JPH05122B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION A. Field of Industrial Application The present invention is directed to a mill housing in which the chock of a pair of processing rolls is slidable within a mill housing so that the axes of the processing rolls are held within one vertical plane. Apparatus and method for rolling flat workpieces, especially wide workpieces, using a pair of small diameter work rolls, such as those installed in The present invention relates to a rolling mill supported by equally spaced pressure transmitting elements, the pressure transmitting elements of at least one of the work rolls being each provided with a controllable fluid pressure device.

Although the rolling mill of the present invention is described herein by way of example for rolling plates of metal, it goes without saying that the invention is equally applicable to sheets or strips of metal. Furthermore, the workpiece is not limited to metal, as the principles of the invention are applicable to strips, sheets, or plates of any plastically deformable material, such as plastics and the like.

B. Prior art and problems Mills that roll steel or other plates or strips (particularly wide plates or strips) using processing rolls with a small diameter to increase the roll pressure Equipped with a device to minimize bending of processing rolls. Otherwise, the workpiece cannot be rolled smoothly.

One way to reduce work roll deflection is to include large diameter bucking rolls. Another method is to construct the mill in the form of a one-piece rigid housing with spaced bucking elements in the beams of this housing, by which the processing rolls can be directly or additionally rolled. It is to support through.
A mill of this type is described, for example, in US Pat. No. 4,295,355.

However, even a bucking roll with a very large diameter will bend to some extent due to the rolling load. To compensate for this, the rolls are made barrel-shaped so that when rolling pressure is applied, the generatrix of the rolls at the roll bite point is straight, thus reducing the roll gap to the workpiece (strip). The aim is to always keep the width uniform over the entire width. Only if the roll gap is uniform will the rate of thinning of the workpiece in the roll pass be uniform across the width of the workpiece, and only in such case
For example, a flat workpiece remains smooth even after a 15% roll pass.

In the above one-piece housing type mill,
Each of the spaced apart bucking elements is provided with an eccentric adjustment device to maintain an even roll gap under rolling pressure. If a strip without corrugations is passed through such a mill, the roll gap will be 0.0001
The above adjustments must be made precisely because even an inch (0.00254 mm) error will result in a visible waveform.

In addition, there is a technology in which multiple split back-up rolls are arranged along the surface of the processing roll, and a hydraulic adjustment mechanism is provided for each of the multiple back-up rolls to control the rolling force in the width direction of the rolls and the roll opening degree. It is shown in Special Publication No. 50-32076. However, in this Japanese Patent Publication No. 50-32076, a plurality of divided back-up rolls are connected via roll joints,
Since pressure is applied to this roll joint from a hydraulic pressure adjustment mechanism, its practical effectiveness is extremely limited. That is, one of the two roll joints on one split back-up roll (which is also one of the roll joints on the other adjacent split back-up roll) is smaller than the other one. When pressure is applied and pressure control is performed, the axis of this back-up roll will not be parallel to the axis of the processing roll (work roll), and in extreme cases, only one end of the split back-up roll will be parallel to the processing roll. This resulted in a contact state, resulting in poor control accuracy.

It is an object of the present invention to improve these drawbacks of the prior art and, instead of suppressing the deflection of the work roll by the stiffness of the bucking element, it is an object of the present invention to The object is to obtain a rolling mill in which the uniformity of the roll gap is maintained by the elements.

C. Means for Solving the Problems The rolling mill of the present invention is a rolling mill for rolling flat workpieces such as plates, sheets, or strips from plastically deformable materials, and includes two housings and , upper and lower buckling beams respectively attached at opposite ends to said housing; and said upper and lower buckling beams.
upper and lower work rolls each supported on a beam; a device for maintaining the axes of the upper and lower work rolls in the same vertical plane; and operatively coupled to the work rolls. a device for rotating the upper and lower work rolls in opposite directions; and a pressure transmission element carrying a plurality of rollers for each of the upper and lower work rolls; the pressure transmitting element for each work roll is located between the work roll and an adjacent bucking beam;
Each of the pressure transmitting elements for each said work roll is separately attached to an adjacent bucking beam, and said pressure transmitting element for each said work roll is operatively connected to an adjacent sector of the respective work roll. a plurality of said rollers in contact with said pressure transmitting rollers spaced evenly along the surface of each work roll, said pressure transmitting for said upper work roll and said lower work roll; the elements are of the same number and arranged opposite each other, each of the pressure transmitting elements for at least one of the upper and lower work rolls being connected to this pressure transmitting element; and an individually controllable fluid pressure device, the pressure transmission element being adapted to transmit rolling force to the sector of the at least one work roll via the individually controllable fluid pressure device. It is characterized by the presence of

The pressure transmitting elements of the present invention can take various forms. For example, each pressure transmitting element can include a bracket supporting two rows of bucking bearings. The rows of bucking bearings are arranged on either side of the plane of symmetry in which the axis of the work roll lies. In another embodiment, the pressure transmitting elements each include an endless chain of rollers that contact a portion of the circumference of the work roll and roll against an arcuate anvil.

For mills requiring work rolls of smaller diameter, especially when rolling wide plates or strips of work-hardening material to thin thicknesses, two intermediate Rolls are used, thus making it possible to construct the well-known six-high mill. In this case, each pressure transmission element would comprise an endless chain of rollers contacting a portion of the circumference of each intermediate roll of the respective work roll and running around an arcuate anvil.

Whether the mill is a two-stage or a six-stage mill, the pressure-bearing capacity of pressure elements of the type that uses an endless roller chain is limited by the pressure-bearing capacity of a series of short rollers, each roller of the chain mounted on the same axis. , which becomes significantly larger when the links between the roller axes are very thin.

Furthermore, according to the present invention, in order to further reduce the torque applied to the processing rolls, the roller chain can be driven so that the chain itself functions as a sub-drive device for the processing rolls. This is important in mills rolling very wide plates where roller drive is an issue. If the roller chain itself is driven, it must have more of the characteristics of a traction chain and its connecting links will therefore be thicker to withstand the tensile forces.

In the present invention, the workpiece to be rolled is passed between upper and lower work rolls, and the pressure applied to the work rolls is continuously monitored by a pressure transmission element having a fluid pressure device, and while or increased or decreased across the width of the faces of both work rolls, thereby compensating for lack of smoothness or uneven gauge or temper of the workpiece. As a result, very wide plates or strips can be rolled to a smooth and uniform thickness using a mill that is simpler and lighter in construction than conventional beam bucking mills. Furthermore, a mill of the type described in this invention comprises:
The structure can be made to handle plates or strips several times wider than previously possible.

The pressure transmitting element of the present invention is reduced in size and this advantage allows the mill to be equipped with two spaced pairs of upper and lower work rolls, each pair of work rolls as described herein. and receives precise and adjustable backing from pressure elements spaced along its length. the two pairs of processing rolls are driven with a constant but controllable speed difference;
This tensions the part of the workpiece between the pairs of work rolls, which further improves the smoothness of the workpiece and allows for stronger rolling passes.

D. Example Similar parts in FIGS. 1 to 3 are designated with the same reference numerals. As shown in the drawings, the housing of the rolling mill of the present invention is constructed by connecting two bucking beams 1 and 2 with four deep channels 3-6. These channels act as columns of the mill and are placed back to back at each end of the beams 1 and 2. A window 7 is formed between the channels 3 and 4, in which sliding jocks 8 and 9 are mounted. A window 10 is likewise formed between the channels 5 and 6, in which sliding jocks 11 and 12 are mounted. Upper processing roll 13 on wheels 8 and 11
are mounted, and a lower work roll 14 is mounted on chock 9 and 12, by means of which the work rolls 13 and 14 can be displaced up and down in one common vertical plane. Processing roll 13
and 14 each include a splined end (not shown) for receiving driving force from a spindle (not shown) in a manner well known in the art. As a specific example, if the mill housing shown in Figures 1, 2, and 3 were built for an 80-inch (2032 mm) wide workpiece, its weight would be greater than that of a conventional mill housing of the same width. for things, e.g. 4
It accounts for only about 20% of the weight of the housing of the stage mill. The reason for this is that the precision of the workpiece produced according to the invention is not achieved by the rigidity of the mill housing, although the housing must have sufficient strength to withstand large roll separation forces. The advantage is that it can be constructed so that it can be bent by such roll separation force or rolling load. For example, in a beam buckling mill of the above dimensions as described in my U.S. Pat. In mill housings, the deflection of the beam under rolling pressure is 0.020 to 0.040
Inch (0.508-1.016mm) is allowed.

The main object of the invention is to provide a rolling mill with backing of narrow work rolls 13 and 14. Upper processing roll 13 and lower processing roll 1
At least one of the work rolls 4 (here referred to as the upper work roll 13 for convenience) is provided with pressure transmitting elements spaced from each other along its length, thereby absorbing roll separation forces and transferring the work rolls. Prevents bending. Each of these pressure transmitting elements of the upper work roll 13 is equipped with a fluid pressure device, such as a hydraulic cylinder 16, together with a device for instantaneous control of its pressure as required by the rolling process. The lower work roll 14 may have similar pressure transmitting elements with fluid pressure devices provided symmetrically along its length, or alternatively without fluid pressure devices along its length. It may also have pressure transmitting elements arranged symmetrically along the backing beam 2 and fixed directly to the plane of the bucking beam 2. This pressure transmitting element merely serves as a bucking bearing. The reason why such simplification is possible is that according to the principle of the present invention, the lower processing roll 14 bends to the extent that it bends the adjacent bucking beam 2 under rolling pressure. The resulting displacement of each pressure transmitting element of the lower work roll 14 is automatically compensated by the opposing or corresponding fluid pressure controlled element 16 of the upper work roll 13.

It will be appreciated that the pressure transmitting elements of the upper work roll 13 are all the same, and that the pressure transmitting elements of the lower work roll 14 can also be the same. The pressure transmission elements of both the upper working roll 13 and the lower working roll 14 may each be equipped with a fluid pressure device. Further, the pressure transmission element of the lower processing roll 14 is equipped with a fluid pressure device, and the upper processing roll 13 is equipped with a fluid pressure device.
The pressure transmitting element may be fixed directly to the adjacent buckling beam 1 without any fluid pressure device and act as a mere buckling bearing.

1, 2 and 3, the work roll 13 is supported by seven pressure transmitting elements, generally designated 15, and each of these pressure transmitting elements 15 is connected to a hydraulic cylinder 16. It is equipped with a type of fluid pressure device. The pressure transmitting elements 15 are evenly spaced along the length of the upper work roll 13 . In the illustrated embodiment, the lower work roll 14 is also provided with a similar pressure transmission element 15 directly below the corresponding pressure transmission element of the upper work roll 13;
Each is provided with a hydraulic cylinder 16. As can be seen from FIG. 2, it is also possible for the pressure transmission element 15 of either the upper working roll 13 or the lower working roll 14 to not be equipped with a fluid pressure device. In this case, the part 16 of the row of pressure transmitting elements that does not have a fluid pressure device may be considered to represent a mounting device for fixing that pressure transmitting element to the surface of the adjacent bucking beam 1 or 2. . In the embodiment of FIGS. 1 and 2, the lower row of cylinders 16
The fluid pressure within will be reduced to zero. The pistons of the cylinders will lower to the bottom of their stroke, and with them the lower work roll 14 will also lower by the same amount, so that the pistons will act as mere bucking bearings. In contrast, the pressure transmission element 15 of the upper work roll 13 provides sufficient control of the rolling pressure at all points on its surface, thereby making it possible to carry out the rolling process according to the invention.

The purpose of each pressure transmission element 15 is to transmit a controllable force to a sector of the rotating work roll 13 or 14. Each pressure transmission element 15 must therefore constitute a kind of bearing that engages with very little friction on a portion of the circumference of the work roll 13 or 14. Depending on the rolling program of the mill, one of several types of pressure transmitting elements can be chosen.

One embodiment of the pressure transmitting element 15 is shown in detail in FIG. This pressure transmission element 15 comprises an endless chain 17 of rollers that abuts a portion of the circumference of the working roll 13 and runs against an arcuate anvil 18 . Two side plates 19 and 20 are attached, one on each side of the anvil 18, and are further welded to the horizontal plate 21. This horizontal plate 21 is secured to the piston 22 of the cylinder 16 by suitable devices such as bolts 22a. Plates 19 and 20 are dimensioned to provide clearance for the return path of roller chain 17. Cylinder 16 is secured to the bottom of bucking beam 1 by suitable devices such as bolts 23.

FIG. 4 also shows one method of controlling fluid pressure within cylinder 16. FIG. Valve 24 in cylinder 16
are connected by a pipe 25, which is also connected to an accumulator 26. valve 24
has a supply pipe 27 connected to a source of high pressure fluid (not shown) and another conduit 28 connected to a tank for closed circuit operation. Rotating slide 2
9 normally closes those connections 27 and 28;
The accumulator 26 then provides the necessary resiliency to the rigid system.

If the pressure in the cylinder 16 is to be increased, the rotating slide 29 is made to make one quick rocking motion, which opens the high pressure line 27 for a short period of time, for example 20 microseconds. This adds a small amount of fluid to the fluid in the cylinder system, which compresses the gas in the accumulator 26 and increases the pressure. Usually such pressure increases are required several times and are performed intermittently at high speeds. To lower the pressure, conduit 28
To open it, the rotating slide is rocked for a short period of time. This is also usually done several times intermittently at high speed. Other pressure control systems could also be used.
The constant fine repetition scheme described above is simple and provides precise control. Whatever pressure control system is provided for each cylinder 16, it could be manually operated or of the type responsive to appropriate sensors.

Other embodiments of pressure transmitting elements are shown in FIGS. 5 and 6. In this embodiment, processing roll 13
is supported from behind by two rows of bucking bearings 30 and 31. These bucking bearings are divided into three groups in this example, and the two bucking bearings are
A bearing 30 is placed on one side of the work roll 13 and one bucking bearing 31 is placed on the other side of the work roll 13. Bucking bearings 30 and 31 are held within a bracket generally designated 32. Bracket 32 in Figure 6 is marked with backing for clarity of drawing.
Bearings 30 and 31 are shown omitted.

The bracket 32 includes a vertical plate 33 extending in a direction parallel to the axis of the upper work roll 13. A pair of brackets 34 and 35 are fixed at right angles to one side of the plate 33 in parallel and spaced apart fashion. A bucking bearing 31 is placed between these brackets 34 and 35 and is rotatably mounted by an axle 36. Similarly plate 3
three brackets 37,
38 and 39 are fixed in parallel and spaced apart. Between these brackets 37, 38, and 39 are a pair of bucking bearings (one of which is shown at 30 in FIG.
) is rotatably mounted by a shaft 40 .

The bracket 32 also includes a horizontal top plate 4 shown in solid lines in FIG. 5 and in dashed lines in FIG.
Contains 1. This top plate 41 is attached to the piston 22 of the cylinder 16 by suitable means such as bolts 42, so that the pressure transmitting elements of FIGS. A controllable force of the cylinder 16 can be transmitted. As can be seen in FIGS. 5 and 6, the cylinder 16 and bracket 32 are eccentric with respect to the axis of the upper work roll 13. The axis of cylinder 16 intersects a horizontal line extending perpendicularly between the axes of axes 36 and 40 at one third of the distance therebetween. The two bucking bearings 30 on the shaft 40 thus create a moment equal to one bucking bearing 31 on the shaft 36, but in opposite directions with respect to the axis of the cylinder 16. Since the horizontal component is absorbed into the common bracket 32 of FIGS. 5 and 6, only the vertical component is active.

If pressure transmitting elements of the type shown in FIGS. 5 and 6 are used, one pressure transmitting element may be provided with two bucking bearings 30 on one side of the work roll 13, then the next The pressure transmitting elements are arranged alternately with one bucking bearing 31 on the same side of the work roll 13. This is necessary, first of all, in order to minimize possible markings on the working roll 13, where the gap between two bearings on one side is opposite to one bearing on the other side; And secondly, one pressure transmission element is always needed to support the same short length of work roll 13 as the other elements.

Particularly when the workpiece is a work-hardening metal such as high carbon steel or stainless steel and smaller diameter work rolls are required, such as when rolling wide plates or strips to thin thicknesses. , a well-known six-high mill is constructed in which two intermediate rolls are used to support each work roll. Figures 7 and 8 show such a mill according to the invention.

FIG. 7 is a fragmentary view similar to FIG. 3, showing the channels 5 and 6, the window 10 formed thereby, the upper chock 11a, and the upper work roll 13a. Upper chock 11a is similar to upper chock 11 of FIG. 3, but includes bearings for a pair of intermediate rolls 43 and 44. The upper working roll 13a is free-floating and guided in the vertical plane of symmetry of the mill by intermediate rolls 43 and 44. It will be appreciated that the lower work roll (not shown) is similarly supported and guided by a pair of chock mounted intermediate rolls (not shown).

FIG. 8 shows an embodiment of a pressure transmission element for use in a mill of the type shown in FIG. The pressure transmitting element of FIG. 8 is similar to that of FIG. 4 and includes an arcuate anvil 45 similar to anvil 18.
Anvil 45 is held rigidly between a pair of plates. One of the plates is illustrated as 46. The plates are similar to plates 19, 20 of FIG. The pair of plates (one of which is shown at 46) is mounted on a horizontal plate 47 similar to horizontal plate 41 of FIG. Plate 47 is fixed to piston 22 of cylinder 16 in the same manner as in FIG. The anvil 45 is configured to support an endless chain 48 of rollers and to provide a gap for the return path of the endless chain 48.

Anvil 45 is shaped to bring endless chain of rollers 48 into contact with a portion of the circumference of intermediate rolls 43 and 44. Anvil 45 and endless roller chain 48 have substantially the same function as anvil 18 and endless roller chain 17 of FIG. 4, except that they operate on intermediate rolls 43 and 44. The anvil 45 also includes an intermediate roll 4
It acts as a beam that absorbs the horizontal component of the roll pressure applied from 3 and 44.

Although FIGS. 4, 5, 6, and 8 show pressure transmitting elements provided on the upper working roll 13 or 13a, similar pressure transmitting elements may also be installed on the lower working roll as shown in FIG. It will be appreciated that you can also prepare for rolls. Both sets of pressure transmitting elements may be fixed to the piston of the cylinder 16. Furthermore, as already mentioned, the rolling method of the present invention is effectively carried out even with accurate control of the pressure of only one work roll (preferably the upper work roll) by means of spaced apart pressure transmitting elements. The lower set of pressure transmitting elements may be fixed to the corresponding housing beam.

While the mill of the present invention is in operation, when rolling the widest plate or strip for the mill, it is necessary to use all cylinders 1 to keep the work roll pressure even across the width of the workpiece.
The pressure within 6 must be maintained the same. If, on the other hand, the width of the workpiece is narrower, it is necessary to maintain the same pressure only in the cylinders 16 of the pressure transmission elements supporting the work roll sectors located within the width of the workpiece. The pressure in the cylinder 16 of the pressure transmitting element supporting the work roll sector which is only partially within the width of the workpiece (ie on both sides of the workpiece) is maintained at an intermediate pressure value. The pressure in the cylinder 16 of the pressure transmitting element supporting the work roll sector completely outside the workpiece width is brought to zero.

Constructions according to the invention require very wide plates or strips, e.g. approximately 80 inches wide (2032
A compact, sturdy and relatively lightweight mill housing can be constructed which is particularly useful in mills that roll plates or strips (mm) or larger. In fact, the mill according to the invention is too large for ordinary four-high mills, and even for known beam buckling mills (such as the mill described in the above-cited patent no. 2,479,974), the housing weighs several hundred tons. It is possible to roll strips of any size as required. width
A mill with the structure shown in Figure 2 rolls 200 inches (5080 mm) of stainless steel to 1/6 inch (4.23 mm) thick.
The total weight, including the drive spindle etc., would be only 125 tons.

The widest steel rolling mill in operation today is a West German beam bucking mill that rolls strips up to 109 inches (2768.6 mm) wide. This mill weighs over 350 tons.
Therefore, designing a rolling mill for 200 inch (5080 mm) wide strips is out of the question. In contrast, in the mill according to the present invention, the 200 inch width is still a considerable margin of limit.
Should the need arise for a 400 inch (10106 mm) wide strip mill, the present invention would be easy to construct and would not require much weight.

The invention also provides a narrower width (80 inches (2032
It can also be applied to mills that roll strip, sheet or plate workpieces (mm) or less. Such a mill constructed in accordance with the present invention would be lightweight, simple in construction, and inexpensive.

9 through 12 illustrate a preferred embodiment of the pressure transmitting element of FIG. 4. FIG. The pressure transmitting elements of FIGS. 9 to 12 have a better pressure bearing capacity than the pressure transmitting elements of FIGS. 5 and 6, respectively.
The pressure transmitting elements of Figures 9 through 12 have a relatively small space requirement, which allows for many applications, and can also be used in other rolling mills, where such pressure transmitting elements would otherwise be used. It can be used to manufacture new types of mills.

In FIGS. 9 and 10, the pressure transmitting element is designated generally at 49 and is assumed to be associated with a lower work roll 50 by way of specific illustration. However, it goes without saying that the pressure transmission element 49 can also be applied to the upper work roll without any modification. Pressure transmitting element 49 comprises an arcuate anvil 51 similar to anvil 18 of FIG. The arcuate shape of the anvil forms a load bearing cavity or depression on its upper surface. Anvil 51 is surrounded by an endless chain 52 of rollers which transmits the pressure of work roll 50 to anvil 51.

Anvil 51 has a pair of side plates 53 and 54
are keyed at 53a and 54a. Side plates 53, 54 are similar to side plate 20 of FIG. 4 and are sized to provide clearance for the return path of roller chain 52. Side plates 53 and 54 are secured by welding or otherwise to a horizontal plate 55 similar to horizontal plate 21 of FIG. This horizontal plate 55 is bolted directly to the face of the piston or backing beam of the rolling mill, as in FIG.

As clearly shown in FIG. 11, the primary difference between the pressure transmitting element 49 of FIGS. 9 and 10 and that of FIG. 4 is in the configuration of the roller chain 52. FIG. 11 shows two adjacent rollers of short length, designated generally at 56 and 57. Each of these rollers includes a plurality of short roller segments 56a and 57a. Although the number of roller segments is not critical, in the illustrated embodiment rollers 56 and 57 are each made of six segments. roller bearings, roller bearings
Hardened and polished steel rollers, whether used in chains or frictionless guideways, typically have a diameter/length ratio of 1/1 to 1/2. This is subject to processing such as warping, heat treatment and centerless polishing. The diameter of these rollers must be larger than the profile of the link 60 connecting the shafts 58 and 59.

Since the roller chains 52 do not transmit tensile forces, the links 60 between them can be very thin (e.g. for 3/4" (19.5 mm) diameter rollers).
0.020° (0.508mm) spring steel links can be used). This thinness of link 60 provides two advantages. The first is that the loss of axial space is very small. Second, the elastic indentations made in the work roll by the rollers are essentially constant over the entire roller surface, so the normal taper at the ends of all roller segments avoids stress concentrations. is no longer necessary.

This latter advantage can be explained as follows. The rollers of chain 52 transmit pressure (roller separation force) from work roll 50 to anvil 51 along two opposing generatrix lines. This causes all three elements to flex elastically.
This results in a narrow area contact (rather than a line contact) between one roller of roller chain 52 and work roll 50. Moshi Laura Chain 52
and the processing roll 50 constitute a continuous cylindrical body of variable length, as long as the roll separation force is uniform over the roll surface, as in rolling flat articles. , the width of the contact surface between the roller and the processing roll is constant. However, conditions are different near the ends of the rollers of roller chain 52. This is because the elastic indentations made by that roller in the work roll 50 do not break off abruptly, but follow elastic stress flow lines. This is shown exaggerated in FIG.
FIG. 13 shows one segment 56 of roller 56.
When only segment a acts on the processing roll 50, the segment 56a acts on the processing roll 50.
An elastic recess 61 is shown. Roller segments 56a are shown in dashed lines so as not to obscure the elastic recesses 61. As seen in FIG. 13, the left end of roller segment 56a is entirely cylindrical. Over almost the entire length of roller segment 56a, elastic recess 61 has a narrow, uniform width. However, at the left end of the roller 56a, the elastic recess expands into a funnel shape.

To prevent this from occurring, the ends of roller segment 56a are tapered, as is well known in the art. To illustrate this, the right end of the roller segment 56a shown is tapered. The taper is exaggerated in FIG. 13 for clarity. As can be seen in FIG. 13, the effect of the taper is that the pressure at that end of roller segment 56a becomes zero, and therefore the width of the elastic recess formed in work roll 50 also narrows to zero. However, if both ends of each roller segment 56a are tapered, the load carried by those ends becomes smaller.
The load carrying capacity of the rollers 56 is reduced.

FIG. 14 is a view similar to FIG. 13, showing schematically in a cutaway manner the impression made by the work roll 50 and the entire chain roller 56 of FIG. 11 thereon. In this case, because of the thin spring steel link 60 (not shown), the gap between the ends of the roller segments 56a is only about 0.020 inch (0.508 mm), so that the outermost roller Only the outer end of segment 56a needs to be tapered. The other ends of all segments 56a are almost butt-jointed, and the stress flow lines smoothly cross the narrow gap between them, so no stress concentration is observed, so there is no escape at those ends. There is no need for tapering. Because there is no stress concentration, the elastic recesses 62 formed in the work roll 50 have a substantially uniform width over their entire length. Depending on the number of segments per roller in roller chain 52, selected thin spring steel links may be omitted in some configurations, in which case adjacent ends of selected roller segments can actually be compared.

The roller chain construction of FIG. 11, in which the rollers are made of multiple roller segments, allows for easier, more accurate, and less expensive fabrication of the roller segments. Except for the outermost portion of the outermost roller segment of each roller in chain 52, the rollers carry the full load along their entire length.

The roller chain of FIG. 11 can be readily adapted to pressure transmission elements for use in a six-high mill of the type shown in FIG. An example of this application is shown in FIG.
The pressure transmitting elements of the bucking rolls 63 and 64 of the lower working roll 65 are shown here. Of course, the bucking roll of the upper working roll can also be provided with the same pressure transmission element.

The pressure transmitting element of FIG. 15 is designated generally at 66. This is similar in many respects to the pressure transmitting element 49 of FIGS. 9 and 10. Pressure transmission element 66 includes an anvil 67 formed with two recesses for transmitting roll separation forces from backup rolls 63 and 64 to anvil 67. This anvil 67 is connected to the roller chain 5 in FIG.
2 and is surrounded by a roller chain 68 substantially identical to 2. Anvil 67 is keyed between a pair of side plates, one of which is shown at 69. Those side plates are horizontal plates 70
fixed by welding or otherwise. The horizontal plate 70 is directly bolted or otherwise connected to a piston of a hydraulic cylinder or to a bucking beam (not shown) of the mill. The configuration in FIG.
It is substantially the same as the configuration of FIG. 8 using the roller chain of FIG. The configurations of FIGS. 8 and 15 are particularly suitable for mills rolling very wide plates where the work rolls do not have sufficient torque transmission capabilities.

The width of the pressure transmitting elements of FIGS. 9 and 15, measured in the axial direction of the work rolls, is primarily limited by the optimum practical width of the roller chain. Each pressure transmission element supports a portion of the surface of a respective work roll. Therefore, in order to achieve complete bucking of the work roll, a sufficient number of pressure transmitting elements must be provided, aligned side to side, to cover the entire length of the work roll.

In some rolling mills for rolling flat workpieces, the pressure transmitting elements of FIG. 9 or FIG. 15 are designed in such a way that the pressure transmitting elements of FIG. It can be designed to help you. This is especially true for
As in the case of mills rolling wide plates,
In cases where the pressure-bearing capacity of the pressure-transmitting element is not very important, and the torque transmission is of considerable importance,
This is desirable. In such cases, if the chain is designed to transmit traction to the work roll and the roller chain is driven, it can be used as an auxiliary drive to assist the work roll. As an illustration thereof, FIG. 16 shows a pressure transmitting element similar to the pressure transmitting elements of FIGS. 9 and 10, but with a driven traction transmitting roller chain. The chain would be similar to that shown in FIG. 11, but the connecting links would be made more robust and able to provide substantial tensile forces. FIG. 16 shows the lower processing roll 7.
2 shows a pressure transmitting element, designated generally at 71, for 2. It will be appreciated that the pressure transmitting elements of the upper work roll can be substantially similar.

The pressure transmission element 71 is the same as the pressure transmission element 49 in FIG.
It has an arcuate anvil 73 having a concave portion that receives a load. This anvil 73 is keyed to a pair of side plates (one of which is indicated at 74) similar to side plates 53, 54 of FIG. The side plates are welded or otherwise secured to the horizontal plate 75. Plate 75 may be attached directly to the bucking beam of the mill or may be coupled to a hydraulic cylinder of the type shown in FIG.

The difference between the pressure transmitting element 71 of FIG. 16 and the pressure transmitting element 49 of FIG. 9 is that one end lobe of the anvil 73 is replaced by a sprocket 76. Sprocket 76 engages and drives a roller chain 77 surrounding it and anvil 73. The lobe portion of anvil 73 that replaces sprocket 76 is outside the load-bearing area of the anvil. Sprocket 76 is therefore also outside its load-bearing area. Pressure transmitting element 71 compared to pressure transmitting element 49 of FIGS. 9 and 10.
Although the load carrying capacity is sacrificed to some extent, the roller chain 77 can transmit substantial traction force to the work roll 72, which helps drive the work roll.
Therefore, the torque shared by the processing rolls can be reduced. This is important in very wide plate rolling mills where roll drive is difficult. The sprocket 76 is fixed to an axle 78, which passes through suitable bearings (not shown) provided in the side plates of the pressure transmitting element 71. axis 78
extends the entire length of the work roll and drives other pressure transmitting elements of the work roll 72 as well.
The end of shaft 78 is coupled to a suitable drive (not shown).

Prior art beam bucking mills, even with spaced adjustable roll supports and very small passes, do not provide acceptable smoothness. After rolling, the plate must be annealed and then flattened by repeated passes through roller levelers and/or by gripping both ends of the rolled plate with a stretcher and pulling the plate flat. According to the present invention, it is possible to provide a plate mill that can produce plates with excellent smoothness without such additional steps. In order to obtain excellent smoothness with very few passes, the pressure transmitting element of the present invention is of small size and is similar to the mill of FIGS. 1-3, but with two parallel spaced apart Preferably, the mill is constructed with a pair of upper and lower working rolls. Such a mill is shown in simplified form in FIG.

Similar to the mills shown in Figures 1 to 3, the 17th
The mill shown has upper and lower bucking beams 79
and 80. These bucking beams are of dual construction. The mill of FIG. 17 includes a first pair of upper and lower work rolls 81 and 82 and a second pair of upper and lower work rolls 83 and 84. In FIG. 17, the mill column and processing roll 81
The sliding chock 84 has been omitted for clarity of the drawing. Work rolls 81-84 each include a plurality of spaced apart pressure transmitting elements along its surface in substantially the same manner as shown in FIG. Each pressure transmitting element of work rolls 81-84 is designated 85-88, respectively. Any of these pressure transmitting elements according to the invention may be used. In the illustrated embodiment, pressure transmitting elements 85-88 are of the preferred embodiment of FIGS. 9 and 10. Pressure transmitting elements 86 and 88 of lower work rolls 82 and 84 are connected to lower bucking beam 80.
mounted directly on. Upper processing rolls 81 and 83
Pressure transmitting elements 85 and 87 are coupled to upper bucking beam 79 via controllable pressure devices 89 and 90, preferably in the form of hydraulic cylinders, as described in FIGS. 2 and 4. As described in FIG. 2, in the present invention, the upper processing roll 81
and 83 pressure transmitting elements 85 and 87 are mounted directly on the upper bucking beam 79 and the lower processing roll 8
Pressure transmitting elements 86 and 88 of 2 and 84 may be attached to adjustable pressure devices such as hydraulic cylinders. Similarly, the pressure transmission elements of both the upper processing rolls 81, 83 and the lower processing rolls 82, 84 can be provided with hydraulic cylinders.

The significance of the millimeter in FIG. 17 is that the two pairs of work rolls 81, 82 and 83, 84 are strictly controlled so that the portion 91a of the workpiece 91 extending between them is maintained in tension. It is characterized by being driven in a correlated manner. As a result, two advantages are obtained. First, the smoothness of the workpiece 91 is enhanced. The second is the ability to make more powerful passes. For example, nickel base alloy 100×200×
0.2 inch (2540 x 5080 x 5.08 mm) can be rolled from 0.35 inch (8.89 mm) in 5 to 7 passes. The operation of the mill of FIG. 17 preferably involves two pairs of processing rolls 8 capable of rolling in both directions to increase productivity.
This is done by accurately controlling the surface velocities of 1,82 and 83,84.

Such precise control can be achieved, for example, by a gearing system of the type shown schematically in FIG.
In FIG. 18, sun gear 92 meshes with surrounding planetary gears 93, 94, 95. These planetary gears are interconnected by suitable spiders. The planetary gears 93, 94, 95 mesh with an internal ring gear 96 surrounding them. This ring gear also has external teeth, which are connected to the shaft 98 of the gear motor 99.
It meshes with the worm 97 mounted above.

When ring gear 96 is stationary, the ratio between the angular velocity of sun gear 92 and the angular velocity of planet gears 93, 94, 95 is constant. Precisely change the ratio between the angular velocity of the sun gear and the planetary gear in small proportions by turning a worm with a gear motor 99 to rotate the ring gear 96 clockwise or counterclockwise at a controlled speed. or can be adjusted, and this adjusted ratio remains constant as long as the ring gear 96 is turned by the worm 97 at the same speed. Therefore, by giving a certain angular velocity to the sun gear 92, the speed of the spider connecting the planetary gears 93, 94, 95 can be precisely and reliably controlled.

Therefore, for example, the shaft of the sun gear 92 drives the processing roll pair 81, 82, and the planetary gears 93, 9
Spider assembly supporting 4,95 (not shown)
If the pair of processing rolls 83 and 84 are driven by the axis of the worm 97, the pair of processing rolls 8
It is possible to accurately control the ratio of the surface speed of the processing rolls 81, 82 and the surface speed of the processing roll pairs 83, 84. The tensile force can be precisely controlled. If the mill is of the reversible type, when reversing is performed the worm 97 is also reversed at the same speed but in the opposite direction. Thus, of course, the same tensile force is maintained between the two work roll pairs as long as they are set to perform the same pass thinning.

The mill of FIG. 17 is equipped with pairs of pinch rolls 100, 101 and 102, 103 on either side thereof;
The first or last part of the workpiece may be gripped and fed back into the roll bite. By providing these pinch rolls, the rolling of each plate can be fully automated.

As mentioned above, the mill of FIG. 17 is capable of rolling plates with excellent smoothness in a very small number of passes. In addition to the control of the roll pressure at all points on the roll surface, which allows uniform stretching of the plate, the two processing rolls are driven in such a way that the surface speeds of the two pairs of processing rolls are in the required ratio. This tensions the plate section between the two pairs of processing rolls, which allows for a greater rate of thickness reduction per pass and allows the workpiece to be stretched with excellent smoothness. .

In operation, the roll pressure, controlled by hydraulic pressure in cylinders 89 and 90, is uniform across the width of the workpiece, with the exception of cylinders near the edges of the workpiece, which are set at significantly reduced pressures. Set. Variations in pass thinning rate of the plate can be determined manually or automatically in one or more cylinders 89 and 9.
This can be corrected by adjusting 0 appropriately. These cylinders are configured to provide pass thickness reduction commensurate with factors such as the type of metal of the workpiece, the power available to drive the work rolls 81-84, heat distribution, etc. Process roll pressure does not need to be changed from pass to pass until the final pass where it is lowered. The two most important factors to monitor are
This is the ratio of the surface velocities of the pair of work rolls 81, 82 and 83, 84, and this ratio must be reversed each time the rolling direction is reversed. This sequence,
The feeding of the workpiece 91 into the roll bite is preferably automatic.

The invention is still capable of various modifications without departing from its spirit.

[Brief explanation of the drawing]

Fig. 1 is an end elevational view of the rolling mill of the present invention;
The figure is a front elevational view of the mill in Figure 1, Figure 3 is a sectional view taken along line 3-3 in Figure 2, and Figure 4 is a cross-sectional view of the pressure transmitting element in Figures 2 and 3. 5 is a partial cross-sectional end view of another embodiment of the pressure transmitting element of the present invention, FIG. 6 is a cross-sectional plan view of the frame of the pressure transmitting element of FIG. 5, and FIG. 7 is a partial sectional end view of another embodiment of the pressure transmitting element of the present invention. 8 is a sectional view of the pressure transmitting element of the mill of FIG. 7; FIG. 9 is a sectional view of another embodiment of the pressure transmitting element of the present invention;
10 is a sectional view taken along the line 10-10 in FIG. 9, FIG. 11 is a plan view of the roller chain in FIGS. 9 and 10, and FIG.
FIG. 13 is a schematic plan view of the work roll and one roller of the roller chain, tapered at one end and untapered at the other end. FIG. 14 is a schematic plan view of the working roll and the segmented roller of the present invention, and shows the elastic impressions or indentations made on the working roll by the segmented rollers. Drawing showing impressions attached, No. 15
Figure 16 is a schematic diagram of the roller chain of Figures 9 to 12 applied to a six-high mill; Figure 16 is a section similar to Figure 9 showing the pressure transmission element with the driven traction roller chain; 17 is a schematic cross-sectional view of a mill with two pairs of processing rolls equipped with the pressure transmitting element of the present invention; FIG. 18 is a schematic view of the drive gearing of the mill of FIG. 17; FIG. 1, 2, 79, 80... Batsking Beam,
13, 14, 50, 65, 72, 81, 82, 8
3, 84, ... Processing roll, 15, 49, 66,
71, 85, 86, 87, 88, ... pressure transmission element, 16, 89, 90 ... hydraulic cylinder, 17,
48, 52, 68, 77... Endless roller chain, 18, 45, 51, 67, 73... Anvil, 30, 31, 43, 44, 63, 64... Bucking roll, 32... Bracket, 56 ，
57... Roller, 56a, 57a... Roller segment, 60... Link, 61, 62... Elastic recess, 76... Sprocket, 91... Workpiece,
92...Sun gear, 93,94,95...Planetary gear, 96...Ring gear, 97...Worm, 9
9...Motor, 100, 101, 102, 103
...Pinch roll.

Claims (1)

[Claims] 1. Plates, sheets,
or a rolling mill for rolling flat workpieces such as strips, comprising two housings, upper and lower buckling beams each having their ends attached to the housings, and the upper and lower buckling beams. upper and lower work rolls supported respectively on side bucking beams; a device for maintaining the axes of said upper and lower work rolls in the same vertical plane; a pressure transmission element carrying a coupled device for rotating said upper and lower work rolls in opposite directions; and a plurality of rollers for each of said upper and lower work rolls; has
The pressure transmission elements for each work roll are disposed between the work roll and an adjacent bucking beam, and each of the pressure transmission elements for each work roll is separately adjacent. attached to a bucking beam, the pressure transmitting element for each said work roll comprising a plurality of said rollers in operative contact with adjacent sectors of the respective work roll. equally spaced along the surface, the pressure transmitting elements for the upper work roll and the lower work roll being of the same number and opposite each other; Each of the pressure transmission elements for at least one of the upper and lower work rolls has an individually controllable fluid pressure device coupled to the pressure transmission element; Rolling mill, characterized in that rolling forces are transmitted to said sector of said at least one work roll via said individually controllable fluid pressure device. 2. A rolling mill according to claim 1, in which the individually controllable fluid pressure devices include a cylinder and a piston, and a pressure transmission element carrying rollers with one fluid pressure device. each of which is attached to the piston and also includes a device for controlling the fluid pressure in the cylinder of each of the fluid pressure devices. 3. The rolling mill of claim 1, wherein each of the pressure transmitting elements includes an endless chain of rollers and an arcuate anvil, and the endless chain of rollers is mounted on the anvil and is connected to the anvil. It is designed to rotate around the
and a support device for said anvil, said support device of each pressure transmitting element comprising said controllable fluid pressure device being attached to a respective fluid pressure device, said support device comprising said fluid pressure device. A rolling mill, characterized in that the supporting device for the pressure transmitting element (not shown) is attached to an adjacent backing beam of the rolling mill.