JP2003088907A - Rolling mill, rolling equipment and rolling method - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rolling mill and rolling equipment which have proper control capacity of sheet crown and are compact. SOLUTION: This rolling mill is provided with a pair of upper and lower work rolls, a pair of upper and lower intermediate rolls, a pair of upper and lower back-up rolls and roll bending devices for respectively imparting bending forces to the work rolls and the intermediate rolls. In the case the maximum usable width of a rolled stock is Wmax (mm), the diameter Dw of the work roll is defined as the range of 300+50×(Wmax-1200)/300<=Dw<=375+50×(Wmax-1200)/300, the diameter Di of the intermediate roll is defined as the range of Dw<=Di<=450+75×(Wmax-1200)/300, and a work roll driving device for rotationally driving the work rolls is provided.

Description

Detailed Description of the Invention

[0001]

TECHNICAL FIELD The present invention relates to a rolling mill, rolling equipment and rolling method.

[0002]

2. Description of the Related Art Japanese Unexamined Patent Publications Nos. 57-202908 and 62-275508 disclose rolling techniques, particularly roll bending apparatus for imparting bending force to work rolls and intermediate rolls in cold rolling equipment. And a 6-high rolling mill (hereinafter referred to as a UC mill) including at least a shift device capable of moving the intermediate roll in the roll axial direction. Further, as another rolling mill, JP-A-1-15
4807 and the like.

In JP-A-57-202908, if the diameter of the intermediate roll is 1.1 times or more the diameter of the work roll, there is an effect of clarifying the shape-correctable range of the work roll and the intermediate roll bender. Is listed.

In JP-A-62-275508, it is stated that a work roll diameter smaller than the reinforcing roll diameter of 0.3 is used.

Japanese Unexamined Patent Publication (Kokai) No. 1-154807 describes a rolling mill having a work roll diameter smaller than a plate width of 0.15. Also, it becomes an intermediate roll or reinforcing roll drive,
A support roller is required to prevent side deflection of the work roll. Further, regarding the diameters of the intermediate rolls and the reinforcing rolls, it is said that they are larger than the plate width of 0.25, and the maximum diameter is not explained.

[0006]

The above-mentioned conventional technique is a technique in consideration of improvement of control capability, and if the control capability is improved, the facility becomes complicated and large, the facility cost increases, and the economy remains a problem. .

[0007] A compact rolling mill and rolling equipment and a rolling method for driving work rolls while maintaining the properties substantially equal to or better than the plate crown control properties that can be achieved by using an acceptable small diameter reinforcing roll are provided. Provision is desired.

An object of the present invention is to provide a compact rolling mill and rolling equipment having appropriate strip crown control capability.

[0009]

SUMMARY OF THE INVENTION The present invention is directed to a pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, and a pair of upper and lower reinforcements for supporting the intermediate rolls. A roll and a roll bending device that applies a bending force to each of the work roll and the intermediate roll, and the maximum usable plate width of the rolled material is Wmax (m
m), the diameter Dw of the work roll is 300 + 5
0 × (Wmax-1200) / 300 ≦ Dw ≦ 375 + 50
X (Wmax-1200) / 300, and the diameter Di of the intermediate roll is Dw ≦ Di ≦ 450 + 75 × (Wmax−1
The range is 200) / 300, and a work roll drive device for rotationally driving the work roll is provided.

[0010]

DESCRIPTION OF THE PREFERRED EMBODIMENTS (Embodiment) The following description will be made with reference to the drawings.

First, a schematic structure of a 6-high rolling mill (UC mill) according to an embodiment of the present invention will be shown. FIG. 4 shows a side view of a six-high rolling mill which is an embodiment, and FIGS. 5 and 6 show sectional views taken along arrows II and I in FIG. 4, respectively.

As shown in FIGS. 4 to 6, this 6-high rolling mill has a pair of upper and lower work rolls 2 which directly roll on the rolled material 1, and a pair of upper and lower intermediate rolls which respectively support the work rolls 2. 3 and a pair of upper and lower reinforcing rolls 4 that respectively support the intermediate roll 3. Bearing boxes 8 and 9 are attached to the roll ends of the work roll 2 and the intermediate roll 3, respectively, and by applying a vertical force to these bearing boxes 8 and 9 as shown in FIG. A work roll bending device 10 and an intermediate roll bending device 11 for bending each roll are installed. The structure is such that it is supported by the housing 5 via the bearing box 6 of the reinforcing roll 4.

A hydraulic pressure-reducing device 7 is installed at the lower part of the housing 5 as a pressure-reducing means, and the rolling-down material 1 is reduced by vertically moving the bearing box 6 of the lower reinforcing roll 4 by this pressure-reducing means.

In particular, in the following, the hydraulic cylinders 10a and 11 for bending the work roll 2 in the direction of expanding the gap.
a is an increment bending device (increase bender), and hydraulic cylinders 10b and 11b for bending in the opposite direction
Is called a decrease bending device (decrees vendor).

The pair of upper and lower intermediate rolls 3 is provided with a roll shift device so as to be movable in the roll axial direction. An example of this shift device will be described with reference to FIG. FIG. 6 shows a shift support member 12 that supports the bearing box 9 of the intermediate roll 3, and a shift head 13 that is joined to the shift support member 12.
This shift head 13 has one side of the intermediate roll bearing box 9
A shift attaching / detaching device including a hook 14 and a coupling cylinder 15 for freely coupling with and is installed. Furthermore, the shift head 13 has a structure in which a shift cylinder 16 fixed to the housing 5 is joined. With such a configuration, it is possible to move the intermediate roll 3 and the shift support member 12 to a free position in the roll axis direction by operating the shift cylinder 16 with the shift attaching / detaching device in the worn state. Become. In particular, since the shift support member 12 has the intermediate roll bending device 11 built therein, the point of action of the bending force does not change even when the work roll 2 is shifted, and the shift stroke can be made large.

Further, in the present embodiment, as shown in FIG. 4, the roll end of the intermediate roll 3 is usually tapered 1.
A chamfer 3a of about 000R is attached. In particular, the distance between the starting point of the chamfer 3a and the plate edge 1 is hereinafter referred to as UCδ. If the starting point of the chamfer 3a is outside the plate edge, the UCδ is represented by a positive value, and if it is inside, the value is represented by a negative value.

In order to provide a compact rolling mill in the 6-high mill as described above, while maintaining the characteristics equal to or better than those of the conventional rolling mill, the inventors of the present invention have combined specifications of roll diameters. I focused on. Conventionally, such a wide range of combinations of roll diameters and the margin of shape control characteristics have not been considered. This is because neither shape control nor compactification was taken into consideration. Then, if such a study is attempted by a shape simulation program, the number of combinations of roll diameters based on various conditions becomes very complicated, which is difficult. Under the circumstances, the present invention focuses on factors having a high influence among various conditions, and according to various conditions,
This was achieved by obtaining new findings.

In the following explanation, by the leveling control, etc.,
The plate crown shape is assumed to be controlled symmetrically,
It is assumed that the entrance side plate thickness before rolling is constant in the plate width direction. Also, with the plate center as the origin, the standardized coordinates normalized by the plate width are x
(= -1.0 to +1.0), and using this, the exit side plate thickness distribution function after rolling is represented by h (x). At this time, the plate crown function C (x) representing the shape of the rolled plate crown is defined by C (x) = h (x) -h (0) (1). That is, hereinafter, the plate crown means a plate thickness deviation between the plate thickness h (0) with the plate width center as a reference and the plate thickness h (x) at the plate width x. Therefore, when the plate thickness at the plate width x is thinner than the plate central portion, the plate crown C (x) at that point is represented by a negative value. Particularly, the plate crown when the work roll and the intermediate roll bending forces (Fw, Fi) are not acting is called a reference plate crown, and this plate crown function is represented by C _b (x). The above reference plate crown function C _b (x)
Is assumed to be symmetrical rolling, and can be expressed by the processing function of x. It is well known that such a function is easily approximated by the sum of quadratic and quartic expressions as shown in the following expression (2).

C _b (x) = A _b2 × x ² + A _b4 × x ⁴ (2) where A _b2 and A _b4 are coefficients of the quadratic and quartic expressions, and each roll diameter, plate thickness, rolling load. Is a constant determined by rolling conditions such as. Hereinafter, the coefficients of the quadratic and quadratic equations will be referred to as the quadratic component and the quadratic component of the reference plate crown. Especially at the plate edge, x =
Since it is ± 1.0, the coefficient means the maximum plate crown amount (μ) of the secondary and quaternary components at the plate edge. In addition, when the roll crown is not controlled by the roll bender, the outgoing side plate thickness generally becomes thinner toward the plate edge (convex shape).
The coefficients A _b2 and A _{b4 in the} equation (2) are negative.

On the other hand, the influence functions of the work roll and intermediate roll bending forces (Fw, Fi) in the UC mill on the plate crown are C _w (x) and C _i (x), respectively. It is considered that the effect of such roll bending force on the plate crown is approximately proportional to each roll bending force. In addition, it is considered that the effect of each roll bending force on the plate crown is approximated by the sum of the quadratic and quartic expressions as in the case of the reference plate crown.

Therefore, the maximum bending forces of the work roll and the intermediate roll, which are substantially determined by the respective roll diameters, are Fwmax,
Fimax, and the bending forces standardized using this are respectively η _w (= Fw / Fwmax) and η _i (= Fi / Fima
x), and the influence function C _w (x) and C of each roll vendor
_i a _{(x), C w (x} ) = η w × (A w2 × x 2 + A w4 × x 4) (3) C i (x) = η i × (A i2 × x 2 + A i4 × x 4 ) Think in (4). Here, the coefficients A _w2 , A _w4, etc. of the quadratic and quaternary equations are constants determined by the rolling conditions as in the equation (2), and are hereinafter referred to as the secondary and quaternary components of each roll bender. Further, each normalized roll bending force is hereinafter referred to as an increase direction (increase bender), with the positive acting direction (concave shape) increasing the exit side plate thickness toward the plate end. The opposite is called the decrease direction (decree vendor), and η _w , η _i
Is negative. To be precise, the characteristics of (3) and (4) have different characteristics in the increment and decrease directions, but the difference is slight, and the control characteristics in the increment direction are mainly examined below. Therefore, the coefficient value in this direction is used.

From the above, the coefficients of the equations (3) and (4) are
When the maximum increment bending force η _w = η _i = + 1.0 is applied independently, it occurs at the plate edge x = ± 1.0 2
The amount of plate crown of the second and fourth order components is shown. Therefore, in general, the coefficients A _w2 , A _w4 and A _{i2 of the} equations (3) and (4) are
Is positive, but A _i4 and A _w2 can be positive or negative depending on the calculation conditions.

Further, the maximum bending force Fmax substantially determined by each roll diameter is regulated by the allowable stress σ of the roll neck portion and is substantially proportional to the square of the given roll diameter D. This means that the roll neck diameter d is substantially proportional to the roll diameter D, and is, for example, d = 0.6 × D 2. On the other hand, the bending stress σ of the roll neck portion is the bending moment M acting on it.
Then, σ∝M / d ³ ∝M / D ³ . Also, the bending moment M is approximately the roll diameter D, where L is the distance between the point of action of the maximum bending force Fmax and the roll neck.
The size is proportional to. Therefore, σ∝Fmax / D ² . From this, the relationship between the maximum bending force Fmax and the roll diameter D is approximately proportional to Fmax∝D ² . From the empirical value of the design, the above proportionality constant is approximately 0 for a forged steel roll.
It is about 5. The following is a simple work rolls and intermediate rolls co ^{Fmax = 0.5 × D 2/1000} (5). However, D (mm) is the diameter of the work roll and the intermediate roll, and at this time, the maximum bending force Fmax of the formula (5)
(ton) is the value for one roll.

In the following, in the above shape characteristic model formula,
A method for obtaining the coefficients of the quadratic and quartic expressions will be described.
In the general plate crown shape, as shown schematically in FIG. 40, there is a so-called edge drop region in which the plate thickness rapidly decreases near the plate edge. This area is generally (2)-
The approximation by the maximum quartic equation as shown in the equation (4) has a large error and may cause a problem. Therefore, the coefficients in the equations (2) to (4) are determined by using the plate crown data in the area excluding the above edge drop area. The approximate plate crown range used in this study was a section of approximately 90% of the total plate width. Therefore, the secondary and quaternary component amounts at the plate edge in the equations (2) to (4) are the extrapolated amounts based on the coefficients determined by using the plate crown data in the approximately 90% section of the total plate width. Become. However, it has been sufficiently confirmed that the plate crown characteristics can be expressed without any problem. When, for example, each coefficient of the reference plate crown function of the equation (1) is obtained using the plate crown shape data in the above-mentioned approximate interval, approximate interval data of the plate crown with each bending force of the work roll and the intermediate roll being zero. Each coefficient may be determined by a well-known method so that the equation (2) is optimally fitted using. Further, for example, when obtaining each coefficient related to the work roll bender of the formula (3), η _w = + with reference to the plate crown of η _w = 0.
The difference with the plate crown at the time of 1.0 is taken, and this is optimally approximated in the above-mentioned approximate interval to determine each coefficient.

Model equations (2) to (4) constructed as described above
Accordingly, the strip crown C after control (x) is capable of substantially overlapping in a sufficiently wide _{range, C (x) = C b} (x) + C w (x) + C i (x) = (A b2 + Η _w × A _w2 + η _i × A _i2 ) x ² + (A _b4 + η _w × A _w4 + η _i × A _i4 ) x ⁴ (6) MAR (A2) = A _b2 + A _w2 + A _i2 (7) where each normalized bending force is η _w = η _i = 1.0 for each coefficient of the quadratic and quartic expressions on the right side of the above equation (6). MAR (A4) = A _b4 + A _w4 + A _i4 (8) The above-mentioned MAR (A2) and MAR (A4) are for the secondary and quaternary components of the plate crown shape control capability of the rolling mill system in the state where the maximum incremental bending force of the work roll and the intermediate roll is applied. It can be said that it represents the degree of control margin. Therefore, when the above value is negative, it means that the control capability for each control component is insufficient. In the following, the above parameter MAR
(A2) and MAR (A4) are called second-order and fourth-order component margins. Also, in order to provide a compact rolling mill, it was important to clarify the optimum combination conditions of various roll diameters. In order to carry out this, the secondary and quaternary component margin characteristics under various rolling conditions are investigated,
The suitable roll diameter combination conditions will be clarified below.

Table 1 shows plate crown simulation conditions used for examining the second-order and fourth-order component margin characteristics.

[0027]

[Table 1]

As shown, the assumed maximum plate width is 1
There were two types, 200 and 1500 mm, and the roll surface length of the rolling mill was 1400 and 1600 mm accordingly. The reason why the maximum plate width is considered is that the wider the plate width is, the more difficult it is to control the shape. For each of the above two types of maximum plate width conditions, two types of plate thickness conditions were separately assumed and simulation was performed. The plate thickness condition (A) is a case where the delivery side plate thickness is relatively large and the rolling load is small, whereas the plate thickness condition (B) is that the delivery side plate thickness is thinner than the plate thickness condition (A) and the rolling load is small. Is assumed to be high. In particular, FIG. 7 shows the relationship between the work roll diameter and the rolling load under each plate thickness condition. As is clear from FIG. 7, the rolling load varies depending on the work roll diameter because the conditions of the inlet and outlet plate thickness are constant. This is because even if the work roll diameter is changed, a comparative examination is performed using the same inlet and outlet side plate thickness conditions. Regarding each roll diameter,
A wide range of combination conditions will be used for the study, and these conditions will be clarified one after another in the explanation of the calculation results. The shift position of the intermediate roll is generally about UCδ.
It is often set to = 0 or plus several tens of mm in the plus direction. In this simulation, UCδ = 0 was used as a uniform value. Further, each roll was a straight roll without giving an initial crown. The conditions in Table 1 below are the maximum plate width 120
The cases of 0 mm and 1500 mm are called 4 width mill equivalent and 5 width mill equivalent, respectively, and the case of plate thickness conditions (A) and (B) are called soft material and hard material conditions, respectively. The above-mentioned conditions assume the so-called reduction rolling equipment of the ordinary cold reverse rolling equipment and the rolling mill for tandem rolling equipment which are the subject of the present invention.

The simulation results will be sequentially described below.

As for the secondary component margin, FIG. 8 shows an example of the secondary component margin calculated under the condition that the reinforcing roll diameter Db = 1300 mm and the soft material has a width of 5 mm. In FIG. 8, the horizontal axis is the work roll diameter and the vertical axis is the intermediate roll diameter, and the contour lines connecting points with the same secondary component margin are shown with an elevation difference of 2.5 μ. Hereinafter, such a diagram is referred to as a secondary component margin characteristic diagram. It is immediately apparent from this figure that there is a combination of a certain work roll and intermediate roll diameter that maximizes the secondary component margin. Such a characteristic was first discovered by the inventors by performing a huge amount of simulation.

Points on the same contour line on the secondary component margin characteristic diagram, for example, the combination points of roll diameters indicated by P1 to P4 in the figure, have substantially the same degree of secondary component margin. It will be. Therefore, it can be said that the combination of roll diameters indicated by P3 is suitable when providing a compact rolling mill while maintaining the same degree of secondary component margin characteristics. From the above basic point of view, how to determine a suitable roll diameter combination range will be described below.

Now, the roll combination area shown in FIG. 8 is divided into four by horizontal and vertical lines X and Y passing through substantially the center of the contour line group. In this example, the line is divided by a line passing through the point where the intermediate roll diameter is 450 mm and the point where the work roll diameter is 375 mm. Further, the four divided areas formed at this time are named first area to fourth area as shown in the figure. In each of the four areas divided in this way, there are roll diameter combination points having substantially the same secondary component margins. Of these, the third area is desirable. That is, the third region is the region where the rolling mill can be made the most compact.

As a more general idea, when the secondary component margin characteristic diagram is divided into four regions by two straight lines passing through substantially the center of the secondary component margin contour line group, the roll combination range in the third region is It can be said that it is very suitable for making the rolling mill compact. On the contrary, if the roll diameters are combined in the above-mentioned third region, it is possible to provide a secondary component margin substantially equivalent to the roll combination characteristics in the other regions and to make the rolling mill suitable compact. The above is a case of considering the secondary component margin characteristics.

Next, the fourth-order component margin characteristic will be described.
FIG. 9 shows the intermediate roll diameter on the horizontal axis and the quaternary component margin on the vertical axis under the same conditions as in FIG. 8 with the work roll diameter as a parameter. From this figure, it can be seen that regardless of the work roll diameter, when the intermediate roll diameter is approximately 450 mm or more, the quartic component margin amount hardly changes. From this, it can be said from the quaternary component margin characteristics that the quaternary component margin amount does not increase even if the intermediate roll diameter is 450 mm or more, which hinders the compacting of the rolling mill. Moreover, the intermediate roll diameter is substantially equal to the maximum diameter of the intermediate roll diameter in the third region. This indicates that determining the maximum diameter of the intermediate roll from the secondary component margin characteristic diagram is appropriate from the viewpoint of the fourth component margin characteristic. That is, considering the fourth-order component margin characteristic, it is desirable to set the third region. Furthermore, it can be seen from this figure that the smaller the work roll and intermediate roll diameters, the larger the quartic component margin. Therefore, it can be said that the third region in which the work rolls and the intermediate roll have a smaller diameter is more advantageous than the other regions in terms of the quaternary component margin. Such a quaternary component has the property of acting more strongly near the plate edge than the quadratic component. That is, it means that using the roll diameter combination range in the third region is more effective for edge drop and thermal crown control.

However, when the diameter of the intermediate roll is excessively reduced as compared with the diameter of the work roll, another problem occurs. Generally, there is an idea that the intermediate roll bender controls a secondary plate crown component, and the work roll bender controls a higher order component of the plate crown. This is to clarify the role of each roll bender on the plate crown and to facilitate actual control. For this purpose, it is preferable that the secondary component control amount of the intermediate roll bender is substantially equal to or larger than the secondary component control amount of the work roll bender. Therefore,
Considering the ratio (= A _w2 / A _i2 ) of the secondary component control amounts of the work roll bender and the intermediate roll bender, it is desired that this value does not greatly exceed 1.0. In order to study this, the characteristics of the ratio of the secondary component control amounts (hereinafter, secondary component ratio) are shown in FIG. 10 under the same conditions as in FIG. In FIG. 10, the horizontal axis is the work roll diameter and the vertical axis is the intermediate roll diameter, and the contour lines where the secondary component ratios are equal are represented by an altitude difference of 0.2 pitch. However, the combination range of each roll diameter is shown in FIG.
In the substantially third region, the straight line L in the figure indicates the point where the work roll diameter and the intermediate roll diameter are equal. Hereinafter, such a diagram is referred to as a secondary component ratio characteristic diagram. From this figure, it can be seen that when the work roll diameter is 375 mm or less on the straight line L, the secondary component ratio is approximately 1.2 or less. Therefore, in consideration of the ease of actual control, it can be said that the intermediate roll diameter is preferably equal to or larger than the work roll diameter. From the above, the range of use of the intermediate roll diameter is restricted to the work roll diameter or more. The straight line L shown in FIG. 8 illustrates the point where the diameter of the intermediate roll and the diameter of the work roll are equal. Therefore, the preferable combination range of the roll diameters is in the third region and above the straight line L.

Further, when considering the operational stability of the rolling mill, it is desirable to drive the work rolls. On the other hand, when the diameter of the work roll is reduced, the required rolling torque may not be directly transmitted to the work roll due to the strength of the drive system. At this time, the intermediate roll is driven. Therefore, the rolling torque required for the work rolls is given by the tangential force generated by the friction between the intermediate rolls and the work rolls. The tangential force generated on the work roll causes the work roll to bend in the horizontal direction. This means that the amount of bending in the horizontal direction fluctuates due to disturbance such as fluctuations in rolling torque, which becomes a factor that hinders stable operation and adversely affects the shape. In order to prevent this as much as possible, in many cases, for example, an offset mechanism or a support roll is installed on the work roll as shown in JP-A-5-50109 (US5406817). However, in this case, there is a problem that the structure becomes complicated and the manufacturing cost becomes high. Further, when such a rolling mill is applied to a so-called reverse rolling facility for repeatedly rolling in the reverse direction, it is necessary to change the offset position according to the rolling direction. This not only reduces the production amount of the rolling equipment, but also requires resetting such as adjustment of the rolling position according to the change of the offset position, which causes a problem of making the rolling operation difficult.

The work roll drive limit is generally determined by the fatigue strength of the drive system spindle. In addition, the required rolling torque is generally larger as the rolling is performed in a place where the plate thickness is thick.
For example, assuming the rolling of general carbon steel using the solvel rolling oil, the working roll diameter is 300 mm, the strip width is 1200 mm, the entry side strip thickness is 4 mm, and the rolling reduction is 50%. It was about 9.5 tons per line. The transmission torque allowed by the fatigue strength of the spindle that drives the work roll is about 10.0 t · m. Therefore, the minimum work roll diameter in this case is preferably 300 mm or more due to the constraint of the work roll drive.

In the following, it will be examined whether or not the above characteristics similarly hold when the diameter of the reinforcing roll, rolling with a soft or hard material, and the maximum plate width are changed. 11 to 1
3 shows rolling with a soft material, and FIGS. 14 to 17 show rolling with a hard material. The second-order component margin characteristic diagrams are shown when they are respectively equivalent to a 4-width mill. However, the reinforcing roll diameter Db is the value shown in each figure. The shaded area in the third area in the figure shows the same area as in FIG. From these figures, the smaller the reinforcing roll diameter is for both soft and hard materials, 1) the margin of secondary component decreases.

2) The maximum point region of the secondary component margin tends to move to the combined region on the large diameter side of the work roll and the intermediate roll diameter, but it does not change so much up to the reinforcing roll diameter of 1000 mm. . However, for hard materials, Db =
In the case of 850 mm, the maximum point region moves largely to the large diameter side.

As a result, the reinforcing roll diameter is at least 100.
Up to 0 mm, the secondary component margin amount obtained in the shaded area in the drawing includes a margin amount substantially equal to the margin amounts obtained in other regions. Therefore, if the reinforcing roll diameter is acceptable, it can be said that the roll diameter combination range of the shaded portion in the third region has a secondary component margin amount that is substantially the same as other regions and is suitable for downsizing of the rolling mill. .

On the other hand, when the hard material is Db = 850 mm as shown in FIG. 17, it is hard to say that the shaded area covers the margin amount obtained in the first area, for example. In such a case, it means that the combination of the three is unsuitable and is not useful for downsizing the rolling mill. Therefore, in terms of the secondary component margin characteristics, it can be said that the reinforcing roll diameter is preferably 1000 mm or more. Further studies on the compacting of the rolling mill, including the combination of the diameters of the reinforcing rolls, will be described later.

The above is the explanation from the secondary component margin characteristic. The fourth-order component margin characteristic will be described below. 18 and 19 show the fourth-order component margin characteristics in the case of a soft material and a hard material, with the horizontal axis representing the work roll diameter and the intermediate roll diameter Di.
Is shown as a parameter. The solid and dotted lines in the figure are for Db = 1300 and 1000 mm. Clearly from this figure, the smaller the working roll diameter and the intermediate roll diameter, the larger the quaternary component margin. Furthermore, even if the diameter of the intermediate roll is 450 mm or more, the quartic component margin hardly changes. The above characteristics do not show a large difference at least when the reinforcing roll diameter is 1000 mm or more. Therefore, also from this characteristic, it can be said that the intermediate roll diameter of 450 mm or less is preferable.

20 and 21 are characteristic diagrams of secondary component ratios in the soft material and the hard material when the diameter of the reinforcing roll is 1000 mm. Comparing the cases of the soft materials of FIG. 10 and FIG. 20, both have almost the same characteristics. From this, it can be seen that the secondary component ratio characteristics are hardly affected by the reinforcing roll diameter. On the other hand, FIGS.
Comparing these, it is clear that the hard material has a smaller secondary component ratio. Therefore, it can be said that the secondary component ratio characteristics should be studied in the case of a soft material. Due to the above, from FIG. 21, the straight line L having the same intermediate roll diameter and work roll diameter
With the above, 2 when the work roll diameter is 375 mm or less
The secondary component ratio is about 1.2 or less. For the same reason as described above, a region where the intermediate roll diameter is equal to or larger than the working roll diameter is set as the combined use range.

However, in an actual rolling mill, the use range of the minimum and maximum diameters of each roll is often allowed to be about 10 to 15%. Therefore, the maximum working roll diameter used is 300
When determined within the range of ˜375 mm, it is desirable that the minimum intermediate roll diameter is substantially equal to or larger than the maximum working roll diameter used as determined above.

To summarize the above description, when the diameter of the reinforcing roll is at least 1000 mm or more, the combined region of the work roll and the intermediate roll diameter is the third region. This allows
The secondary component margin obtained for the determined reinforcing roll diameter is similar to the case where other regions are used, and the quaternary component margin has characteristics more than those in other regions. It becomes possible to provide. Further, the work roll diameter is 3 in order to drive the work roll from the stability of rolling operation.
From the viewpoint of making it easier to control each roll bender, the intermediate roll diameter is equal to the work roll diameter,
Or set it to a larger range. From the above, it was understood that when the diameter of the reinforcing roll is 1000 mm or more, the shaded region shown on the secondary component margin characteristic diagram is a range suitable for providing a compact rolling mill. Further, the minimum intermediate roll diameter is preferably substantially equal to or larger than the maximum working roll diameter used, which is determined within the range of 300 to 375 mm. This clarifies the roles of the work roll and intermediate roll benders on the plate crown, and makes actual control easier. For example, the maximum working roll diameter used is 3
When the length is 75 mm, the minimum intermediate roll diameter is preferably 375 mm or more.

In order to further reduce the size, the diameter of the reinforcing roll may be reduced. Hereinafter, this limit will be described.

22 and 23, the work roll diameter is 350 mm.
As a result, the secondary and quaternary component margins are shown with the horizontal axis as the reinforcing roll diameter and the intermediate roll diameter as a parameter. 22 shows the characteristics of a soft material and FIG. 23 shows the characteristics of a hard material. From this figure, it can be seen that when the diameter of the reinforcing roll is reduced, the margin of the second-order component decreases and the margin of the fourth-order component increases. Further, even if the reinforcing roll diameter is set to 1300 mm or more, the secondary and quaternary component margins do not change significantly in any case.
Therefore, in order to provide a compact rolling mill, the diameter of the reinforcing roll is 1300 mm or less. On the other hand, in the case of the hard material of FIG. 23, the secondary component margin is almost zero or negative when the reinforcing roll diameter is 800 mm and the intermediate roll diameter is 350 mm or less. This means that the secondary component cannot be controlled sufficiently. Such a secondary component allowance differs depending on the combination with the intermediate roll diameter, but the reinforcing roll diameter is 9
If it is 00 mm or more, any of the fourth order component margins is positive. Therefore, the reinforcing roll diameter may be 900 mm or more in view of the quartic component margin characteristics. However, from the viewpoint of the secondary component margin characteristics, the reinforcing roll diameter is preferably 1000 mm or more as described above, and therefore the reinforcing roll diameter is 1000 mm or more.

The above description has been made for the case of a 4-width mill having a maximum plate width of 1200 mm. In the following, a case of a 5-width mill having a maximum plate width of 1500 mm will be described.
24 to 31 are secondary component margin characteristic diagrams corresponding to a 5-width mill. 24 to 27 show the case of a soft material, and FIG.
8 to 31 show the case of a hard material. The reinforcing roll diameter is
Each is shown in each figure. In this case, 2
It can be said that the characteristic characteristics are not so different, except that the maximum area of the secondary component margin characteristics moves to the larger diameter side of the work roll and the intermediate roll than in the case of a 4-width mill equivalent. Therefore, as the third area in this case, the intermediate roll diameter is 525 mm or less 35
The area where 0 mm or more, the work roll diameter is 425 mm or less and 350 mm or more, and Di ≧ Dw is shown by hatching. The method of taking the third area is the same as that for a 4-width mill. That is, the area dividing line of Dw = 425 mm and Di = 525 mm is a point passing through substantially the center of the secondary component margin contour line group. However, when the diameter of the reinforcing roll is 1000 mm, it is located outside the central portion, but in this case it indicates that the diameter of the reinforcing roll is too small.

The minimum work roll diameter was determined from the shape control characteristics. Generally, when the plate width is wide and the work roll diameter is small, the secondary component of the work roll bender may become negative. As an example, FIG. 32 shows the influence coefficient function of the work roll vendor. The condition is that the work roll diameter is 325 mm,
Intermediate roll and reinforcing roll diameters are 500 and 1150 mm, respectively
And calculated in the case of a hard material. The secondary and quaternary components of the work roll bender at this time are A _w2 = -10.21
μ, A _w4 = 136.42 μ. In FIG. 32, the plate crown data when the second-order and fourth-order components are obtained and the curve calculated by using the above-mentioned coefficient with a solid line are shown at the same time.
In this figure, it is difficult to understand due to the scaling, but the effect coefficient function value at the center of the plate is negative. That is, it can be said that when the work roll bending force is increased in the increase direction, the central portion of the plate has a function of generating a convex shape. In such a case, a composite stretched plate shape is likely to occur, and shape control becomes difficult. Therefore, in the case of a 5 width mill, the work roll diameter should be 350 mm or more in consideration of the above.

The quartic component margin characteristics are shown in FIGS. 33 and 34 with the horizontal roll as the intermediate roll diameter and the work roll diameter as a parameter. 33 shows a case of a soft material, and FIG. 34 shows a case of a hard material. From the figure, in the case of a 5 width mill, even if the diameter of the intermediate roll is about 525 mm or more, the margin of the quaternary component hardly changes, and in this sense, it can be said that there is no need to increase the diameter further. On the contrary, it is advantageous to set it below this in order to increase the margin of the fourth-order component.

Further, FIG. 35 shows an example of the secondary component ratio characteristic. The conditions are as follows: the reinforcing roll diameter is 1150 mm and the material is soft. From this figure, the work roll diameter is 4 on the straight line L.
When the thickness is 25 mm or less, the secondary component ratio is about 1.1 or less. Therefore, considering the ease of actual control, the range of use of the intermediate roll diameter is set to be equal to or larger than the work roll diameter, as in the case of the four-width mill. However, with respect to the minimum intermediate roll diameter, it is preferable that the minimum work roll diameter is substantially equal to or larger than the maximum work roll diameter determined in the range of the work roll diameter (= 350 to 425 mm), in the case of 4 width mill equivalent. Is the same as.

From the above, when the allowable reinforcing roll diameter is determined even in the case of a 5 width mill, by setting the combined area of the work roll and the intermediate roll diameter to the third area, other margins for the secondary component can be obtained. It was understood that it is possible to provide a compact rolling mill that has characteristics similar to those of the other regions with respect to the fourth-order component margin and that of the other regions. That is, when at least the reinforcing roll diameter is 1150 mm or more, it can be said that the shaded area shown on the secondary margin characteristic diagrams of FIGS. 24 to 31 is very suitable for making the rolling mill compact. .

In order to make the device more compact, the diameter of the reinforcing roll may be reduced, and this point will be described below. 36 and 37, the work roll diameter is 400 mm,
The secondary and quaternary component margins are shown when the reinforcing roll diameter is taken on the horizontal axis and the intermediate roll diameter is taken as a parameter. Further, FIG. 36 shows characteristics of a soft material and FIG. 37 shows characteristics of a hard material. From the figure, when the diameter of the reinforcing roll is made smaller, the secondary component margin decreases and the quaternary component margin increases conversely. Further, even if the diameter of the reinforcing roll is set to 1400 mm or more, the margins of the secondary and quaternary components do not change significantly in any case. Therefore, in order to provide a compact rolling mill, the reinforcing roll diameter is 1400 mm or less. Also in FIG.
In the hard material of No. 2, when the reinforcing roll diameter is 1000 mm and the intermediate roll diameter is 350 mm, the secondary component margin is negative. This means that the secondary component cannot be controlled sufficiently. Such a secondary component allowance varies depending on the combination with the intermediate roll diameter, but any secondary component allowance is positive if the reinforcing roll diameter is 1100 mm or more.
Therefore, the diameter of the reinforcing roll is 1100 mm or more.

In summary, the maximum usable plate width is 1200.
In the case of mm, the combination conditions of roll diameter are as follows: 1) Working roll diameter Dw is 300 mm or more and 375 mm or less.

If the maximum working roll diameter determined within the above range 1) is MAX (Dw), 2) the intermediate roll diameter Di is 450 mm or less and Di ≧ MA.
A range that satisfies X (Dw).

3) The reinforcing roll diameter Db is 1000 mm or more and 1300 mm or less.

Further, when the maximum usable plate width is 1500 mm, 4) the work roll diameter Dw is 350 mm or more and 425 mm or less.

If the maximum working roll diameter used in the above 4) is MAX (Dw), 5) the intermediate roll diameter Di is 525 mm or less and Di ≧ MA.
A range that satisfies X (Dw).

6) The reinforcing roll diameter Db is 1100 mm or more and 1400 mm or less. Therefore, it can be said that the above range is suitable.

The above relationship is represented by a mathematical expression using the following symbols.

Wmax: Maximum use width (mm) DwMax (DwMin): Maximum (minimum) work roll diameter (mm) when maximum use width is Wmax DiMax (DiMin): When maximum use width is Wmax Maximum (minimum) intermediate roll diameter (mm) DbMax (DbMin): When the maximum usable plate width is Wmax, assuming the maximum (minimum) reinforcing roll diameter (mm), the conditions 1) and 4) The minimum and maximum roll diameter are DwMax = 375 + 50 × (Wmax-1200) / 300 (9) DwMin = 300 + 50 × (Wmax-1200) / 300 (10) Similarly, maximum and minimum reinforcement with the maximum plate width Wmax used as a variable. Regarding roll diameter, condition 3)
And 6), DbMax = 1300 + 100 × (Wmax-1200) / 300 (11) DbMin = 1000 + 100 × (Wmax-1200) / 300 (12) Regarding the maximum and minimum intermediate roll diameters, from Conditions 2) and 4), DiMax = 450 + 75 × (Wmax-1200) / 300 (13) DiMin = MAX (Dw) (14) However, MAX (Dw) is the maximum working roll diameter used, which is determined within the range of the expressions (9) and (10).

In the above relationship, the horizontal axis represents the maximum usable plate width,
Graphs in which the vertical axis represents the maximum and minimum roll diameters are shown by the solid lines in FIGS. 1 and 2. In the figure, the straight line A is the minimum work (intermediate) roll diameter of the formula (10), the straight line B is the maximum work roll diameter of the formula (9), the straight line C is the maximum intermediate roll diameter of the formula (13), and the straight lines D and E are The minimum and maximum reinforcing roll diameters of equations (12) and (11) are shown. From the above, when the maximum usable plate width is specified, the working range of the work roll diameter is determined within the range of straight lines A and B in FIG. 1, and the working range of the intermediate roll diameter is (1
4) the minimum roll diameter determined by the equation and not more than C,
The use range of the reinforcing roll diameter is D or more and E or less.
If such a combination range of roll diameters is used, 2
The secondary component margin characteristics are almost the same as those that can be achieved with the selected reinforcing roll diameter, and the fourth component margin characteristics are equal or higher, and it is possible to provide a compact rolling mill. It is clear from the explanation above. Further, it is important to determine the use range of each roll diameter so as to be limited to the above range. This makes it possible to provide a compact rolling mill that maintains the above characteristics in the entire range of use combinations of roll diameters.

Further, to make the rolling mill compact,
Considered below. As described above, the use range of each roll diameter in an actual rolling mill often allows about 10 to 15%. In the following, it is assumed that about 15% is allowed. Therefore, if the minimum working roll diameters for 4 and 5 width mills are 300 and 350 mm respectively, the maximum roll diameters at this time are 300 x 1.15 respectively.
˜350 mm and 350 × 1.15 to 400 mm. However, the values are rounded appropriately. Dotted line B'in FIG.
Represents a straight line passing through the above two points. If the maximum working roll diameter used at this time is expressed as DwMAX by an equation, DwMAX = 350 + 50 × (Wmax-1200) / 300 (15). The maximum roll diameter of the intermediate roll DiMAX
For the maximum work roll diameter of conditions 1) and 4),
If conditions 2) and 5) are always satisfied, 375 × 1.15 to 425 respectively for 4 width and 5 width mills.
mm and 425 × 1.15 to 500 mm. A straight line C ′ passing through the above two points is shown by a dotted line in FIG. If the above straight line is expressed by an equation, DiMAX = 425 + 75 × (Wmax-1200) / 300 (16) Similarly, the maximum roll diameter DbMAX used for the reinforcing roll is 1000 × using the minimum roll diameter of the conditions 3) and 6).
1.15 ~ 1150 mm and 1100 x 1.15 ~ 125
It will be 0 mm. A straight line E ′ shown by a dotted line in FIG. 2 is a straight line passing through the above two points. Similarly, when the above is expressed by an equation, DbMAX = 1150 + 100 × (Wmax-1200) / 300 (17). It is obvious that if the maximum roll diameter used for each roll is the roll diameter represented by the above dotted line, it is possible to provide a more compact rolling mill. Therefore, the combination range of the roll diameters used in this case is a straight line A or more and B'or less for the working roll diameter, a straight line B or more and C'or less for the intermediate roll diameter, and a straight line D or more and E'for the reinforcing roll diameter. Below, it will be decided in. It can be said that the above gives a compact mill specification that is close to the limit when the usage range of each roll is 15%.

The above is due to the reduction of the diameter of each roll used,
The compacting of the rolling mill was explained. Further, it goes without saying that the mill housing can be made compact by reducing the diameter of each roll used. As a result, the manufacturing cost of the mill housing can be reduced. Also, shortening the length of the mill housing can reduce the required height of the factory building. That is, the height required to normally carry in and install the mill housing is the minimum required as the height of the factory building.
On the other hand, if the mill housing is shortened, the required height can be reduced. This makes it possible to reduce the cost of building a factory building. Further, it is natural that the transportation cost can be reduced. Further, the load fluctuation is small, and the vibration of the housing can be suppressed.

From the above, it can be said that shortening the mill housing length largely contributes to the reduction of the total plant construction cost. It is clear that the length of such a mill housing is approximately proportional to the sum of the roll diameters.
Therefore, the sum of the roll diameters is a suitable index (hereinafter referred to as a compaction index) indicating compactness of the mill. Therefore, these are added by the equations (15) to (17),
Considering the compaction index S, S = 1925 + 225 × (Wmax-1200) / 300 (18). The compaction index S of the above formula (18) is a value in a compacted mill that is close to the limit when the use range of each roll is clearly set to 15%. Therefore, the compaction index S, which is a measure of compacting the rolling mill, is
Equation (18) or less is desirable. The graph of Equation 18 is shown by the straight line S in FIG. However, in this case, each roll diameter is selected within the range of the expressions (9) to (14). Therefore, the sum of the maximum work roll diameter and the maximum intermediate roll diameter at this time is the sum of equations (9) and (13), and is similarly shown by the solid line B + C in FIG. To make it more compact, it is sufficient to add equations (15) and (16), which is shown by the dotted line B '+ C' in FIG. If you do this,
It is possible to provide a rolling mill that can keep the compaction index as small as possible and can maintain the secondary and quaternary component margin characteristics that are substantially equal to or higher than the characteristics that can be achieved with the selected reinforcing roll diameter. . However, it goes without saying that the compaction index S is equal to or larger than the sum of the minimum intermediate roll diameters determined by the equations (10), (12) and (14).

The compaction index S becomes essentially important when the existing 4-high rolling mill is converted into a 6-high rolling mill, for example. That is, in order to reduce the cost of modification as much as possible, it is effective to divert the housing of the existing rolling mill. To this end, the compacting index S of the existing rolling mill is
The compaction index S of the modified 6-high rolling mill must be substantially the same or small. According to the present invention, the compaction index S of the 6-high rolling mill is kept as small as possible, and
Regarding the secondary and quaternary component margin characteristics, it can be said that it is particularly suitable for the above-mentioned modification because it can maintain characteristics that are substantially equal to or higher than the characteristics that can be achieved with the selected reinforcing roll diameter.

In the above explanation, the roll crown is not attached to all the rolls and the straight roll is used. In this case, the minimum diameter of the reinforcing roll was determined so that the secondary component margin does not become negative, especially when it corresponds to a 5-width mill. A means for increasing such a secondary component margin is
Various methods other than roll bending are possible.
For example, the reinforcing roll is provided with a convex crown that is gradually tapered from the center of the roll toward the end of the roll, and has a substantially quadratic curved shape. By doing so, the secondary component of the reference plate crown is reduced, and as a result, the secondary component margin can be increased, so that it is obvious that the diameter of the reinforcing roll can be further reduced. Naturally, the same effect can be obtained by applying the roll crown as described above to rolls other than the reinforcing roll. However, when the crown roll is used, there is a problem that the roll polishing work becomes difficult. Further, when the small diameter reinforcing roll is used, the change of the plate crown with respect to the change of rolling load is naturally large, and the rolling stability in this sense is deteriorated. Further, the fatigue strength of the roll neck, the bearing life, etc. are also reduced, and it can be said that there is a limit to the minimum reinforcing roll diameter even when a crown roll is used.

However, as described above, especially for a remodeling project, it becomes significant to reduce the remodeling cost as much as possible by reducing the compaction index S by the above method or the like. Furthermore, if the rolling load of each pass can be reduced by increasing the number of rolling passes, such as rolling equipment mainly for rolling soft material and reversible rolling equipment, the minimum of the reinforcing roll diameter The value may be used in the expression (12) or less. Particularly when a straight roll is used, which is equivalent to a 4-width mill using a soft material, it is apparent from the secondary component margin characteristic diagram of FIG. 13 and the reinforcing roll diameter and secondary component margin characteristic shown in FIG. It can be seen that a diameter of 900 mm can be applied without any problem. In such a case, the sum of the maximum working roll diameter used and the maximum intermediate roll diameter used is the straight line B + C or less in FIG.
A rolling mill can be used in which the diameter of the reinforcing roll is as small as possible under the condition that B ′ + C ′ or less and the compacting index S of the rolling mill is set to (18) or less. This makes it possible to provide a very compact rolling mill.

FIG. 38 shows a case where the rolling mill as described above is applied to a batch type tandem rolling mill. The rolled material 1 is set in the unwinder 17 and unwound, and the incoming pinch roll 1
It is conveyed in the direction of four rolling mills M1 to M4 installed via 8 and continuously rolled. The rolled material 1 after rolling is used as rolling equipment which is wound by a winding machine 20 via a delivery pinch roll 19. In such a rolling facility, it is necessary to perform rolling with a limited number of rollings by the installed rolling mill. Therefore, there is a general need for strong reduction.
In such a case, it is usual to carry out a strong reduction in the former rolling mill and a comparatively light reduction in the latter rolling, particularly the final rolling mill, which mainly controls the shape. It can be said that the rolling torque becomes larger in the former stage than in the latter rolling mill. Further, in the batch type tandem rolling mill, each time a new rolling coil is installed, each roll is repeatedly bitten and threaded. At this time, the work roll has a small diameter,
When the entry side plate thickness is as thick as about 3 to 4 mm, the rolled material may not be caught in the roll when rolled with a large reduction amount. As described above, the large diameter of the work roll is preferable from the viewpoint of transmission of a large torque and relaxation of the restriction on the bite. From the above, in the tandem rolling equipment, especially in the batch type rolling equipment, the rolling mill in the first stage is more
It may be advantageous to make the work roll larger in diameter. In this sense, the work roll diameters of the preceding rolling mills M1 to M2 in FIG. 38 are, for example, in the case of a four-width equivalent mill, the working roll diameter range of 340 to 375 mm, and the working roll diameters of the succeeding rolling mills M3 to M4 are, for example, 325 to. It is considered to be used in the roll diameter range of 350 mm. Further, in this case, for example, when the work roll diameter of the former stage becomes 340 mm or less, which is the minimum, by using this in the mill of the latter stage, it can be further used until it reaches the minimum roll diameter of the latter mill. That is, this corresponds to the expansion of the range of use of the diameter of the actual work roll, and the work roll can be used efficiently. Further, if the sum of the maximum work roll diameter and the maximum intermediate roll diameter is set to the same value in the front and rear stages, it means that the rear intermediate roll diameter is larger than the front intermediate roll diameter. At this time, when the diameter of the intermediate roll in the subsequent stage reaches the allowable minimum diameter, this can be diverted to the rolling mill in the previous stage. Therefore, it can be said that the intermediate roll can be efficiently used. Further, increasing the diameter of the intermediate roll in the latter stage obviously means that the secondary component ratio becomes smaller in the latter stage. This has the effect of ensuring the shape control in the rolling mill at the subsequent stage, as described in the above description. By applying the rolling mill according to the present invention as described above, it can be said that the tandem rolling mill can be effectively made compact.

FIG. 39 shows a case where the rolling mill according to the present invention is applied to a reversible cold rolling facility. The rolling coil 1 is first set on the unwinder 21 and conveyed to the rolling machine M1 via the pinch rolls 22 and the like. The rolled material 1 continuously rolled by the rolling mill M1 is wound up by the winding and unwinding machine 23 installed on the delivery side, and when the trailing end of the rolled material reaches the completion of rolling or immediately before the completion of rolling, it is immediately rolled in the opposite direction. While being wound, it is wound up by the winding and unwinding machine 24 installed on the entrance side. At this time, the rolling of the rolled material 1 of the normal take-up winding machine 23 is stopped before the entire material is unwound, and the next reverse rolling is immediately performed. In such a reversible rolling facility, the number of rolling passes can be increased as long as the reduction in the production amount is allowed. Therefore, by increasing the number of rolling passes, it is possible to set a schedule for reducing the rolling load, rolling torque, etc. of each pass. On the contrary, if the above is possible, the reinforcing roll diameter can be used particularly on the smaller diameter side as described above. That is, the sum of the maximum working roll diameter and the maximum intermediate roll diameter is set to a straight line B + C or less, preferably B ′ + C ′ or less in FIG. 3 according to the maximum sheet width to be used, and the compacting index S of the rolling mill is set to ( A rolling mill can be used in which the diameter of the reinforcing roll is as small as possible under the condition of formula 18 or less. This makes it possible to provide a very compact reversible rolling mill.

The above description is for the case where a straight roll is used, in which each roll does not give a crown. However, the present invention can be applied to a 6-high rolling mill in which a gradually decreasing local crown is provided in the vicinity of one movable work roll end. The local crown in the rolling mill controls the edge drop that occurs near the plate edge. On the other hand, the plate crown in the entire width direction of the rolled material plate is performed by the work roll and the intermediate roll bender, and this function and effect are substantially the same as those of the present invention. Further, the 6-high rolling mill according to the present invention can be provided with a locally crowned taper near the end of one movable work roll. In this case, the thermal crown generated near the plate edge is controlled. Any of the rolling mills described above is used for the purpose of controlling a local strip crown that strongly occurs near the strip edge. When controlling such a local plate crown, it is preferable that the work roll diameter is small. That is, by reducing the diameter of the work roll, the work roll bender can have a larger quaternary control component, and the control in the vicinity of the plate edge becomes reliable. Therefore, as is apparent from the above description, according to the present invention, by appropriately combining the roll diameters, it is possible to effectively reduce the work roll diameter, so it is also very effective for edge drop and thermal crown control. It can be said to be effective. By applying such a rolling mill to a rolling mill having a local roll crown at the work roll end, it is obvious that the control effect of the plate edge can be further enhanced.

Further, the essential effect of the present invention is brought about by the characteristics of the work roll bender and the intermediate roll bender. Therefore, for a rolling mill without the above control means, a six-high rolling mill is out of the scope of the present invention. For example, this is the case when a rolling mill that crosses intermediate rolls does not have an intermediate roll bender. In such a rolling mill,
The secondary component margin characteristic is determined by the cross amount of the intermediate roll regardless of the diameter of the intermediate roll. Therefore, the maximal characteristics of the work roll and intermediate roll diameter clarified in the present invention, which are caused by the combined use, do not occur. However, even in the above rolling mill, the present invention can be applied when both the working roll bender and the intermediate roll bender are installed.

[0073]

According to the present invention, it is possible to provide a compact rolling mill and rolling equipment having an appropriate plate crown controllability.

[Brief description of drawings]

FIG. 1 is a diagram showing a relationship between a plate width and roll diameters according to an embodiment of the present invention.

FIG. 2 is a diagram showing a relationship between a plate width and a reinforcing roll diameter according to an embodiment of the present invention.

FIG. 3 is a diagram showing a relationship between a plate width and a roll diameter, which is an embodiment of the present invention.

FIG. 4 is a lateral view of a 6-high rolling mill that is an embodiment of the present invention.

FIG. 5 is a vertical cross-sectional view of a 6-high rolling mill that is an embodiment of the present invention.

FIG. 6 is a top view of a six-high rolling mill which is an embodiment of the present invention.

FIG. 7 is a diagram showing a relationship between work roll diameter and rolling linear pressure.

FIG. 8 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 9 is a fourth-order component margin characteristic diagram at a plate width of 1200 mm.

FIG. 10 is a secondary component ratio characteristic diagram with a plate width of 1200 mm.

FIG. 11 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 12 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 13 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 14 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 15 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 16 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 17 is a secondary component margin characteristic diagram at a plate width of 1200 mm.

FIG. 18 is a fourth-order component margin characteristic diagram at a plate width of 1200 mm.

FIG. 19 is a fourth-order component margin characteristic diagram at a plate width of 1200 mm.

FIG. 20 is a secondary component ratio characteristic diagram with a plate width of 1200 mm.

FIG. 21 is a secondary component ratio characteristic diagram at a plate width of 1200 mm.

22 is a reinforcing roll diameter and a secondary and quaternary component margin characteristic diagram at a plate width of 1200 mm. FIG.

FIG. 23 is a diagram showing the reinforcing roll diameter and the secondary and quaternary component margin characteristics at a plate width of 1200 mm.

FIG. 24 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 25 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 26 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 27 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 28 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 29 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 30 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 31 is a secondary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 32 is an explanatory diagram of plate crown data and a work roll vendor influence function.

FIG. 33 is a fourth-order component margin characteristic diagram at a plate width of 1500 mm.

FIG. 34 is a fourth-order component margin characteristic diagram at a plate width of 1500 mm.

FIG. 35 is a secondary component ratio characteristic diagram at a plate width of 1500 mm.

FIG. 36 is a reinforcing roll diameter and a secondary and quaternary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 37 is a reinforcement roll diameter and a secondary and quaternary component margin characteristic diagram at a plate width of 1500 mm.

FIG. 38 is a view showing a cold tandem rolling facility.

FIG. 39 is a view showing a reversible cold rolling facility.

FIG. 40 is a schematic diagram illustrating a plate crown.

[Explanation of symbols]

DESCRIPTION OF SYMBOLS 1 ... Rolled material, 2 ... Work roll, 3 ... Intermediate roll, 4 ... Reinforcing roll, 5 ... Housing, 6 ... Reinforcing roll bearing box, 7
... hydraulic pressure reduction device, 8 ... work roll bearing box, 9 ... intermediate roll bearing box, 10 ... work roll bending device, 11 ...
Intermediate roll bending device 12, shift support member 12,
13 ... Shift head, 14 ... Shift hook, 15 ... Coupling cylinder, 16 ... Shift cylinder, 17, 21 ... Unwinder, 18, 19, 22 ... Pinch roll, 20 ... Winder,
23, 24 ... Winding and unwinding machine.

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kenji Horii             4-6 Kanda Surugadai, Chiyoda-ku, Tokyo             Within Hitachi, Ltd. (72) Inventor Hideo Kobayashi             4-6 Kanda Surugadai, Chiyoda-ku, Tokyo             Within Hitachi, Ltd. (72) Inventor Hirokazu Nakamae             4-6 Kanda Surugadai, Chiyoda-ku, Tokyo             Within Hitachi, Ltd. (72) Inventor Koichi Matsumoto             4-6 Kanda Surugadai, Chiyoda-ku, Tokyo             Within Hitachi, Ltd. (72) Inventor Shigekazu Yamada             4-6 Kanda Surugadai, Chiyoda-ku, Tokyo             Within Hitachi, Ltd.

Claims (13)

[Claims] 1. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, the work roll and the A roll bending device that applies a bending force to each of the intermediate rolls is provided, and when the maximum usable plate width of the rolled material is Wmax (mm), the diameter Dw of the work roll is 300 + 50 × (Wmax-1200) / 300 ≦ Dw ≦ 3
75 + 50 × (Wmax-1200) / 300, and the diameter Di of the intermediate roll is Dw ≦ Di ≦ 450 + 75 × (Wmax-1200) / 3
The rolling mill is characterized in that a work roll drive device for rotating and driving the work roll is provided. 2. The work roll diameter according to claim 1, wherein a diameter Dw of the work roll is 300 + 50 × (Wmax-1200) / 300 ≦ Dw ≦ 3.
A rolling mill having a range of 50 + 50 × (Wmax-1200) / 300. 3. The intermediate roll diameter Di according to claim 1, wherein Dw ≦ Di ≦ 425 + 75 × (Wmax-1200) / 3.
A rolling mill having a range of 00. 4. The diameter Db of the reinforcing roll according to claim 1, which is 1000 + 100 × (Wmax-1200) / 300 ≦ D.
A rolling mill having a range of b ≦ 1300 + 100 × (Wmax-1200) / 300. 5. The diameter Db of the reinforcing roll according to claim 1, wherein 1000 + 100 × (Wmax-1200) / 300 ≦ D
A rolling mill having a range of b ≦ 1150 + 100 × (Wmax-1200) / 300. 6. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, the work roll and the A roll bending device that applies a bending force to each of the intermediate rolls is provided, and when the maximum usable plate width of the rolled material is Wmax (mm), the sum of the diameter Dw of the work roll and the diameter Di of the intermediate roll is obtained. 650 + 100 × (Wmax-1200) / 300 ≦ Dw
+ Di ≦ 825 + 125 × (Wmax-1200) / 30
A rolling mill having a range of 0 and a work roll drive device for rotationally driving the work roll. 7. The method according to claim 6, wherein the sum of the diameter Dw of the work roll and the diameter Di of the intermediate roll is 675 + 100 × (Wmax-1200) / 300 ≦ Dw.
+ Di ≦ 775 + 125 × (Wmax-1200) / 30
A rolling mill having a range of 0. 8. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, and an axis of the intermediate rolls. A moving device that moves in the direction, and a roll bending device that applies a bending force to each of the work roll and the intermediate roll, and when the maximum usable plate width of the rolled material is Wmax (mm), The sum of the diameter Dw, the diameter Di of the intermediate roll and the diameter Db of the reinforcing roll is Dw + Di + Db ≦ 1925 + 225 × (Wmax-12
00) / 300 and is provided with a work roll drive device for rotationally driving the work roll. 9. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls respectively supporting the work rolls, a pair of upper and lower reinforcing rolls respectively supporting the intermediate rolls, and an axis of the intermediate rolls. A moving device that moves in the direction, and a roll bending device that applies a bending force to each of the work roll and the intermediate roll, and when the maximum usable plate width of the rolled material is Wmax (mm), The diameter Dw is in the range of 300 + 50 × (Wmax-1200) / 300 ≦ Dw, the diameter Di of the intermediate roll is in the range of Dw ≦ Di, and the diameter Dw of the work roll and the diameter D of the intermediate roll are
The sum of i and the diameter Db of the reinforcing roll is Dw + Di + Db ≦ 1925 + 225 × (Wmax-12
00) / 300 and a work roll driving device for rotating and driving the work roll is provided. 10. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, the work roll and the A roll bending device that applies a bending force to each of the intermediate rolls is provided, and when the maximum usable plate width of the rolled material is Wmax (mm), the diameter Dw of the work roll is 300 + 50 × (Wmax-1200) / 300 ≦ Dw ≦ 3
75 + 50 × (Wmax-1200) / 300, and the diameter Di of the intermediate roll is Dw ≦ Di ≦ 450 + 75 × (Wmax-1200) / 3
Tandem type rolling mill having at least one rolling mill provided with a work roll driving device for rotating and driving the work roll. 11. A pair of upper and lower work rolls for rolling a rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls, a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, the work roll and the A roll bending device that applies a bending force to each of the intermediate rolls is provided, and when the maximum usable plate width of the rolled material is Wmax (mm), the diameter Dw of the work roll is 300 + 50 × (Wmax-1200) / 300 ≦ Dw ≦ 3
75 + 50 × (Wmax-1200) / 300, and the diameter Di of the intermediate roll is Dw ≦ Di ≦ 450 + 75 × (Wmax-1200) / 3
Reversible rolling equipment having a range of 00 and a work roll driving device capable of reversibly rotating and driving the work roll. 12. A rolled material comprising a pair of upper and lower work rolls for rolling the rolled material, a pair of upper and lower intermediate rolls for supporting the work rolls respectively, and a pair of upper and lower reinforcing rolls for supporting the intermediate rolls, respectively. When the maximum usable plate width of No. 3 is Wmax (mm), the diameter Dw of the work roll is 300 + 50 × (Wmax-1200) / 300 ≦ Dw ≦ 3
75 + 50 × (Wmax-1200) / 300, and the diameter Di of the intermediate roll is Dw ≦ Di ≦ 450 + 75 × (Wmax-1200) / 30
A rolling method for a rolling mill having a range of 0, characterized in that the work roll is rotationally driven, and a bending force is applied to each of the work roll and the intermediate roll to control the plate crown of the rolled material. Rolling method. 13. A method of remodeling a four-high rolling mill having a housing into a six-high rolling mill, wherein a housing of the four-high rolling mill is used for the modified six-high rolling mill, and a plate of rolled material is used. A method of remodeling a rolling mill, characterized in that a compaction index of each rolling mill is obtained based on the crown control characteristic, and the rolling mill is remodeled into a 6-high rolling mill having a compaction index less than or equal to the compacting index of the 4-high rolling mill.