in size and smaller in weight, thereby simplifying the overall structure.

When the eccentric sleeves 21 and 21 and the roll supporting shafts 18 and 18 are constituted by movable members, as shown in 10 (a) and 10 (b), the axial protruding / retracting mechanism is held in engagement with the gear. In this case, an axial error occurs when changing the calibar as in the above-described embodiment between each of the roll supporting shafts 18 and the driven pinion gears 19 installed on the first or second pinion gear 16 or 17. Allow, and are installed on the first and second intermediate transfer shafts 11, 12. In addition, in this case, the overall structure is simplified because it is not necessary to separately provide a special component having an axial protrusion and a discharge function.

If the roller housing 7, each eccentric sleeve 21 and each roller support shaft 18 are conveyed to the calibar change as the movable member described above, if their movement is detected by the position sensor, further improvement is made in the operation of the calibar change. Phase and working efficiency are obtained.

In this case, an operation is made to start the movement of the movable member for each calibar change, and the timing for performing the stop operation as the movable member arrives at a predetermined position is determined from an associated position sensor. It is obtained according to the detection signal provided. Therefore, it is not necessary to perform these operations while visually detecting the movement of the working roller 18 on the pass line, but it can be performed remotely, for example, so that the calibar changing operation is facilitated and the time required for changing the calibar is reduced. Will be shortened.

Although the rolling mill in the above embodiment is constituted by a block mill, the present invention is also applicable to rolling mills of other types in which each working roller is installed with cantilever compensation at the tip of the roll supporting shaft.

No content

1 is a vertical sectional view of a rolling mill for a long product composed of a block mill as an embodiment of the present invention.

2 is a cross-sectional view of the basic portion of the rolling mill, showing a roll supporting shaft and a work roller having a work roller installed thereon.

3 is a cross-sectional view taken along the direction of the arrow in FIG. 2.

4 is a plan view showing the overall structure of the block mill.

5 is a front view of a rolling mill for a long product composed of a block mill according to another embodiment of the present invention.

6 is a cross-sectional view showing the internal structure of a roll stand used in the rolling mill shown in FIG.

7 is a cross-sectional view showing the internal state of the lower stand after a calibar exchange (or change) performed from the state of FIG.

8 is a cross-sectional view for showing a state when there is a housing replacement in the rolling mill shown in FIG.

9 is a cross-sectional view showing the structure of the roll stand in the rolling mill according to another embodiment of the present invention.

10 shows the structure of the basic part of the long product rolling mill according to the embodiment of the present invention, wherein the protection (a) is a front view of the basic part, and the roll support shaft and the work roller are shown. As a front view, it shows the state which Calibar exchange is performed from state (a).

11 is a schematic plan view showing the structure of a conventional block mill.

FIG. 12 is a schematic diagram showing the structure of the rotational driving force transmission mechanism for transmitting the rotational driving force from the line shaft to the work roller in the block mill shown in FIG.

13 is a cross-sectional view taken along the arrow Y-Y line in FIG.

14 is a cross-sectional view of the basic portion showing a structure as an embodiment for installing the working roller at the tip of the roll support shaft in the conventional rolling mill.

FIG. 15 is a cross-sectional view of the basic portion showing the installation state after the calibar exchange is performed using the working roller of FIG.

Explanation of symbols on the main parts of the drawings

3a Drive bevel gear (drive force input member)

4-roll stand

6Bevel Gearbox (Fixed Housing)

7roll housing (movable member)

8 working rolls

10 drive transmission shaft

11th Intermediate Transmission Shaft

12 2nd intermediate transmission shaft

18 roll support shaft

21 eccentric sleeve

25 Shaft Couplings (Spline Shaft, Axial Protrusion / Extractor)

26Housing transfer actuator (transfer mechanism)

P pass line

C ₁ , C ₂ Kalibar (formal)

No content

As described above, according to the structure of the rolling mill for long product according to claim 1 of the present invention, a movable member is provided which is moved in the axial direction of the working roller, and the working roller moves integrally with the movable member.

Therefore, since it is not necessary to release the work roller when changing the calibar, the calibar changing operation is simplified, the time required is short, and thus the productivity is increased.

In the long product rolling mill as defined in claim 2, an axial protruding / ejecting mechanism is provided in a drive transmission passage for transmitting a rotational driving force to each work roller from a driving force input member located on one side of the roll stand. Therefore, the transfer operation of the movable member for changing the calibar can occur while holding the position of the unchanged drive input member. For example, according to the structure of claim 3, the roll housing is separated from the fixed housing surrounding the driving force input member and used as a movable member as a roll support shaft, which is to be supported inside the roller housing, and is capable of axial protruding / extracting. The spline shaft as a member is provided at an intermediate position of the shaft member extending in both the fixed housing and the roller housing so that the driving force is distributed from the line shaft to each roll stand as in the block mill described above. Even in such a structure, the line shaft can be configured as a shaft surrounded by straight lines. Therefore, the high speed operation which brings high productivity can be made more stable.

According to the long product rolling mill as defined in claim 4, the gears installed on the shaft member are moved axially while being engaged with each other, thereby contemplating an axial protruding / retracting mechanism, and the aforementioned spline shaft As such, it is not necessary to separately provide such as a shaft coupling, so that the whole structure can be simplified.

In the long product rolling mill defined in claim 5, the gear on the roller housing side is releasably installed on the front end of the shaft member protruding toward the fixed housing, and thus, for example, between the roller stands in the case of constituting a block mill. The difference in the number of revolutions of can be overcome by simply changing the gear to another gear. As such, the preliminary housing is usually available and in this case the overall structure is simplified.

In the long product rolling mill as defined in claim 6, the moving conveying mechanism of the roller housing when changing the calibar has a movable stroke for moving the roller housing to the hoist movable position upward. Thus, the roller housing is hoisted by a crane at transport time, for example, as a maintenance work station for replacing a bearing, so that a separate moving mechanism or a moving operation is not required and the work can be easily performed.

In the long product rolling mill as defined in claim 7, the movable member is composed of an eccentric sleeve fitted tightly on a pair of roll supporting shafts, so that the object to be moved in the calibar change becomes smaller and lighter. The movement operation is made simply and automatically, resulting in higher productivity and cost savings.

In the long product rolling mill defined in claim 8, since the movable member is constituted by a roll supporting shaft, the object to be moved by changing the calibar becomes smaller and lighter in size, and thus, the overall structure Simplifies and reduces total manufacturing costs.

In the long product rolling mill as defined in claim 9, a position sensor is provided for detecting the movement amount of the movable member, and the axial movement of each working roller is changed visually on the pass line, for example, when changing the cab. It can be done remotely without the need for easier calibar changes and less time required for calibar changes.

Claims (9)

On the passline side of the roller stands placed towards the pathline as the stock enters, a pair of working rollers with multiple calibars on the outer surface are arranged in cantilevered state in parallel to each other. In the rolling mill for long products, The movable member moving along the space between the adjacent calibars is disposed in the axial direction of the working roller, and the working roller is supported to move integrally with the movable member (A long) product rolling mill) 2. The rolling mill of claim 1, wherein the drive transmission shaft, the intermediate transmission shaft, and the pair of roll supporting shafts are mutually parallel from a driving force input member positioned on one end side of the roll stand toward the opposite end side. And the working rollers are coaxially installed on the front end side of the roll supporting shaft to transfer rotational driving force from the driving force input member to the driving transmission shaft and the intermediate transmission shaft, and are also capable of protruding / retracting axially. And a protruding / retractable mechanism capable of protruding and retracting axially while being in peripheral engagement with respect to the transmission of the rotational driving force is disposed in a driving force transmission passage extending through the shaft. 3. The movable member of claim 2, wherein the movable member comprises a roller housing supporting a roller supporting shaft therein, and the roller housing is formed separately from the fixed housing for sealing the driving force input member therein, and the axial protrusion / exit The possible mechanism is a long product rolling mill, characterized in that it is constituted by a spline shaft formed at an intermediate position of the shaft extending between the fixed housing and the roll housing. 3. The movable member according to claim 2, wherein the movable member is composed of a lower housing for supporting the roll supporting shaft therein, and the lower housing is formed separately from the fixed housing for sealing the driving force input member therein. The moon gear is installed so as to protrude / retract axially on the shaft member supported by the fixed housing and the shaft member supported by the roller housing, even though an error occurs in the gear tooth width direction due to the transfer operation of the roller housing in the interlocked state. Long product rolling mill, characterized in that. 5. The rolling mill for a long product according to claim 4, wherein the gear on the roller housing side is releasably installed on the front end of the shaft member protruding from the roller housing toward the fixed housing side. 6. A transport mechanism according to any one of claims 3, 4 and 5, wherein a transport mechanism is provided for transporting the roll housing in the axial direction of the work roller, and the transport mechanism protrudes / axially such as the roll housing moves. A rolling mill for a long product, characterized in that it has a movable stroke which releases the state engaged with the surroundings so as to be retractable and moves the lower housing up to the hoist movable position. 3. The movable member according to claim 2, wherein the movable member is axially mounted on the pair of roll support shafts to support the roll support shafts in the roll housing, and on the roll support shafts and the intermediate transfer shaft. And a gear for transmitting the driving force in the interlocking state while allowing a deviation in the claw width direction with the axial movement of the eccentric sleeve installed by the protruding / retracting mechanism. 3. The roll supporting shaft according to claim 2, wherein the movable member is constituted by a roll supporting shaft, and the transmission gear of driving force is in the gear tooth width direction having an axial movement of the roll supporting shaft while being engaged with each other. And a long product rolling mill, characterized in that respectively installed on the intermediate transfer shaft. The long product rolling mill according to any one of claims 1 to 8, wherein a position sensor for detecting a feed amount of the movable member is provided.