EP0509136B1

EP0509136B1 - Rolling roller and rolling mill

Info

Publication number: EP0509136B1
Application number: EP91117673A
Authority: EP
Inventors: Takashi Nagamine; Jun Furukawa; Masayoshi Matsuda; Misao Makinohara; Hiroatsu Asari; Masatoshi Fukuda; Ryoichi Yamase
Original assignee: Kawasaki Heavy Industries Ltd; Kawasaki Jukogyo KK; NKK Corp; Nippon Kokan Ltd
Current assignee: Kawasaki Heavy Industries Ltd; JFE Engineering Corp; Kawasaki Motors Ltd
Priority date: 1991-04-17
Filing date: 1991-10-16
Publication date: 1995-01-11
Anticipated expiration: 2011-10-16
Also published as: KR940002747B1; DE69106692T2; KR920019435A; EP0509136A1; DE69106692D1

Description

The present invention relates to a rolling roller according to the precharacterizing part of claim 1. Such rollers can adjust the roll width, which means a gap of the shoulder of the rolling wheel portion, so as to roll flat steel. The invention also relates to a rolling mill provided with such rolling roller.
Rolling mills for rolling steel have a horizontal roller that comprises a roller shaft and sleeves that engage with the outer side of the roller shaft. Such a configuration makes it possible to roll H-section steels that have different web heights since the position of the sleeve in the axial direction can be changed to alter the roll width, which means the gap between the shoulder of the rolling wheel provided to the sleeve and the shoulder of the rolling wheel provided to the roll shaft, or the gap between the shoulders of each of the rolling wheels of two sleeves.
One example of such a conventional rolling mill is disclosed in JP-A-61-17310. In this example, the adjustment of the position of the sleeve in the direction of the shaft requires means for moving the sleeve and fix it with respect to the roll. This rolling mill is provided with hydraulic blocks (so-called hydraulic cylinders) to a distal end portions of the roll shaft and these blocks are also linked to the sleeves on the roller shaft to move and fix it.
JP-A-62-156007 discloses a rolling roller of the type defined in the precharacterizing part of claim 1, and the roller has an adjustment screw and a rotational drive mechanism built into the rolling roller so that the position of the sleeve in the axial direction can be adjusted by turning the screw to feed the sleeve.
However, the conventional rolling mill disclosed in JP-A-61-17310 has the problems described under a) and b) below.

a) It is necessary for a hydraulic block that adjusts the position of the sleeve to be large and have a high output and to be provided on the rolling roller. During rolling, a significant rolling reaction, which can reach the order of several tons when large H-sections are being rolled, acting from the material being rolled and in the direction of the shaft, in other words, the direction of thrust is applied to the sleeve and this force is a force that moves the sleeve with respect to the roller shaft. A significant output to resist this force is therefore necessary.
b) In addition to the rolling roller which is assembled to the rolling mill and used therefor, it is also necessary to also include a spare rolling roller. When there is wear and the like of the roller surface, the rolling roller that is assembled to the roller shaft and the sleeve and other parts must be taken from the fixing housing as it is, the rolling mill placed in standby and another rolling roller brought in to replace it. It is necessary from the point of view of productivity that this replacement work should be performed quickly and so a hydraulic block provided on the roller shaft must be assembled beforehand at a required place. This means that large-scale hydraulic blocks are necessary in large numbers and this requires additional cost, and there is also a considerable maintenance load as the replacement work becomes complex and involves much time.
On the other hand, when there is a position adjustment screw between the sleeve and the roll shaft, it is necesary to have a complex mechanism in order to drive the screw. That mechanism must also be incorporated into the rolling roller itself and so must also be exchanged when the rolling roller is exchanged and this also involves a significant cost and maintenance load.

The object of the present invention is to provide a rolling roller that can have the position of the sleeve adjusted by a simple structure that facilitates replacement; also a rolling mill that can have the roll width adjusted on line using such a rolling roller is provided.
The rolling roller of the present invention is defined in claim 1. The hydraulic fluid supply paths are, for example, formed via an internal portion of a roller shaft or sleeve and from a distal end.
The rolling roller described above can be fixed so that exchange of the rolling wheel is possible with respect to one sleeve and another portion such as another sleeve or roller shaft.
The rolling mill of the present invention is defined in claim 3. It includes means assembled into a housing via said chocks and which connects said hydraulic fluid supply means, such as piping that is connected to a pump or the like, to the supply paths and that adjusts a position of engagement in the axial direction of a sleeve and a roll shaft with respect to at least one of the chocks. This adjustment means can be any means as long as it is mounted to the fixed housing or the like, to a structural object on the same floor, or to the facility installation platform, and as long as it exerts a force in with respect to the chock, in the direction of the shaft of the rolling roller.
With the rolling roller of the present invention, the tightening force at the place of fitting and engagement tightly fixes the sleeve, without the use of any special mechanisms, with respect to the roller shaft. When the roller is in this status, the roller wheels respectively provided at the two places on the one sleeve and the roller shaft, that is, the roller wheels respectively provided at the two places of the one sleeve and another sleeve perform the rolling of the formed steel.
The adjustment of the roll width, which means the gap between the shoulder of the roller wheels at the two places described above, in such a rolling roller can be performed by applying hydraulic pressure to the place of engagement via hydraulic fluid supply paths such as through the implementation of oil injection, and then applying relative movement between the sleeve and the roller shaft at that place. If a hydraulic pressure (so-called surface pressure) that exceeds the tightening force is applied to the entire region of the place of engagement described above, and if that place is not the inner side of the roller wheel, then the internal diameter of the sleeve is effectively increased because of Pascal's Principle for fluid pressure. In this status, position adjustment of the sleeve with respect to the roller shaft can be easily performed by one of many means such as a special drive mechanism or a simple fitting or jig of the manual operation type so that it is possible to adjust the roller width even inside the rolling mill while on line, or in the on line status when the rolling roller is taken from the rolling mill. When the changing of the roller width is completed, the fluid pressure can be reduced and the sleeve engaged with the roller shaft and fixed. Moreover, if the place for engagement is on the inner side of the roller wheel, then the same portion of thickness can prevent the expansion of the inner diameter of the sleeve, so that during hot rolling, the temperature conditions of that portion are considered whenever roll width adjustment has to be performed. For this reason, a place on the inner side of the rolling wheel should be avoided as the place for engagement.
On the basis of performing simple adjustment of the rolling width using one of a number of simple methods, this rolling roller does not require the provision of a drive mechanism such as a sleeve or the like, to the rolling roller itself and so the structure of the portion that is the object of exchange is simplified and there is the advantage of exchange operation being facilitated.
In addition, the rolling roller can be exchanged by independently exchanging the roller wheel that is easily worn because it is in contact with the material of the object to be rolled, and therefore has a long life as a rolling roller. This is to say that if only the rolling wheel that is easily worn, deformed or cracked is exchanged, the other portions that have relatively little wear will able to be used for a long period.
Furthermore, the rolling mill of the present invention is provided with the rolling wheel described above as the flat roller, and is also provided with hydraulic fluid supply means to between the roller shaft and the sleeve, which is the place of tightening and engagement, and means for adjusting the position of engagement of the sleeve via the chock and so the adjustment of the position of the roller width is simple and the maintenability of the rolling roller is also simplified. More specifically, the adjustment of the roller width can be performed by supplying hydraulic fluid from the supply means described above and via the hydraulic fluid supply paths to the place of tightening and engagement and by using the adjustment means described above to change the position between the roller shaft and the sleeve via the chock. The chock, that is, the bearing box supports the rolling roller via the bearings and so the roller width adjustment is can be performed, for example, while the rolling roller is rotating. In addition, the engagement position adjustment means is not provided to the roller itself, it is possible to remove only the rolling roller itself without removing the adjustment means, and opening the connection between the rolling roller and the hydraulic fluid supply means is simple and so other than the adjustment means described above and the fluid supply means described above, the rolling roller of the present invention can have maintenance, including demounting and mounting, operation performed in an effective status with respect to the cost and the workability.
Moreover, with this rolling mill, the engagement position adjustment means for between the sleeve and the roller shaft is provided to a portion other than the rolling roller as described above and so the speed and the performance for adjusting the roller width can be easily raised. When there is means provided to the rolling roller itself as is conventionally done, the limitations of size and weight result in the means having an insufficient performance, and hamper the fast adjustment of the roll width.

FIG. 1 is a horizontal sectional drawing taken along the rolling roller and shows one portion of a rolling mill according to a first embodiment of the present invention;
FIG. 2 is an enlarged drawing of the portion indicated by A in FIG. 1;
FIG. 3 is a horizontal sectional drawing taken along the rolling roller as for FIG. 1, and shows one portion of a rolling mill according to a second embodiment of the present invention; and
FIG. 4 is a horizontal sectional drawing taken along the rolling roller as for FIG. 1, and shows one portion of a rolling mill according to a third embodiment of the present invention.

A preferred embodiment of the present invention will become understood from the following detailed description referring to the accompanying drawings. FIG. 1 is a horizontal sectional drawing taken along the rolling roller and shows one portion of a rolling mill according to a first embodiment of the present invention, and FIG. 2 is an enlarged drawing of the portion indicated by A in FIG. 1. This rolling mill is a universal mill for rolling H-section steel and, in addition to the roller 1 shown in the figure, has another rolling roller (not shown in the figure) and which is parallel to the roller 1, while two vertical rollers (also not shown in the figure) are vertically provided at each end of the shaft. The gap W1 between the shoulders 11a and 21a on each of the outer sides of the rolling wheels 11 and 21 in the center of the drawing is the rolling width, and becomes the height of the web (inner piece) of the H-section steel that is rolled.
The rolling roller 1 engages with the roller shaft 10 and the sleeve 20 as shown in FIG. 1. and so is supported by the chocks 30 and 40 (so-called the bearing box) at two places provided to the two outer sides of the rolling wheels 11 and 21. Engaging the roller shaft 10 and the sleeve 20 allows both to be slid to change the dimension of the gap W1, and enables various types of H-section steel having different web heights to be roller without exchanging the rolling roller 1. Moreover, the transmission of the rolling torque from the roller shaft 10 to the sleeve 20 is such that there is a sufficient frictional force due to the tightening between the two so that there is no relative movement between the two. In this example, the transmission of the rolling torque is made more definite by the gear 12 between the roller shaft 10 and the sleeve 20 although the two can be connected by a spline. In addition, the rolling wheels 11 and 21 are made into a single unit by being respectively welded to the outer circumference of the roller shaft 10 and the sleeve 20. The distal end portion 13 of the roller shaft 10 is the connection portion to the rotational drive source (not shown in the figure) and that comprises a motor and the like.
The chocks 30 and 40 are inserted into the main body between the fixed housing 101 of the rolling mill so that they do not rotate, but can move in the direction of the shaft, and each support the roller 1 via the bearings 31 and 41 on their inner sides respectively, so that the roller 1 is freely rotatable. Moreover, the chock 30 is directly supported on the outer circumference of the sleeve 20 and the chock 40 supports the roller shaft 10, while each of the chocks 30 and 40 sufficiently supports the thrust load as well as the radial load.
The gap W1 described above is freely set, that is, the sleeve 20 can be moved and fixed with respect to the roller shaft 10, and so the rolling mill is made to have the mechanisms 1) and 2) described below.

1) To the roller shaft 10 and one portion of the sleeve 20 is provided a place of engagement having a tightening fitting and there is oil injection between the engaging surfaces at that place. In this example, the tightening fitting is the portion on the inner side of the chock 30, and an intermediate tightening fitting having only slight tightening or engagement with a gap still remaining is on the inner side of the rolling wheel 21. To the surface of the roller shaft 10 at the place of the tightening fitting is provided a ring-shaped pressure space 55, and to the inner portion of the roller shaft 10 are formed the hydraulic fluid supply paths 53 and 54 so that the space 55 has an opening. Connected via a rotary joint 52 to the distal end portion of this supply path 53 is a hydraulic pipe 51 connected in turn to a hydraulic fluid source (not shown in the figure), as the hydraulic fluid supply means 50.
Because the the sleeve 20 is fixed to on the roller shaft 10 by a suitable tightening force, even if a large rolling reaction, which means thrust force acting in the direction to approach the shoulders 11a and 21a, acts against the rolling wheels 11 and 21 during rolling, there is no slippage between the roller shaft 10 and the sleeve 20. On the other hand, when the supply means 50 described above performs oil injection for between the engaging surfaces the engagement between the roller shaft 10 and the sleeve 20 is released and the relative movement of both in the direction of the shaft is enabled. At this time, the outer diameter of the sleeve 20 is increased but the amount of this enlargement is only slight and presents no problem for containment within the engagement gap with respect to the bearing 31. Moreover, the rolling reaction force during rolling is practically all cancelled in the direction opposing the direction of the shaft which means the direction to the left and right in FIG. 1 and so the thrust load that is applied to the chocks 30 and 40 and to the engagement position adjustment means 110 and 120 to be described later is extremely small when compared to the absolute value of the rolling reaction force.
2) The engagement position adjustment means 110 and 120 that are configured so as to freely contract and elongate are respectively mounted to the fixed housing 101 and engage so as to be freely mountable and demountable with respect to each pair of brackets 32 and 42 and the chocks 30 and 40. The engagement position adjustment means 110 on the side of the chock 30 is configured from a base portion 111 that is fixed to the fixed housing 101, a distal end portion 112 that engages with the bracket 32, a hydraulic cylinder 113 disposed between the two and is provided further to the outer side, which means the side of the reaction shaft, than the chock 30. To the distal end portion 112 is a keeper plate 112a that engages with the concave portion 32a of the bracket 32 and which is mounted to the contracting and elongating end of the hydraulic cylinder 112b. The adjustment means 120 on the side of the other chock 40 is configured in the same manner as the chock 30, and comprises a base portion 121, a distal end portion 122, and a hydraulic cylinder 123 and the like, and to the distal end portion 122 are provided a hydraulic cylinder 122b and a keeper plate 122a that can engage with the concave portion 42a of the bracket 42. Moreover, the hydraulic cylinders 113 and 123 can be any type of actuator, such as a solenoid type of a screw mechanism, as long as they can elongate and contract but the output must be greatly smaller than the rolling reaction force for the reason described above.

When oil injection is performed by 1) above, the cylinder 113 of the adjustment means 110 contracts from the status shown in FIG. 1 and the sleeve 20 moves in the direction of the roller shaft 10 along with the chock 30, and when the cylinder 123 of the adjustment means 120 contracts, the roller shaft 10 moves along with the chock 40.
The engagement position adjustment means 110 and 120 have their distal end portions 112 and 122 can be mounted and dismounted to and from their respective brackets and when each of the cylinders 112b and 122b are contracted, the keeper plates 112a and 122a are separated from the brackets 32 and 42 and retreat in the outwards direction. In this retreated status, the separation between the piping 51 and the joint 52 for example, enables the rolling roller 1 that is to be exchanged (that is, the sleeve 20 and the rolling wheels 11 and 21 assembled to the rolling roller 10) to be taken from the fixed housing 101 along with the chocks 30 and 40, and independently from the engagement position adjustment means 110 and 120. When this is done, the engagement position adjustment means 110 and 120 are not removed and remain in fixed the housing 101 and the distal end portions 112 and 122 engage with respect to the chock 30, 40 of the rolling roller 1 that is newly placed in. This is to say that in this rolling mill, the rolling roller 1 can be exchanged without any ancillary mechanisms to move it between the roller shaft 10 and the sleeve 20 and to fix it. In accordance with necessity, the chocks 30 and 40 are demounted and mounted with respect to the rolling roller 1 that has been taken from the rolling mill but this work entails no particular difficulty and is performed in the conventional manner.
In the rolling mill configured as described in 1) and 2) above, the gaps W1 and W2 of the rolling wheels 11 and 21 (the shoulders 11a and 21a) of the rolling roller 1 is as described below.

(1) As shown in FIG. 1, in the status where each of the distal end portions 112 and 122 ( keeper plates 112a and 122a) of the engagement position adjustment means 110 and 120 are respectively engaged with the brackets 32 and 42, oil is injected from the hydraulic fluid supply means 50 to inside the space 55 and via the supply paths 53 and 54 that are formed inside the roller shaft 10.
(2) Each of the cylinders 113 and 123 of the engagement position adjustment means 110 and 120 are respectively tightened by

$(W1 - W2)/2$

so that the sleeve 20 in FIG. 1 moves to the left and so that the roller shaft 10 moves to the right to make the gap between the roller wheels 11 and 21 equal to W2.
(3) The cylinders 113 and 123 are stopped and the oil injection stopped (to lower the hydraulic pressure) and the roller shaft 10 and the sleeve 20 are again returned to their tightened status and fixed.

In this first embodiment described above, the engagement position adjustment means 110 and 120 are provided to the fixed housing 101 for either of both of the chocks 30 and 40 but an engagement position adjustment means 110, 120 that has such a contraction and elongation function can perform change of the gap W1 by being provided to either only the chock 30 or the chock 40. FIG. 3 and FIG. 4 show rolling mills of second and third embodiments, and that are provided with an adjustment mechanism for only the gap between the fixed housing and the chock on one side.
First, in the rolling mill shown in FIG. 3 (second embodiment), the adjustment mechanism 110 is provided only with respect to the chock 30 that directly supports the sleeve 20, and there is no contraction and elongation function with respect to the chock 40 on the side that supports the roller shaft 10, and there is only a stopper means 130 fixed to the fixed housing 101 so as to determine the reference position of the chock 40. The stopper means 130 is provided with a hydraulic housing 132b that has mounted to it a keeper plate 132 to the end that contracts and elongates, and has only the function of the distal end portion 122 of the adjustment means 120 described above. More specifically, it is possible for the chock 40 and the concave portion 43a of the pair of brackets 43 to engage the keeper plate 132a if the cylinder 132b is elongated, and for the plate 132a to be separated from the bracket 43 and retreat to the outer side when the cylinder 132b is contracted.
In the rolling mill shown in FIG. 3, the procedure for changing the gap W1 between the rolling wheels 11 and 21 is as described below.

(1) Each of the keeper plates 112a and 132a of the engagement position adjustment means 110 and the stopper means 130 are respectively engaged with the brackets 32 and 42.
(2) Oil is injected to between the engaging surfaces of the roller shaft 10 and the sleeve 20, via the supply path 53.
(3) The cylinder 113 of the engagement position adjustment means 110 is contracted and sliding the sleeve 20 along with the chock 30 in the direction to the left makes the gap between the rolling wheels 11 and 21 to the required gap W2.
(4) The oil injection is stopped once the cylinder 113 has come to a stop.
(5) By moving only the sleeve 20, the centers of the rolling wheels 11 and 21 are in the displaced status and so when the procedure (4) above has been completed, the plate 132a of the stopper means 130 is separated from the bracket 43 and the cylinder 113 is returned slightly by half of the amount of elongation and contraction of the procedure (3) above and centering performed.

During rolling, the plate 132a of the stopper means 130 does not engage with the concave portion 43a of the bracket 43 and so the stopping of the movement in the direction of the shaft of the rolling roller 1 and with respect to the fixed housing 101 is due to the force of the adjustment manes 110. As has been described above, the force of the rolling reaction force that moves the absolute position of the rolling roller 1 is small and so no problems occur because of it. When the gap W2 is changed further, the status under the procedure (1) above occurs again when the roller 1 is moved by the adjustment means and the procedures (2) above and later are then performed.
Moreover, depending upon the facility arrangement before and after the rolling mill, there are cases where it is not necessary to perform centering with the center of the rolling line and the center of the roll width (the gap W1 or W2 of the rolling wheels 11 and 21) and in these cases it is not necessary to perform the procedure (5) described above.
On the other hand, with the rolling mill of the third embodiment shown in FIG. 4, there is an engagement position adjustment means 120 provided with respect to only the chock 40 on the side of the roller shaft 10 and stopper means 140 that has the same structure and function as the stopper means 130 described above is fixed to the fixed housing 101 with respect to the other chock 30. In this rolling mill as well, it is possible to change the gap W1 of the rolling wheels 11 and 21 by a means that is the same as that of the second embodiment described above. However, the gap W1 is adjusted to the gap W2, for example by moving the roller wheel 10 and not the sleeve 20 and so it is necessary for the procedures (1) to (5) above to be suitably reordered.
In addition to the embodiments described above, it is also possible to have many modifications for the rolling roll and the rolling mill of the present invention. For example, two sleeves can engage on the rolling wheel and rolling wheels can be respectively provided to each of the sleeves. In this case, if there are fluid supply paths and fluid supply means are configured so that the hydraulic pressure is respectively and separately applied to the places for tightening and engagement between the roller shaft and each of the sleeves, then it is possible to adjust the engagement position, that is, the gap (roller width) of the roller wheel in exactly the same manner as has been described above. The roller wheel portion can be fixed with respect to the roller wheel and the sleeve as shown in FIG. 1 (for the first embodiment) so that it can be exchanged but it is also possible for it to be a unit as in the cases shown in FIG. 3 (for the second embodiment) and FIG. 4 (for the third embodiment).
The rolling roller of the present invention has simple adjustment of the roller width and also does not require a drive mechanism (engagement position adjustment means) to be provided to the rolling roller itself for adjustment, and therefore has a simple structure. Accordingly, it is possible to eliminate mechanisms for spare rollers and for the cost to be lowered, along with other advantages such as simplified maintenance and exchange operations for the rolling rollers.
In addition, the rolling roller can be made to have an extended life by exchanging only the rolling wheel in accordance with the conditions of wear. This is an important factor in reduce the costs involved with rolling.
The rolling mill of the present invention produces the following effects.

1) With respect to adjustment of the roller width, it is not necessary to have high output means as the means for performing movement and fixing between the rolling shaft and the sleeve.
2) The adjustment of the roller width can be performed on line while the rolling roller is rotating. Accordingly, it is possible to realize reverse rolling where the rolling width is changed during passes after one pass has been completed and before the next pass has started.
3) The engagement position adjustment means is a portion other than the rolling roller and can be easily made to have a high performance, thereby facilitating fast adjustment of the roller width. This, along with the effect 2) described above, improves the rolling efficiency and, in particular when hot rolling processes are being performed, means that rolling can be performed while the temperature drop of the material being rolled is still small.
4) Unlike conventional rolling mills where the roller width is changed on the basis of the roller width or the sleeve, it is possible to have position adjustment of the roller with respect to the absolute position of the rolling roller, that is, with respect to the rolling line itself, and not as a relative position between both.
5) The rolling roller is removed from the rolling mill independently of the engagement position adjustment means and so there are cost and workability advantages relating to the maintenance of the rolling roller.

While the presently preferred embodiments of the present invention have been shown and described, it is to be understood that this disclosure is for the purpose of illustration and that various changes and modifications may be made without departing from the scope of the invention as set forth in the appended claims.

Claims

A rolling roller (1) having adjustable roll width, comprising a roller shaft (10), at least one sleeve (20), which fits over said roller shaft (10), rolling wheels (11,21) mounted on said roller shaft, wherein at least one roller wheel (21) is mounted on said sleeve (20),
characterized in that
said sleeve (20) tightly fits over said roller shaft (10) at a portion other than that at which said roller wheels (11,21) are mounted, and hydraulic fluid supply paths (53,54) to said portion are formed inside said roller shaft (10).
The rolling roller according to claim 1, wherein said rolling wheel (21) is detachably fitted over said sleeve (20).
A rolling mill comprising a rolling roller (1) according to claim 1 or 2, wherein said roller (1) is immovably supported in the axial direction so as to freely rotatable by means of chocks (30,40), and at two positions (31,41), other than the mounting position of said sleeve, is installed in a fixed housing (101) through said chocks (30,
40), and further comprising hydraulic fluid supply means (50) being connected to said hydraulic fluid supply paths (53,54) and engagement position adjustment means (110) for adjusting a position of engagement in the axial direction of said sleeve (20) and said roll shaft (10) with respect to at least one of said chocks (30,40).