CA2065801C - Tension roller leveler - Google Patents
Tension roller levelerInfo
- Publication number
- CA2065801C CA2065801C CA 2065801 CA2065801A CA2065801C CA 2065801 C CA2065801 C CA 2065801C CA 2065801 CA2065801 CA 2065801 CA 2065801 A CA2065801 A CA 2065801A CA 2065801 C CA2065801 C CA 2065801C
- Authority
- CA
- Canada
- Prior art keywords
- rolls
- work rolls
- backup
- rows
- tension
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
Classifications
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D1/00—Straightening, restoring form or removing local distortions of sheet metal or specific articles made therefrom; Stretching sheet metal combined with rolling
- B21D1/05—Stretching combined with rolling
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Straightening Metal Sheet-Like Bodies (AREA)
Abstract
ABSTRACT
A tension roller leveler which will produce neither abnormal noise nor flaws called chatter marks even in a high-speed treatment line. A plurality of work rolls are disposed on each of an upper frame and a lower frame. The upper frame and/or the lower frame can be regulated to adjust opening degrees of the work rolls in the inlet side and the outlet side for a strip. A
plurality of the work rolls are each supported indepen-dently over substantially the entire length by one set of backup rolls in two rows, and the backup rolls in two rows are arranged in a zig-zag pattern such that shaft support portions of one set of the backup rolls in two rows will not overlap with each other.
A tension roller leveler which will produce neither abnormal noise nor flaws called chatter marks even in a high-speed treatment line. A plurality of work rolls are disposed on each of an upper frame and a lower frame. The upper frame and/or the lower frame can be regulated to adjust opening degrees of the work rolls in the inlet side and the outlet side for a strip. A
plurality of the work rolls are each supported indepen-dently over substantially the entire length by one set of backup rolls in two rows, and the backup rolls in two rows are arranged in a zig-zag pattern such that shaft support portions of one set of the backup rolls in two rows will not overlap with each other.
Description
CA 0206~801 1999-01-14 BACKGROUND OF THE lNv~NllON
Field of the Invention The present invention relates to a tension roller leveler, and more particularly to a tension roller leveler capable of high-speed treatment.
Prior Art As an apparatus for reforming strip plates or sheets, there has been conventionally known, by way of example, a tension leveler in combination of extension rolls 20 and succeeding anti-cambering rolls 21 as shown in Fig. 4, or an apparatus including a roller leveler 22 which is located down-stream of such a tension leveler and comprises a number of work rolls 1', 2' respectively arranged on the upper and lower sides of a strip plate S.
In the former tension leveler, however, sensitivity is so high that a curl (longitudinal curvature~, particularly, is changed to a large extent upon a small amount of penetration, as shown in Fig. 6. This results in the necessity of delicate control and hence difficulties in achieving a stable levelling effect.
In the latter apparatus, sensitivity is not so sharp as the former tension leveler, as shown in Fig. 7, meaning that a stable levelling effect can be attained relatively easily in a control sense. Although the 2~6~
1 latter apparatus is superior to the former tension leveler from that point of view, the roller leveler 22 inherently requires not only a number of the work rolls 1', 2' having a relatively small diameter, but also backup rolls 3', 4' for respectively supporting those work rolls 1', 2'.
Because the backup rolls 3', 4' need to have sufficient strength to prevent the work rolls 1', 2' from bend, their diameter must be remarkably larger than that of the work rolls 1', 2'.
With the work rolls 1', 2' arranged closely to each other, therefore, an installation space enough to accommodate the backup rolls 3', 4' cannot be secured.
For that reason, it is usual that intermediate roll 3' or 4' is disposed in a strA~ling relation to plural (two) work rolls 1' or 2' so as to support the p}ural (two) work rolls by an int~ -~iAte roll. Alternatively, as disclosed in Japanese Patent Publication No. 48-44629, work rolls are independently supported by intermediate and backup roll arranged with a spacing therebetween in the lengthwise direction of the work rolls. More speci-fically, two rows of backup roll pairs are arranged at positions different from each other in the lengthwise direction of the work rolls such that one pair (group) of backup rolls support one work roll in an independent manner and the other pair (group) of backup rolls support another work roll, adjacent to the one work roll, in an independent manner.
2 0 ~
1 Generally, while the above-described tension leveler can relatively easily 1~ ve such deformation as edge waves and center buckles of treated materials (strip) through its levelling process, there occur a curl and a cross bow (gutter) by bending under tension, which residual curvatures remain even after levelling.
To remove those residual curvatures, therefore, the strip is sub~ected to a roller leveler under a low-tension or no-tension state.
Meanwhile, recent frequent use of those metal-lic strips, which are thin and hard material, has provided that the cor.~entional roll arrangement cannot satisfactorily remove such residual curvatures.
Where a strip plate has a thickness of 0.15 mm and a yield stress of 60 kgf/mm2, for example, a roller leveler requires work rolls having a diameter of about 16 mm. But, the roller leveler comprised of the so many and thin work rolls encounters difficulties in reforming at a high speed over 300 mpm. In high-speed lines, the dia-meter of each work roll is usually desirable to be in arange of about 30 to 40 mm from the s~Andpoints such as of maint~ining the roll accuracy and ensuring the roll's service life.
In the case of handling the thin and hard strip, however, the roller leveler comprised of the work rolls having a diameter in a range of about 30 to 40 mm cannot produce any plastic strain due to bending and thus cannot offer any effect in reforming residual curvature, 2~6~01 1 as will be seen from Fig. 8.
On the other hand, it is also known that even ; in the thin and hard strip, a plastic strain effect can be attained by applying a tension and also imposing a deformation due to bending under the tension, as will be seen from Fig. 9.
However, since the adjacent work rolls are contacted and coupled with each other via the backup roll as shown in Fig. 5 and a plastic elongation caused by that roller leveler produces a corresponding speed difference between portions of a strip held in contact with the inlet side work roll and the outlet side work roll, such a speed difference appears as a relative slip at any location in the roller leveler.
~he above relative slip due to a plastic elongation practically gives rise to few trouble in levelling at low-speed less than 300 mpm as practiced col.Yel~tionally and, especially, no problem in equipment where the reforming is carried out under a wet condition using a cleaning liquid or the like.
On the contrary, when the levelling is carried out in a high-speed range not less than 300 mpm, particu-larly, under a dry condition, the above relative slip due to a plastic elongation generates abnormal noise and causes damages, called chatter marks or scratch marks, on the strip, whereby the surface state of the strip is so ~reatly deteriorated as to impair its commercial value.
Fig. 10 shows the relationship between a line 2~5~0~
1 speed and a noise level in the roller leveler of the type that one backup roll is disposed in a straddling relation to a plurality of work rolls as shown in Fig. 5. As will be seen from Fig. 10, when the line speed is regulated to increase, abnormal noise due to resonation has occurred in a range exceeding 500 mpm. Conversely, when the line speed is regulated to decrease, abnormal noise due to resonation has occurred until lowering down to 400 mpm.
Note that although the occurrence of such abnormal noise is fluctuated to some extent depending on the size of the strip S, surface roughness and other properties, a similar tendency appears under any conditions.
Meanwhile, where work rolls are independently supported by two groups of backup rolls arranged with a spacing therebetween in the lengthwise direction of the work rolls as disclosed in the above-cited Japanese Patent Publication No. 48-44629, the foregoing problem of the relative slip due to a plastic elongation will not occur, but there produces a difference in press force between the portion where the work rolls are supported ~y the backup rolls and the portion where they are not supported by the backup rolls because the work rolls are simply supported by the backup rolls at different positions from each other in the lengthwise direction of the work rolls. Such a difference appears as line~r flaws on the surface of the strip, which impairs its commercial value.
CA 0206~801 1999-01-14 SUMMARY OF THE lNV~NllON
An object of the present invention is to provide a tension roller leveler by which stable curl and gutter reforming can be performed even in a high-speed range not less than 300 mpm without causing abnormal noise and vibration, while ensuring superior surface condition of a strip and final products with a high commercial value.
The present invention provides a tension roller leveler comprising an upper frame for mounting a plurality of upper work rolls thereon, a lower frame for mounting a plurality of lower work rolls thereon in opposite relation to said upper work rolls, bridle rolls disposed on the inlet side and the outlet side of a path line of a strip formed between the row of said upper work rolls and the row of said lower work rolls, and means for regulating the vertical position and the inclination of said upper frame relative to said lower frame, wherein said work rolls are each supported independently by one set of backup rolls in two rows over the substantially entire length thereof, and said backup rolls in two respective rows are arranged in a zig-zag pattern such that axial positions of shaft support portions of said backup rolls in two respective rows do not overlap with each other in view of the direction of said path line.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a schematic side view of an embodiment of the present invention.
Fig. 2 is a schematic plan view showing an arrangement of backup rolls in the present invention.
1 Fig. 3 is a side view of a roller leveler unit in the present invention.
Fig. 4 is a schematic side view of a conven tional tension leveler.
Fig. 5 is a schematic side view of a combina-tion of a conventional tension leveler and roller leveler.
Fig. 6 is a graph showing the relationship between an amount of penetration and an amount of residual curvature in the conventional tension leveler.
Fig. 7 is a graph showing the relationship between an amount of penetration and an amount of residual curvature in a combination of the conventional tension leveler and roller leveler.
Fig. 8 is a graph showing stress distribution when a strip plate is subjected to ben~ing under no tension.
Fig. 9 is a graph showing stress distribution when a strip plate is sub~ected to bending under ten~ion.
Fig. 10 is a graph showing the relationship between a line speed and a noise level in the conven-tional tension roller leveler.
DE~ATT~n DESCRIPTION OF PREFERRED EMBODIMENT
Hereinafter, an embodiment of the present invention will be described with reference to Figs. 1 to 3.
As shown in Fig. 1, upper work rolls la, lb and 2~8~ ~
1 lower work rolls 2a, 2b arranged on the upper and lower sides of a strip S are supported to an upper roll support 5 and a lower roll support 6 via backup rolls 3a, 3b and 4a, 4b, respectively.
The upper work rolls la, lb and the lower work rolls 2a, 2b are each separately supported by a pair of backup roll rows 3a, 3b and 4a, 4b, respectively. More specifically, as shown in Fig. 2, the backup roll rows 3a, 3b and 4a, 4b each comprise a plurality of rolls divided in the lengthwise direction of the work rolls la, lb, 2a, 2b and joined to each other via bearing members (not shown) disposed between every adjacent divided rolls such that the total length is substantially equal to the length of the work rolls la, lb, 2a, 2b. A pair of every two backup roll rows 3a, 3b or 4a, 4b separately ~up~o Ls each of the upper or lower work rolls la, lb or 2a, 2b in an independent manner, respectively.
Then, the pairs of two backup roll rows 3a, 3b, or 4a, 4b are arranged in a zig-zag pattern so that the bearing members of ones of the paired backup roll rows 3a or 3b, 4a or 4b will not overlap with the bearing members of the other counter-part backup rolls.
The upper roll support 5 and the lower roll support 6 are fixed to an upper frame 7 and a lower frame 8, respectively, either one of which (the lower frame 8 in this embodiment) is supported in a movable manner.
More specifically, the lower frame 8 is sup-ported at its lower surface by rods lla, llb which are CA 0206~801 1999-01-14 movable up and down by worm jacks lOa, lOb, respectively, carried on a base 9 whereby the lower frame 8 can be moved vertically and also tilted upon actuation of the worm jacks lOa, lOb. Accordingly, the work rolls la, lb, 2a, 2b can be controlled to desirably adjust an amount of closing and opening degrees (penetration) of the inlet side work roll and the outlet side work roll.
Denoted at 12a, 12b are rollers rotatably supported on the opposite sides of the lower frame 8. These rollers 12a, 12b are arranged to respectively rest on rails 13a, 13b when the lower frame 8 is descended, thereby allowing the lower frame 8 to move laterally (in a direction normal to the drawing sheet of Fig. 3).
Denoted at 14a, 14b (Figure 1) are bridle rolls respectively disposed on the inlet side and the outlet side of the work rolls la, lb, 2a, 2b for applying a predetermined tension to the strip S.
While the number of the work rolls la, lb, 2a, 2b is illustrated in this embodiment to be eleven in total, i.e., five for the upper work rolls plus six for the lower work rolls, the number of the work rolls may be of any desired one so long as the number of the upper work rolls is one more (or less) than that of the lower work rolls and the total number of both the work rolls is not less than five.
Further, it is desirable that the work rolls la, lb, 2a, 2b have their diameters which are so selected as to gradually increase from the inlet side toward the ... ....
- 2 ~
1 outlet side of the roller leveler for the purpose of gradually decreasing the curvature of bending of the strip S.
Operation of this embodiment will now be described.
The strip S is moved to pass through the work rolls la, lb and 2a, 2b while undergoing a predetermined tension from the bridle rolls 14a, 14b.
Accordingly, the strip S is repeatedly sub-jected to bending under the tension and thus deliveredfrom the inlet side toward the outlet side of the roller leveler while causing an elongation due to plastic strain, as explained above in connection with Fig. 9.
Therefore, the path length of the strip S is changed between the every two work rolls adjacent to each other. With the present invention, however, the adjacent work rolls are each separately supported by a corre-sponding pair of backup roll rows so that the individual work rolls la, lb, 2a, 2b are rotatable in an independent manner.
If the ad~acent work rolls are supported by a cc ~n single backup roll as with the prior art, those ad~acent work rolls are held in slide contact with each other and the rotation of one work roll is mechanically fed back to the other work roll, thereby causing both the work rolls to be forced to rotate at the same speed. For that reason, where an extension of thé strip S occurs be~ween both the work rolls, a relative slip is 2 ~
1 necessarily caused at any location in the roller leveler unless a speed difference corresponding to the amount of such an elongation is provided. In contrast, with the present invention, the adjacent work rolls are mechani-cally separated from each other and separately rotatable,resulting in no possibility of the occurrence of such a relative slip.
As described above, according to the present invention, since work rolls are each supported by one pair of backup rolls, even if a strip is repeatedly subjected to bending under tension in a tension leveler and thus extended so as to change the path length between the adjacent work rolls, the work rolls and the backup rolls can be rotated in an independent manner, whereby no relative slip is caused at any location in the tension leveler for absorbing an extension of the strip between the adjacent work rolls unlike the conventional tension roller leveler. Consequently, while the relative slip has produced abnormal noise due to abnormal resonation and has resulted in flaws called chatter marks in a conventional high-speed treatment line, any such abnor-mality will not occur in the present invention.
Further, although the backup rolls are each formed by joining a plurality of rolls to each other in the lengthwise direction of the work rolls, a pair of backup rolls are arranged in a zig-zag pattern such that the bearing members of the divided rolls of one backup roll will not overlap with the bearing members of the 2~6~
1 divided rolls of the other. Therefore, the joints between the divided rolls of each backup roll will not be transferred to the surface of the strip via the work roll to appear as linear flaws~ As a result, the tension roller leveler with superior stability in a high-speed range can be obtained.
Field of the Invention The present invention relates to a tension roller leveler, and more particularly to a tension roller leveler capable of high-speed treatment.
Prior Art As an apparatus for reforming strip plates or sheets, there has been conventionally known, by way of example, a tension leveler in combination of extension rolls 20 and succeeding anti-cambering rolls 21 as shown in Fig. 4, or an apparatus including a roller leveler 22 which is located down-stream of such a tension leveler and comprises a number of work rolls 1', 2' respectively arranged on the upper and lower sides of a strip plate S.
In the former tension leveler, however, sensitivity is so high that a curl (longitudinal curvature~, particularly, is changed to a large extent upon a small amount of penetration, as shown in Fig. 6. This results in the necessity of delicate control and hence difficulties in achieving a stable levelling effect.
In the latter apparatus, sensitivity is not so sharp as the former tension leveler, as shown in Fig. 7, meaning that a stable levelling effect can be attained relatively easily in a control sense. Although the 2~6~
1 latter apparatus is superior to the former tension leveler from that point of view, the roller leveler 22 inherently requires not only a number of the work rolls 1', 2' having a relatively small diameter, but also backup rolls 3', 4' for respectively supporting those work rolls 1', 2'.
Because the backup rolls 3', 4' need to have sufficient strength to prevent the work rolls 1', 2' from bend, their diameter must be remarkably larger than that of the work rolls 1', 2'.
With the work rolls 1', 2' arranged closely to each other, therefore, an installation space enough to accommodate the backup rolls 3', 4' cannot be secured.
For that reason, it is usual that intermediate roll 3' or 4' is disposed in a strA~ling relation to plural (two) work rolls 1' or 2' so as to support the p}ural (two) work rolls by an int~ -~iAte roll. Alternatively, as disclosed in Japanese Patent Publication No. 48-44629, work rolls are independently supported by intermediate and backup roll arranged with a spacing therebetween in the lengthwise direction of the work rolls. More speci-fically, two rows of backup roll pairs are arranged at positions different from each other in the lengthwise direction of the work rolls such that one pair (group) of backup rolls support one work roll in an independent manner and the other pair (group) of backup rolls support another work roll, adjacent to the one work roll, in an independent manner.
2 0 ~
1 Generally, while the above-described tension leveler can relatively easily 1~ ve such deformation as edge waves and center buckles of treated materials (strip) through its levelling process, there occur a curl and a cross bow (gutter) by bending under tension, which residual curvatures remain even after levelling.
To remove those residual curvatures, therefore, the strip is sub~ected to a roller leveler under a low-tension or no-tension state.
Meanwhile, recent frequent use of those metal-lic strips, which are thin and hard material, has provided that the cor.~entional roll arrangement cannot satisfactorily remove such residual curvatures.
Where a strip plate has a thickness of 0.15 mm and a yield stress of 60 kgf/mm2, for example, a roller leveler requires work rolls having a diameter of about 16 mm. But, the roller leveler comprised of the so many and thin work rolls encounters difficulties in reforming at a high speed over 300 mpm. In high-speed lines, the dia-meter of each work roll is usually desirable to be in arange of about 30 to 40 mm from the s~Andpoints such as of maint~ining the roll accuracy and ensuring the roll's service life.
In the case of handling the thin and hard strip, however, the roller leveler comprised of the work rolls having a diameter in a range of about 30 to 40 mm cannot produce any plastic strain due to bending and thus cannot offer any effect in reforming residual curvature, 2~6~01 1 as will be seen from Fig. 8.
On the other hand, it is also known that even ; in the thin and hard strip, a plastic strain effect can be attained by applying a tension and also imposing a deformation due to bending under the tension, as will be seen from Fig. 9.
However, since the adjacent work rolls are contacted and coupled with each other via the backup roll as shown in Fig. 5 and a plastic elongation caused by that roller leveler produces a corresponding speed difference between portions of a strip held in contact with the inlet side work roll and the outlet side work roll, such a speed difference appears as a relative slip at any location in the roller leveler.
~he above relative slip due to a plastic elongation practically gives rise to few trouble in levelling at low-speed less than 300 mpm as practiced col.Yel~tionally and, especially, no problem in equipment where the reforming is carried out under a wet condition using a cleaning liquid or the like.
On the contrary, when the levelling is carried out in a high-speed range not less than 300 mpm, particu-larly, under a dry condition, the above relative slip due to a plastic elongation generates abnormal noise and causes damages, called chatter marks or scratch marks, on the strip, whereby the surface state of the strip is so ~reatly deteriorated as to impair its commercial value.
Fig. 10 shows the relationship between a line 2~5~0~
1 speed and a noise level in the roller leveler of the type that one backup roll is disposed in a straddling relation to a plurality of work rolls as shown in Fig. 5. As will be seen from Fig. 10, when the line speed is regulated to increase, abnormal noise due to resonation has occurred in a range exceeding 500 mpm. Conversely, when the line speed is regulated to decrease, abnormal noise due to resonation has occurred until lowering down to 400 mpm.
Note that although the occurrence of such abnormal noise is fluctuated to some extent depending on the size of the strip S, surface roughness and other properties, a similar tendency appears under any conditions.
Meanwhile, where work rolls are independently supported by two groups of backup rolls arranged with a spacing therebetween in the lengthwise direction of the work rolls as disclosed in the above-cited Japanese Patent Publication No. 48-44629, the foregoing problem of the relative slip due to a plastic elongation will not occur, but there produces a difference in press force between the portion where the work rolls are supported ~y the backup rolls and the portion where they are not supported by the backup rolls because the work rolls are simply supported by the backup rolls at different positions from each other in the lengthwise direction of the work rolls. Such a difference appears as line~r flaws on the surface of the strip, which impairs its commercial value.
CA 0206~801 1999-01-14 SUMMARY OF THE lNV~NllON
An object of the present invention is to provide a tension roller leveler by which stable curl and gutter reforming can be performed even in a high-speed range not less than 300 mpm without causing abnormal noise and vibration, while ensuring superior surface condition of a strip and final products with a high commercial value.
The present invention provides a tension roller leveler comprising an upper frame for mounting a plurality of upper work rolls thereon, a lower frame for mounting a plurality of lower work rolls thereon in opposite relation to said upper work rolls, bridle rolls disposed on the inlet side and the outlet side of a path line of a strip formed between the row of said upper work rolls and the row of said lower work rolls, and means for regulating the vertical position and the inclination of said upper frame relative to said lower frame, wherein said work rolls are each supported independently by one set of backup rolls in two rows over the substantially entire length thereof, and said backup rolls in two respective rows are arranged in a zig-zag pattern such that axial positions of shaft support portions of said backup rolls in two respective rows do not overlap with each other in view of the direction of said path line.
BRIEF DESCRIPTION OF THE DRAWINGS
Fig. 1 is a schematic side view of an embodiment of the present invention.
Fig. 2 is a schematic plan view showing an arrangement of backup rolls in the present invention.
1 Fig. 3 is a side view of a roller leveler unit in the present invention.
Fig. 4 is a schematic side view of a conven tional tension leveler.
Fig. 5 is a schematic side view of a combina-tion of a conventional tension leveler and roller leveler.
Fig. 6 is a graph showing the relationship between an amount of penetration and an amount of residual curvature in the conventional tension leveler.
Fig. 7 is a graph showing the relationship between an amount of penetration and an amount of residual curvature in a combination of the conventional tension leveler and roller leveler.
Fig. 8 is a graph showing stress distribution when a strip plate is subjected to ben~ing under no tension.
Fig. 9 is a graph showing stress distribution when a strip plate is sub~ected to bending under ten~ion.
Fig. 10 is a graph showing the relationship between a line speed and a noise level in the conven-tional tension roller leveler.
DE~ATT~n DESCRIPTION OF PREFERRED EMBODIMENT
Hereinafter, an embodiment of the present invention will be described with reference to Figs. 1 to 3.
As shown in Fig. 1, upper work rolls la, lb and 2~8~ ~
1 lower work rolls 2a, 2b arranged on the upper and lower sides of a strip S are supported to an upper roll support 5 and a lower roll support 6 via backup rolls 3a, 3b and 4a, 4b, respectively.
The upper work rolls la, lb and the lower work rolls 2a, 2b are each separately supported by a pair of backup roll rows 3a, 3b and 4a, 4b, respectively. More specifically, as shown in Fig. 2, the backup roll rows 3a, 3b and 4a, 4b each comprise a plurality of rolls divided in the lengthwise direction of the work rolls la, lb, 2a, 2b and joined to each other via bearing members (not shown) disposed between every adjacent divided rolls such that the total length is substantially equal to the length of the work rolls la, lb, 2a, 2b. A pair of every two backup roll rows 3a, 3b or 4a, 4b separately ~up~o Ls each of the upper or lower work rolls la, lb or 2a, 2b in an independent manner, respectively.
Then, the pairs of two backup roll rows 3a, 3b, or 4a, 4b are arranged in a zig-zag pattern so that the bearing members of ones of the paired backup roll rows 3a or 3b, 4a or 4b will not overlap with the bearing members of the other counter-part backup rolls.
The upper roll support 5 and the lower roll support 6 are fixed to an upper frame 7 and a lower frame 8, respectively, either one of which (the lower frame 8 in this embodiment) is supported in a movable manner.
More specifically, the lower frame 8 is sup-ported at its lower surface by rods lla, llb which are CA 0206~801 1999-01-14 movable up and down by worm jacks lOa, lOb, respectively, carried on a base 9 whereby the lower frame 8 can be moved vertically and also tilted upon actuation of the worm jacks lOa, lOb. Accordingly, the work rolls la, lb, 2a, 2b can be controlled to desirably adjust an amount of closing and opening degrees (penetration) of the inlet side work roll and the outlet side work roll.
Denoted at 12a, 12b are rollers rotatably supported on the opposite sides of the lower frame 8. These rollers 12a, 12b are arranged to respectively rest on rails 13a, 13b when the lower frame 8 is descended, thereby allowing the lower frame 8 to move laterally (in a direction normal to the drawing sheet of Fig. 3).
Denoted at 14a, 14b (Figure 1) are bridle rolls respectively disposed on the inlet side and the outlet side of the work rolls la, lb, 2a, 2b for applying a predetermined tension to the strip S.
While the number of the work rolls la, lb, 2a, 2b is illustrated in this embodiment to be eleven in total, i.e., five for the upper work rolls plus six for the lower work rolls, the number of the work rolls may be of any desired one so long as the number of the upper work rolls is one more (or less) than that of the lower work rolls and the total number of both the work rolls is not less than five.
Further, it is desirable that the work rolls la, lb, 2a, 2b have their diameters which are so selected as to gradually increase from the inlet side toward the ... ....
- 2 ~
1 outlet side of the roller leveler for the purpose of gradually decreasing the curvature of bending of the strip S.
Operation of this embodiment will now be described.
The strip S is moved to pass through the work rolls la, lb and 2a, 2b while undergoing a predetermined tension from the bridle rolls 14a, 14b.
Accordingly, the strip S is repeatedly sub-jected to bending under the tension and thus deliveredfrom the inlet side toward the outlet side of the roller leveler while causing an elongation due to plastic strain, as explained above in connection with Fig. 9.
Therefore, the path length of the strip S is changed between the every two work rolls adjacent to each other. With the present invention, however, the adjacent work rolls are each separately supported by a corre-sponding pair of backup roll rows so that the individual work rolls la, lb, 2a, 2b are rotatable in an independent manner.
If the ad~acent work rolls are supported by a cc ~n single backup roll as with the prior art, those ad~acent work rolls are held in slide contact with each other and the rotation of one work roll is mechanically fed back to the other work roll, thereby causing both the work rolls to be forced to rotate at the same speed. For that reason, where an extension of thé strip S occurs be~ween both the work rolls, a relative slip is 2 ~
1 necessarily caused at any location in the roller leveler unless a speed difference corresponding to the amount of such an elongation is provided. In contrast, with the present invention, the adjacent work rolls are mechani-cally separated from each other and separately rotatable,resulting in no possibility of the occurrence of such a relative slip.
As described above, according to the present invention, since work rolls are each supported by one pair of backup rolls, even if a strip is repeatedly subjected to bending under tension in a tension leveler and thus extended so as to change the path length between the adjacent work rolls, the work rolls and the backup rolls can be rotated in an independent manner, whereby no relative slip is caused at any location in the tension leveler for absorbing an extension of the strip between the adjacent work rolls unlike the conventional tension roller leveler. Consequently, while the relative slip has produced abnormal noise due to abnormal resonation and has resulted in flaws called chatter marks in a conventional high-speed treatment line, any such abnor-mality will not occur in the present invention.
Further, although the backup rolls are each formed by joining a plurality of rolls to each other in the lengthwise direction of the work rolls, a pair of backup rolls are arranged in a zig-zag pattern such that the bearing members of the divided rolls of one backup roll will not overlap with the bearing members of the 2~6~
1 divided rolls of the other. Therefore, the joints between the divided rolls of each backup roll will not be transferred to the surface of the strip via the work roll to appear as linear flaws~ As a result, the tension roller leveler with superior stability in a high-speed range can be obtained.
Claims (2)
1. A tension roller leveler comprising an upper frame for mounting a plurality of upper work rolls thereon, a lower frame for mounting a plurality of lower work rolls thereon in opposite relation to said upper work rolls, bridle rolls disposed on the inlet side and the outlet side of a path line of a strip formed between the row of said upper work rolls and the row of said lower work rolls, and means for regulating the vertical position and the inclination of said upper frame relative to said lower frame, wherein said work rolls are each supported independently by one set of backup rolls in two rows over the substantially entire length thereof, and said backup rolls in two respective rows are arranged in a zig-zag pattern such that axial positions of shaft support portions of said backup rolls in two respective rows do not overlap with each other in view of the direction of said path line.
2. A tension roller leveler according to claim 1, wherein said tension leveler has a reform speed not lower than 350 mpm.
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP10651591A JPH0576934A (en) | 1991-04-12 | 1991-04-12 | Tension roller leveler |
| JP03-106515 | 1991-04-12 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CA2065801A1 CA2065801A1 (en) | 1992-10-13 |
| CA2065801C true CA2065801C (en) | 1999-08-03 |
Family
ID=14435554
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CA 2065801 Expired - Lifetime CA2065801C (en) | 1991-04-12 | 1992-04-10 | Tension roller leveler |
Country Status (4)
| Country | Link |
|---|---|
| EP (1) | EP0508475B1 (en) |
| JP (1) | JPH0576934A (en) |
| CA (1) | CA2065801C (en) |
| DE (1) | DE69201395T2 (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4323385C1 (en) * | 1993-07-13 | 1995-01-19 | Bwg Bergwerk Walzwerk | Method for eliminating transverse curvatures in metal strips, in particular thin metal strips up to 2.0 mm thick |
| DE10124836C5 (en) † | 2001-05-22 | 2007-07-19 | Bwg Bergwerk- Und Walzwerk-Maschinenbau Gmbh | Method for eliminating transverse curvatures in a metal strip |
| EP2475473B1 (en) | 2009-09-09 | 2012-12-26 | Siemens Vai Metals Technologies SAS | Levelling machine with multiple rollers |
| JP6199892B2 (en) * | 2012-11-29 | 2017-09-20 | スチールプランテック株式会社 | Leveler equipment and plate straightening method |
| DE102016106208A1 (en) | 2016-04-05 | 2017-10-05 | Bwg Bergwerk- Und Walzwerk-Maschinenbau Gmbh | Method for stretch bending of a strip |
| CN110385385B (en) * | 2018-04-23 | 2024-04-26 | 无锡市夏音电器有限公司 | Straightening machine for refrigerator wire production and processing |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| AT314453B (en) * | 1971-07-09 | 1974-04-10 | Bwg Bergwerk Und Walzwek Masch | Method and device for reducing sheet metal strips in strip lines |
| JPS5118016B2 (en) | 1971-10-08 | 1976-06-07 | ||
| JPS5214568A (en) * | 1975-07-26 | 1977-02-03 | Ube Industries | Tension roller leveller |
| DE2536582C3 (en) * | 1975-08-16 | 1979-08-09 | Bwg Bergwerk- Und Walzwerk-Maschinenbau Gmbh, 4100 Duisburg | Interchangeable crossbeam |
| DE3234160C2 (en) * | 1982-09-15 | 1986-10-23 | Bwg Bergwerk- Und Walzwerk-Maschinenbau Gmbh, 4100 Duisburg | Method and hot strip mill for producing thin metal strip, in particular metal wide strip, from hot strip |
| JPH0220618A (en) * | 1988-07-06 | 1990-01-24 | Hitachi Ltd | Roller leveler |
-
1991
- 1991-04-12 JP JP10651591A patent/JPH0576934A/en active Pending
-
1992
- 1992-04-10 CA CA 2065801 patent/CA2065801C/en not_active Expired - Lifetime
- 1992-04-10 DE DE1992601395 patent/DE69201395T2/en not_active Revoked
- 1992-04-10 EP EP19920106289 patent/EP0508475B1/en not_active Revoked
Also Published As
| Publication number | Publication date |
|---|---|
| DE69201395D1 (en) | 1995-03-23 |
| JPH0576934A (en) | 1993-03-30 |
| EP0508475A3 (en) | 1992-12-02 |
| EP0508475B1 (en) | 1995-02-15 |
| CA2065801A1 (en) | 1992-10-13 |
| EP0508475A2 (en) | 1992-10-14 |
| DE69201395T2 (en) | 1995-08-03 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| EEER | Examination request | ||
| MKEX | Expiry |