JP2003025005A - Apparatus and method for reducing slab width - Google Patents

Abstract

PROBLEM TO BE SOLVED: To restrain the occurrence of buckling with a slab conveying means having simple structure. SOLUTION: An apparatus for reducing the slab width is provided with a pressing tool for edging the slab and a width press driving device with which this pressing tool can reciprocaly drive in the slab width direction through a block. Then, in the width-press driving device, a rotating shaft is supported with a supporting member through a first bearing and this rotating shaft is connected with the block through a second bearing, and the first bearing or the second bearing is formed as an eccentric bearing.

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a slab width reducing device and a slab width reducing method for reducing the width of a slab.

[0002]

2. Description of the Related Art In the width reduction technique using a press tool described in Japanese Patent Laid-Open No. 8-224605, a press tool is arranged in the center of a device, and a housing for receiving a pressing force is provided on a side of a slab in a longitudinal direction. And one is placed on the outlet side. A pinch roller, which is a slab conveying means, is installed adjacent to the outside of these two housings. Four bearings for supporting the crankshaft are arranged at both ends of each housing.

[0003]

In the above-mentioned prior art, 2
Since the pinch rollers are installed adjacent to the slab entrance and exit on the outside of the book housing, the distance between the entrance and exit pinch rollers is long and short slabs with a relatively short distance in the longitudinal direction are conveyed to the width press machine. There is a problem that you cannot do it. Further, there is a problem that the width-wise restraining force of the slab is weakened in inverse proportion to the distance between the front and rear pinch rollers during the width pressing, and the slab is likely to buckle in the width direction.

Further, four bearings for supporting the crankshaft are arranged at both ends of each housing, and four connecting rods for connecting the width reduction block on which the press tool is mounted and the crankshaft are also arranged. As a result, the number of bearings becomes eight, and the number of parts is large and the construction cost is high. A rolling bearing is generally used as the bearing that supports the crankshaft. Its outer diameter is about 1800 mm, which makes it larger. The life of the bearing is determined by the load history of the rolling surface of the bearing outer ring on which the roller rolls. The part of this bearing that bears the pressing force is only about 90 degrees of the part on the opposite side of the press tool when viewed from the center of the bearing, and the other 3/4 is not effectively used. This outer ring of large diameter is rotated. Therefore, two housings and a large and long crankshaft are required.
Maintenance work is very difficult due to the large number of parts and large size. The housing is a heavy product with a weight of over 100 tons, and the material is cast steel or a welded structure of ultra-thick slab material, and its manufacturing requires high cost and advanced technology. There are challenges.

As described above, the conventional technique has many problems in terms of performance, economy, maintenance of machine, structure and manufacturability.

An object of the present invention is to provide a slab width reducing device and a slab width reducing method which are capable of suppressing the occurrence of buckling by arranging slab conveying means in close proximity with a simple structure.

[0007]

A slab width reducing device of the present invention comprises a press tool for width-reducing a slab and a width press drive device for enabling the press tool to reciprocate in the slab width direction via a block. Equipped with the width press drive device,
A rotatable rotating shaft is supported by a support member via a first bearing, the rotating shaft is connected to the block via a second bearing, and the first bearing or the second bearing is an eccentric bearing. And

Alternatively, the slab width reducing method of the present invention is a slab width reducing method using a slab width reducing device equipped with a press tool, wherein the slab width is reduced to a supporting member via an eccentric bearing at the center of a rotatable rotary shaft. The pressing tool is supported and connected to both ends of the rotating shaft via blocks, the rotating shaft is rotated, and the pressing tool is reciprocated in the slab width direction to reduce the width of the slab.

[0009]

BEST MODE FOR CARRYING OUT THE INVENTION (First Embodiment) An embodiment of the present invention will be described below with reference to the drawings. Figure 1
FIG. 2 shows a partial plan view of one side of a width press apparatus which is an embodiment of the present invention, FIG. 2 shows a partial side view of one side of a width press apparatus which is an embodiment of the present invention, and FIG. 1 is an overall plan view of a slab width reducing device that is an embodiment of the present invention.

As shown in FIGS. 1 to 3, the slab width reducing device of this embodiment mainly consists of a width press drive device for reciprocally moving the press tool 11 to width press the slab, and a desired slab width. It is provided with a slab width adjusting device to be set and a slab moving device which is a conveying means for moving the slab in its longitudinal direction under desired conditions.

The width press drive device is supported by a single housing 1 which is a support member arranged in the central portion. Eccentric bearings 2 are installed near both ends of the housing 1 in the longitudinal direction. For the pair of press tools 11, the shafts 3 are arranged at the column portions near the both ends in the longitudinal direction of the housing 1, respectively. A shaft 3 is shrink-fitted and inserted into an inner ring of the eccentric bearing 2. That is, the eccentric bearing 2 rotatably supports the shaft 3 substantially in the center of the shaft 3 in the axial direction.

The shaft 27 is rotatably supported by bearings 27 in the vicinity of both ends of the shaft 3 in the axial direction of the shaft 3. By rotating the shaft 3, the press tool 11 can be moved forward and backward through the connecting rod 4, the outer block 5, and the inner block 10 to which the bearing 27 is attached. The outer block 5 is provided with means for guiding reciprocating movement. That is, the outer block 5 includes a support roller 36 that is rotatable along the outer wall of the upper surface of the housing 1, and a support roller shaft 37 that is a rotation axis of the support roller. The support roller 36 allows the outer block 5 to be accurately reciprocated along the outer wall of the upper surface of the housing 1.

By using the eccentric bearing structure as the reciprocating means, the number of bearing parts can be reduced. Also,
In the conventional eccentric crankshaft mechanism, it is necessary to support the support members at two places, but the eccentric bearing structure of the present embodiment can have one support structure, and the housing 1 can be one. It is possible to have a simple structure. And
The housing 1 is usually an expensive member, and since the installation work of the housing 1 requires a lot of time and labor, it is possible to obtain great effects such as a cost reduction and a construction period reduction as compared with the conventional two-housing. .

Further, since there is only one housing 1, it is possible to arrange the slab conveying means in close proximity. In other words, in the conventional two-housing, if it is attempted to arrange the conveying means inside both of them, it is difficult to attach the driving device for the conveying means. Therefore, it is necessary to provide them on the outer side of the two housings, and the distance between the transport means on the inlet side and the transport means on the outlet side of the slab is increased. If the distance between the transport means on the inlet side and the distance on the outlet side of the slab is increased, even if a short slab is introduced, the slab cannot be transported, and the length of the slab that can be introduced is limited. In the present embodiment, since the housing 1 has one housing with the eccentric bearing structure, it is possible to provide the respective conveying means in the immediate vicinity of the inlet side and the outlet side of the housing 1. Therefore, it is possible to introduce a short slab. Further, this conveying means also serves as a pressing means from the up and down direction. Therefore, since the position to be pressed by the press tool 11 and the respective conveying means can be arranged close to each other, it is possible to obtain the effect of suppressing the buckling when the pressing force presses from the vertical direction of the conveying means.

Therefore, the buckling can be suppressed by the slab conveying means with a simple structure.

Here, in this embodiment, the eccentric bearing 2 is applied to the bearing (for example, the first bearing) on the side that imparts the rotational force to the shaft 3, and the bearing on the side that reciprocates from the shaft 3 (for example, the first bearing). The bearing 27 is applied to the second bearing),
The respective configurations may be reversed. It is preferable that one bearing has an eccentric structure and the other bearing has a concentric structure.

For example, as an example of the reverse configuration, FIG.
The partial top view of one side of the width | variety press apparatus which is one Example of this invention is shown. As shown in FIG. 8, the eccentric bearing 2 is arranged in the connecting rod 4, which is the side that reciprocates from the shaft 3. A shaft 3 is connected to the eccentric bearing 2 by shrink fitting. Here, the eccentric bearing 2 is arranged at the central portion of the shaft 3 in the axial direction. Then, the bearing 27 is provided on the housing 1 side, which is the side that applies the rotational force to the shaft 3. Here, the bearings 27 are arranged at both axial ends of the shaft 3. A support base 26 that supports these two bearings 27 is provided, and the support base 26 is fixed to the housing 1. Even in such a structure, the eccentric bearing mechanism can be applied to the reciprocating mechanism.

In the embodiment shown in FIG. 8, there is one screw 7. At this time, it is desirable that the point of application of the press load of the press tool 11, the axial center of the single screw 7, and the load center on the housing 1 side substantially coincide with each other. Unequal load can be suppressed by matching these.

The housing 1, which is a supporting member, has an upper surface,
It has a mouth-like shape with a bottom part, a first pillar and a second pillar. In other words, it has a shape in which a plate-shaped member is erected in a vertical direction and the inside thereof is hollowed. The shaft 3 and the like described above are attached to and supported by the mouth-shaped first pillar and the second pillar, respectively. Since it has such a mouth-like shape,
It is possible to maintain an appropriate strength with respect to the force acting toward the outside. In addition, the upper surface of the support member can serve as a guide for the reciprocating motion of the press tool. The top surface portion and the bottom surface portion of the support member suppress the deformation of the pillar due to the outward force on the pillar.

The two columns can respectively support the reciprocating mechanism and the position adjusting mechanism of each of the pair of press tools 11. Various mechanisms are arranged and housed between the two columns.

As a driving force transmission mechanism to the width press driving device, a press driving electric motor 19 which emits a driving force, a coupling 20 which connects the press driving electric motor 19 and the driving device 21 and transmits the driving force, and a driving force A drive machine 21 that reduces the rotation speed to an appropriate number of revolutions, and a free drive shaft 22 that transmits a rotational force from the drive machine 21 to the shaft 3 are provided. Since the movable drive shaft 22 is provided, even if the axial center of the shaft 3 reciprocates in the horizontal direction in the direction perpendicular to the axial direction of the shaft 3 (slab width direction), the movement can be followed and the rotational force can be changed. Can be communicated. In other words, even if the shaft center of the shaft 3 to be rotated reciprocates in the direction perpendicular to the shaft 3, the rotational force can be transmitted to the shaft 3 by the freely movable drive shaft 22.

The slab width adjusting device includes a nut 6 provided on the outer block 5 and screws 7a and 7b screwed to the nut 6,
A worm gear 8 is provided on the outer circumference of the nut 6. The nut 6 can be rotated by a worm shaft 9 that is screwed into the worm gear 8 and is rotationally driven. The rotation of the nut 6 allows the screws 7a and 7b to move along the screw axis. That is, these screws 7a, 7
By moving b, the relative positions of the inner block 10 and the outer block 5 connected to the tips of the screws 7a and 7b can be adjusted, and the position of the press tool 11 attached to the inner block 10 can be adjusted. By adjusting the relative positions of the inner block 10 and the outer block 5, the position of the press tool 11 in the slab width direction can be set. A balance cylinder 18 is attached to the inner block 10 and the outer block 5. The balance cylinders 18 are provided above and below the slab height (pass line), respectively, and are configured to balance the gap between the inner block 10 and the outer block 5. Further, the vertical balance means can suppress the rattling of the device in the vertical direction.

The mechanism for transmitting the driving force to the slab width adjusting device includes a drive motor 16, a free drive shaft 17 connected to the drive motor 16, and a worm shaft 9 connected via the free drive shaft 17. ing.

As shown in FIG. 5, the slab moving device, which is a slab conveying means, is operated by pinch rollers 49 arranged before and after the main press. This pinch roller 49
It is provided on the entrance side and the exit side of the slab 13 to this device.
A pair of pinch rollers 49, which are the transporting means, are provided above and below the slab, and a pressing force is applied to the slab by a minute force and the pinch rollers 49 are rotatable. At least one pinch roller 49 is provided with a rotation drive device,
The slab 13 is rotated and conveyed from the entrance side to the exit side. Conventionally, if two housings 1 are arranged and an eccentric crank is used, it is necessary to provide the conveying means outside the two housings due to the necessity of a driving device for the conveying means. However, in the present embodiment, the supporting member is provided. Since only one housing 1 may be provided at the center of the apparatus, the center distance Lp between the pinch rollers 49, which are the transporting means disposed before and after it, can be minimized. Therefore, the buckling is suppressed by the slab conveying means with a simple structure. Further, since the slab transportation means can be arranged close to each other, the width of the short slab can be reduced.

Reference numeral 12 in FIG. 3 indicates the path center of the slab 13 which is the material to be pressed. Reference numeral 14 indicates a center line of the eccentric bearing 2. Reference numeral 15 indicates the center line of the shaft 3.

Next, the initial position setting operation and the pressing operation of the slab moving device configured as described above will be described in detail below.

In the initial position setting operation by the slab width adjusting device, first, the driving electric motor 16 is driven, and the rotational driving force is transmitted to the worm shaft 9 which is connected to the driving electric motor 16 via the freely movable driving shaft 17. To be done. The rotational force of the worm shaft 9 is transmitted to the worm gear 8 and rotates the nut 6. By rotating the nut 6, the screws 7a and 7b can be moved in the screw axial direction with reference to the outer block 5. In addition, the inner block 10 is screwed by the balance cylinder 18 shown in FIG.
It is pressed against the tip of b. The balance cylinder 18 balances the force in the gap between the outer block 5 and the inner block 10.

As described above, the rotation of the drive motor 16 increases or decreases the gap between the inner block 10 and the outer block 5, so that the distance between the press tool 11 and the outer block 5 can be increased or decreased. Then, in this initial position setting operation, the nut 6 is rotated in accordance with the initial width W of the slab 13 that is the material to be pressed to move the screws 7a and 7b in the axial direction with the outer block 5 as a reference, and Inner block 10
Is carried out by moving in the axial direction.

In the press operation by the width press drive device, the press drive electric motor 19 is driven, and the speed is reduced to an appropriate rotational speed by the drive device 21 via the coupling 20. The drive shaft 21 is rotated by the driving machine 21, and the shaft 3 connected by shrink fitting is rotated. The inner ring of the eccentric bearing 2 rotates via the shaft 3, and the outer block 5 is rotated via the connecting rod 4 by a distance twice the eccentric amount e.
Can be moved in the width direction of the slab 13. At this time, the outer block 5 moving along the outer wall of the housing 1
Moves in a direction perpendicular to the moving direction of the material slab 13 to be pressed, and the press tool 11 and the inner block 10 connected thereto move in the same manner, so that a pressing operation can be performed.

The mechanisms for performing these pressing operations are arranged symmetrically with respect to the path center 12 of the slab 13 which is the material to be pressed, and the left and right mechanisms operate symmetrically with respect to the path center. Therefore, the total width reduction of the slab 13 is 4e on the left and right sides.

The driving machine 21 is arranged symmetrically with respect to the path center 12. In order to operate the left and right press mechanisms symmetrically with respect to the path center, a connecting shaft 23 is provided between the two driving machines 21. There is. That is, the drive shaft 21 is synchronized by the connecting shaft 23.

As shown in FIGS. 1 and 2, the outer block 5 moves by a distance twice the eccentric amount e of the eccentric bearing 2. A balance cylinder 24 is installed on the outer wall of the housing 1 in order to ensure the contact between the connecting rod 4 and the outer block 5,
Further, the contact point of the connecting rod 4 with the outer block 5 is
An arcuate portion 25 is provided in a part of the above to absorb the swinging movement of the connecting rod 4 due to the eccentric rotation movement of the shaft 3. In addition, a bearing 27 is incorporated between the connecting rod 4 and the shaft 3 to similarly absorb the swinging motion of the connecting rod 4.

A ring 28 is installed on the outer side of the eccentric bearing 2 and fixed to the housing 1 by a cap 29 and a bolt nut 30.

Next, referring to FIGS. 2 and 5, the outer block 5
The detailed configuration of the inner block 10 will be described. 5 is shown in FIG.
The CC arrow view of is shown.

As shown in FIG. 5, the outer block 5 and the inner block 10 are constructed such that the single housing 1 is arranged at the center and straddles it. It mainly includes rails 31 provided on both outer walls of the housing 1, support rollers 32 that run on the rails 31, and a shaft 33 that connects the rails 31 to the inner block 10. With this configuration, the inner block 10 can be moved along the outer peripheral surface of the housing 1 in a direction perpendicular to the moving direction of the slab 13 (width direction of the slab 13). Furthermore, to ensure this movement,
Inner block 1 is provided with guides 34 on both outer walls of housing 1.
The guide rollers 35 may be provided on both sides of 0.

As for the outer block 5, similarly to the inner block, the support roller 36, the shaft 37, the guide 38,
By providing the guide roller 39, the outer block 5 can be reliably moved in the width direction of the slab 13.

As described above, since the eccentric bearing is used for the reciprocating mechanism at both ends inside the housing, the number of bearings for supporting the eccentric bearing can be greatly reduced and the number of parts can be reduced. Further, by adopting the eccentric bearing, the supporting member can be a single housing. Further, since the eccentric bearing is adopted for the reciprocating mechanism and the eccentric bearing can be supported by one housing, the maintainability of the bearing is significantly improved.

(Second Embodiment) The effective use of the rolling surface of the eccentric bearing portion employed in this embodiment will be described. FIG. 6 shows a structural explanatory view of the eccentric bearing portion. The bearing includes an outer ring 40, rollers 42, and an inner ring 41 into which the shaft 3 is inserted. The inner ring 41 has the center line 14 of the eccentric bearing 2,
It has an eccentricity e with respect to the center line 15 of the shaft 3. When the press load P acts on the eccentric bearing 2, a load zone A is generated on the rolling surface of the roller 42 of the outer ring 40 on the opposite side. Therefore, only the area of the load area A of the rolling surface is used, and the range of 360 ° -A of the rolling surface of the outer ring 40 is not effectively used.

In order to effectively utilize the rolling surface of the outer ring 40, in this embodiment, a gear tooth profile is provided on the outer periphery of the end of the ring 28, and a pinion 43 meshing with the gear tooth profile is engaged. That is, means for rotating the rolling surface of the outer ring 40 is provided. Then, the pinion 43 can be rotated by an arbitrary driving device to rotate the rolling surface of the outer ring 40.
By rotating the rolling surface of the outer ring 40, the outer ring 4
The rolling surface of 0 can be effectively used, and the life can be extended. It is desirable to perform this rotation operation at a desired time, for example, periodically. As described above, the rolling surface of the outer ring 40 can be effectively used, and the bearing life can be extended.

(Third Embodiment) An eccentric load suppressing means acting on a press tool will be described below. In FIG. 1, the center line 44 of the housing 1 is also the center line of the two screws 7a and 7b arranged in this embodiment.

It is considered that the point of action of the press load P varies depending on the width reduction amount of the slab 13. A comparison will be made between the case where the width reduction amount ΔWa is relatively large and the case where the width reduction amount ΔWb is small.

The contact length between the press tool 11 and the slab 13 is
A large width reduction ΔWa is La, and a small width reduction ΔWb is Lb. The action point of the press load P is almost in the middle of the contact length, and the action point 45 in FIG.
a, an action point 45b. That is, when the width reduction amount is ΔWa and when the width reduction amount is ΔWb, the action points 45a to 45
It changes by ΔL up to b. Due to the change in the action point due to the change in the width reduction amount, an eccentric load acts on the housing 1, the screw 7, the eccentric bearing 2, and the like.

In this embodiment, a cylinder 46 for moving the press tool 11 back and forth in the same direction as the moving direction of the pressed material slab 13 is provided at the end of the inner block 10. The cylinder 46 is attached to the inner block 10 and can move the press tool 11 in the longitudinal direction (conveying direction) of the slab 13. The action point of the press load P moves according to the width reduction amount by the deviation ΔL between the action point 45 and the center line 44 of the housing 1. Therefore, the press tool 11 is moved by the cylinder 46 according to this action point movement. Constitute. With such a configuration, it is possible to suppress an unbalanced load due to a change in the action point of the press load P. In this embodiment, an example in which two screws 7a and 7b are arranged is shown.
One screw is enough. The structure of one screw is shown in Fig. 8.
Etc. will be described later.

As described above, since the means for moving the press tool 11 in the slab conveyance direction is provided, it is possible to suppress an eccentric load caused by a change in the press action point due to a change in the width reduction amount. Further, by providing the inner block 10 with means for moving in the slab conveyance direction, adjustment with the load transmission center with respect to the housing 1, the screw 7, the eccentric bearing 2, etc. can be easily carried out, and an eccentric load can be suppressed.

(Fourth Embodiment) The structure and manufacture of the housing 1 will be described below. The housing 1 may be an integral structure of a welded structure of cast steel or super-thick slab material. However, considering the manufacturability, the following structure is desirable.

As shown in FIG. 7A, the housing 1
Is preferably composed of a plurality of thick steel plates 1a, 1b, 1c and the like, and these are fixed by bolts and nuts 47. With such a structure, manufacturing is facilitated while maintaining strength.

Further, as shown in FIG. 7B, the housing 1
Is preferably composed of a plurality of thick steel plates 1a, 1b, 1c and the like, and these are welded and fixed to each other 48.
With such a structure, manufacturing is facilitated while maintaining strength.

Since one housing can be constructed for one device, a plurality of such thick steel plates can be used, and manufacturability is improved.

Further, by using a single housing and a plurality of thick steel plate welded structures, the construction cost can be reduced, the distance from the pinch rollers installed before and after the press can be shortened, and short slabs can be used. It becomes possible to press.

As described above, instead of the conventional crankshaft, the eccentric bearings are employed in the reciprocating mechanism at both ends inside the housing, so that the number of bearings for supporting them is greatly reduced and the parts are The score can be reduced. Further, by adopting the eccentric bearing, the supporting member can be a single housing. Also, since the eccentric bearing is adopted for the reciprocating mechanism and the eccentric bearing can be supported by one housing, the maintainability of the bearing is significantly improved and the outer ring of the eccentric bearing can be easily rotated. it can. Furthermore,
Since it is not surrounded by two housings, maintenance of various devices is easy.

Further, in the press tool, since the point of action of the press force changes depending on the press rolling amount, an unbalanced load acts on the crankshaft support bearing, but the press tool is moved back and forth in the slab conveyance direction. Depending on the configuration
The action point of the pressing force can be adjusted so as to coincide with the center of the housing and the bearing, and the unbalanced load can be suppressed. When the press tool is provided with a parallel portion and an inclined portion along the slab conveyance direction, the point of action of the pressing force changes particularly depending on the press reduction amount. It is effective in the case of a press tool having an inclined portion.

According to the above-described embodiment, since one housing is arranged at the center, the distance between the pinch rollers arranged before and after the press for conveying the material slab 13 to be pressed can be minimized. The slab can be pressed and the widthwise buckling that occurs during pressing can be suppressed.

Further, since one eccentric bearing is arranged at each end of the housing in order to obtain the press stroke, the number of bearings can be greatly reduced and the cost can be reduced.

Further, since the housing has a welded structure of a plurality of thick steel plates, the manufacturing is easy and the cost can be reduced. Further, if a high tensile steel plate is adopted, the cross-sectional area of the housing can be reduced and the weight can be reduced. Further, the cost can be reduced.

Since the point of action of the press load is at the center of the press, the eccentric load does not act on the housing, the eccentric bearing, and the screw portion. Since it is possible to use only one screw, the cost can be further reduced.

[0056]

According to the present invention, it is possible to provide a slab width reducing device and a slab width reducing method capable of suppressing buckling by arranging slab conveying means in a close proximity with a simple structure. .

[Brief description of drawings]

FIG. 1 is a partial plan view of one side of a width press apparatus according to an embodiment of the present invention.

FIG. 2 is a partial side view of one side of a width press device according to an embodiment of the present invention.

FIG. 3 is an overall plan view of a width press device that is an embodiment of the present invention.

FIG. 4 shows a view taken along the line BB of FIG.

5 shows a view taken along the line CC of FIG.

FIG. 6 is a structural explanatory view of an eccentric bearing portion.

FIG. 7 shows a structural explanatory view of a housing.

FIG. 8 is a partial plan view of one side of a width press device according to an embodiment of the present invention.

[Explanation of symbols]

1 ... Housing, 2 ... Eccentric bearing, 3, 33 ... Shaft, 4 ... Connecting rod, 5 ... Outer block, 6 ... Nut, 7 ... Screw, 8 ... Worm gear, 9 ... Worm shaft, 10 ...
Inner block, 11 ... Press tool, 12 ... Path center, 13
... slab, 14 ... center line of eccentric bearing, 15 ... center line of shaft 3, 16 ... drive motor, 17 ... universal drive shaft,
18, 24 ... Balance cylinder, 19 ... Press drive motor, 20 ... Coupling, 21 ... Drive machine, 22 ... Free drive shaft, 23 ... Connection shaft, 25 ... Arc part, 26 ... Support base, 27 ... Bearing, 28 … Rings, 29… Caps, 3
0, 47 ... Bolt nuts, 31 ... Rails, 32, 36 ...
Support roller, 34, 38 ... Guide, 35, 39 ... Guide roller, 37 ... Support roller shaft, 40 ... Eccentric bearing outer ring, 41 ... Eccentric bearing inner ring, 42 ... Eccentric bearing roller, 43 ... Pinion, 44 ... Center line of housing 1, 45 ... Point of action of press load P, 46 ... Cylinder, 48 ... Weld fixation, 49 ... Pinch roller.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Takashi Kamoshida             3-1-1 Sachimachi, Hitachi City, Ibaraki Prefecture Stock Association             Hitachi, Ltd., Hitachi Works (72) Inventor Nao Hashimoto             3-1-1 Sachimachi, Hitachi City, Ibaraki Prefecture Stock Association             Hitachi, Ltd., Hitachi Works F-term (reference) 4E002 AB01 AB04 BD01 CA09

Claims (13)

[Claims] 1. A press tool for width-reducing a slab, and a width press drive device capable of reciprocating the press tool in a slab width direction via a block, the width press drive device being rotatable. A slab width in which the shaft is supported by a supporting member via a first bearing, the rotary shaft is connected to the block via a second bearing, and the first bearing or the second bearing is an eccentric bearing. Reduction device. 2. A press tool for width-reducing a slab, a width press drive device capable of reciprocating the press tool in the slab width direction, a support member for supporting the width press drive device, and a bearing for the support member. A slab width reducing device for converting the rotational motion of the rotary shaft into a reciprocating motion of the press tool in the slab width direction by an eccentric bearing mechanism. 3. A rotatable rotary shaft, a first bearing for rotatably supporting the rotary shaft, a support member for supporting the rotary shaft via the first bearing, and a first bearing for the rotary shaft. A slab width reduction device that is connected via two bearings and is provided with a press tool that can reciprocate by the rotation of the rotary shaft, wherein the first bearing or the second bearing is an eccentric bearing. 4. A press tool for width-reducing a slab, a width press drive device for enabling the press tool to reciprocate in the slab width direction through a block, and means for adjusting a gap between the press tool and the block. In the width press drive device, a rotatable rotary shaft is supported by a support member via a first bearing, and the block is connected to the rotary shaft via a second bearing, Slab width reducing device having the eccentric bearing as the bearing or the second bearing. 5. The slab width reducing device according to claim 1, wherein the supporting member has a welded structure of a plurality of thick steel plates. 6. The slab width reducing device according to claim 1, further comprising an outer ring rotating device that rotates an outer ring of the eccentric bearing. 7. The slab width reducing device according to claim 1, further comprising a press tool moving device for moving the press tool in a horizontal plane at a right angle to a reciprocating direction. Slab width reduction device. 8. A press tool having a parallel portion and a slanted portion for width-reducing a slab, and a width press drive device capable of reciprocating the press tool in the slab width direction via a block. A slab width reducing device provided with a press tool moving device that can move the press tool in a direction perpendicular to the reciprocating direction in a horizontal plane so as to suppress an unbalanced load. 9. A press tool for width-reducing a slab, a width press drive device capable of reciprocating the press tool in a slab width direction through a block, and an upper surface portion and a bottom surface supporting the width press drive device. Part, a support member having first and second columns, and means for adjusting a distance between the press tool and the block, and a rotating shaft rotatable to each of the first and second columns of the support member. A slab width reduction in which the first bearing or the second bearing is an eccentric bearing, and the block is connected to the rotary shaft via a second bearing. apparatus. 10. A press tool for width-reducing a slab, and a width press drive device for enabling the press tool to reciprocate in the slab width direction via a block, wherein the width press drive device is rotatable. The shaft is supported by a support member via a first bearing, the rotary shaft is connected to the block via a second bearing, and the first bearing or the second bearing is an eccentric bearing, A slab width reduction device that connects a drive motor to a shaft via a freely movable drive shaft. 11. A slab width reducing method using a slab width reducing device equipped with a press tool, comprising: supporting a supporting member at a central portion of a rotatable rotating shaft through an eccentric bearing, and both end portions of the rotating shaft. A slab width reduction method in which the press tool is connected to a block via a block, the rotary shaft is rotated, and the press tool is reciprocated in the slab width direction to reduce the width of the slab. 12. A slab width reducing method using a slab width reducing device equipped with a press tool, comprising: supporting a supporting member through an eccentric bearing at a central portion of a rotatable rotary shaft, and both end portions of the rotary shaft. The press tool is connected to the press tool via a block, and the press tool is moved in the slab width direction so as to suppress an unbalanced load on the press tool, and the rotary shaft is rotated to move the press tool in the slab width direction. A slab width reduction method that reciprocates to reduce the width of the slab. 13. A slab width reducing method using a slab width reducing device equipped with a press tool, comprising: supporting a supporting member at a central portion of a rotatable rotating shaft through an eccentric bearing, and both end portions of the rotating shaft. The press tool via a block, the outer ring of the eccentric bearing is rotated at a desired time, the rotary shaft is rotated, and the press tool is reciprocated in the slab width direction to reduce the width of the slab. Slab width reduction method.