JPS6228018A - Rolling mill - Google Patents

Abstract

PURPOSE:To adjust each roll gap separately and to stabilize a rolling work by providing a liquid cylinder for pressurizing a work roll on a backup roll and by equipping driving and controlling mechanisms for adjusting a gap at one position of work roll gap. CONSTITUTION:At the rolling, a target value 26 of the 2nd roll gap 22 is given to a control device 27 and by the liquid cylinders 19, 20 rolling loads are applied on each roll 12-15 through the backup rolls 11, 16. When the rolling load is varied, a signal of the 2nd roll gap 22 detected by a detector 25 and the target value are compared and calculated by the control device 27, then according to its deflection, a command is outputted from the control device 27 to the driving mechanism 24 to control the 2nd roll gap to be settled. In this case, the adjustment of the 1st and 3rd roll gaps 21, 23 is performed by the liquid cylinders 19, 20 and the 1st-3rd roll gaps are independently varied, respectively.

Description

Detailed Description of the Invention [Field of Industrial Application] The present invention relates to a rolling mill for rolling metal strip material (hereinafter referred to as rolled material), and particularly to a rolling mill that is capable of rolling multiple buses per stand.・It is related to rolling mill.

[Prior Art] Recently, as shown in FIG.
ing (rawing) rolling methods have been developed to reduce the size of rolling mills, reduce roll wear, roll hard materials such as high-strength steel, and reduce edge drop.

Further, as an improvement to the above RD rolling method, a rolling mill as shown in FIG. 8 has been proposed. FIG. 8 shows a rolling mill capable of rolling three buses per stand.
, 6, 7, 8, 9° 10 are slidably attached in this order from below in the vertical direction along the vertically extending edge wall of the window 4, and the roll chocks 6, 7, . Work rolls 12, 13, 14.15 are rotatably supported on L9, and backup rolls 11, 16 are rotatably supported on roll chock 5.10.

In this one-stand three-bath mill, the rolled material S is wound around each work roll 12, 13, 14.15, and while the work rolls 12, 13, 14.15' are rotated at different circumferential speeds, a backup roll, 11°16
Press down. Thus, the rolled material S is rolled on the work roll 12.1.
3 bus (first bus), bus between work rolls 13 and 14 (second bus), bus between work rolls 14 and 15 (
3rd bus). During this time, work roll 12.
1st stage rolling by work rolls 13, 14, 3rd stage rolling by work rolls 14 and 15.
Rolling of stages is performed simultaneously on one stand.

In addition, instead of winding the rolled material around the work roll, pull-out rolls 17 and 18 are provided as shown in FIG.
A rolling mill has also been proposed in which the material is rolled via the pull-out rolls 17, 18 without being wound around the work rolls 12, 13, 14, 15.

In the above-mentioned meat rolling machine, the thickness of the rolled material S is increased by the first stage of rolling. The plate thickness is changed from hl to hl by the second rolling, and the plate thickness is changed from hl to hl by the third rolling.
h3.

Therefore, the rolling reduction ratio of one stand in such a one-stand three-pass mill is expressed as: Compared with the one-stand one-pass mill, it is possible to perform high reduction rolling with a lower rolling load, and has excellent productivity. It has the advantage of being suitable for downsizing.

[Problems to be Solved by the Invention] However, in each of the above-mentioned rolling mills, the load applied to the backup rolls 11 and 16 acts equally on each work roll, and the rolling load in the first bus, second bus, and third bus is Since they are both equal, there is the following difficulty.

In other words, when performing control to guarantee plate thickness accuracy using rolling down control, load fluctuations associated with rolling down control immediately result in load fluctuations in all buses, and sheet thicknesses h1 and hl also constantly vary in accordance with load fluctuations, resulting in Precisely keeping the side plate thickness h3 constant is at least the reduction AGC (Δautoma
Controlling only ticQ aQ (3C0ntrO+) was nearly useless.

In addition, when controlling the plate thickness by controlling the tension applied to the rolled material S (output side tension, input side tension, or tension between buses), in other words, when performing GC on the tension, load control is performed as a result. However, it has the same difficulties as above.

Furthermore, the same applies when controlling the plate thickness by limiting the load due to the effect of different speeds of work rolls for each bus.

Furthermore, in the case of the rolling mill shown in FIG. 8, depending on the rolling conditions, as shown in FIG. There is also the problem that it can break.

Incidentally, this situation is not limited to only one-stand three-bath mills, but is common to conventional one-stand multi-bath mills.

The present invention has been made with the object of providing a rolling mill that can eliminate the above-mentioned drawbacks of the one-stand multi-bus mill, and can maximize the advantages of the one-stand multi-bus mill.

[Means for Solving the Problems] The present invention provides a rolling mill that is equipped with three or more work rolls per stand and is capable of simultaneously rolling a rolled material by passing it between two or more work rolls. A drive mechanism in which a hydraulic cylinder for pressurizing the work rolls is provided between a roll chock that supports the final loaded roll and a rolling mill housing post, and the drive mechanism adjusts the roll gap at at least one of the roll gaps of the intermediate work rolls. and a control mechanism for giving a command to the drive mechanism to maintain the roll gap constant.

[Function] Therefore, in the present invention, when the roll gap of a predetermined work roll deviates from the target value due to fluctuations in rolling load, a command signal is output from the control mechanism to the drive mechanism, and the drive mechanism operates to reduce the roll gap. The work rolls are adjusted almost independently so that they are held constant.

[Example] Hereinafter, an example of the present invention will be described with reference to the accompanying drawings.

In the embodiments of the present invention, the same parts as shown in FIGS. 7 and 8 are given the same reference numerals.

FIG. 1 shows a first embodiment of the present invention, in which a hydraulic cylinder 19 is disposed in the lower cross member of the housing post 3, and the hydraulic cylinder 19 is configured to act as a reduction blade on a roll chock 5 that pivotally supports a backup roll 11. A roll chock 1 with a backup roll 16 pivotally mounted on the upper cross member of the housing boss 3
A hydraulic cylinder 20 is disposed so as to apply a reduction blade to the cylinder 0.

The rolling mill S is inserted into a 10th wheel gap 21 formed between the work rolls 12 and 13, and the work roll 13
After being wound around the work roll 14, the 20th loop gap 22 formed between the work rolls 13 and 14 is inserted, and the 30th loop formed between the work rolls 14 and 15 is further wound around the work roll 14. - It is designed to be inserted through the ring gap 23.

Roll chock that pivots the work rolls 13 and 14 7.
A drive mechanism 24 is provided between the roll gap detector 25 and the drive mechanism 24 for keeping the 20th wheel gap 2'2 constant even when the rolling load changes. Roll gap and preset 20th
A control device 27 compares and calculates a target value 26 for the roll gap 22, and if there is a deviation between the detected roll gap and the target value, a command signal can be output to the drive mechanism 24.

When rolling is performed, the target value 26 of the 20th roll gap 22 is given to the control device 27, and the hydraulic cylinder 19.20 controls the roll chock 5.10 and the backup roll 1.
A rolling load is applied to each roll 12, 13, 14, 15 through 1, 16.

When the roll gap of the 20th roll gap is within the target value, since the deviation between the roll gap detected by the roll gap detector 25 and the target value is zero, the controller 2
No command signal is output from 7. However, when the rolling load fluctuates, the roll gap signal of the 20th wheel gap 22 detected by the 20th wheel gap detector 25 and the target value are compared and calculated by the control device 27, and the control device 27 outputs a signal according to the deviation. A command signal is output to the drive mechanism 24, and the drive mechanism 24 is operated to adjust the roll gap of the 20th roll gap 22 to be constant. When the roll gap reaches the target value, the control device 27 no longer outputs the command signal, so the drive mechanism 24 stops. Further, roll gap adjustment of the first and 30th roll gaps 21.23 during such rolling is performed by a hydraulic cylinder 19.20 and a υIWJ device (not shown). In addition, as the above-mentioned drive mechanism 24, arbitrary types, such as an electric type and a hydraulic type, can be used.

In this way, by controlling the 20th-hole gap 22 to be held constant, the 1st and 30th-hole gaps 2
Each roll gap of 1.23 can be controlled separately and easily.

In other words, the 1st, 2nd, 30th - gap 21.2
2.23 can be changed independently, especially the plate j in the third gap 23 which is the final bus.
can be directly controlled.

Figure 2 shows a second embodiment of the present invention, in which the roll chock 7.8
A hydraulic cylinder 28 is disposed between the hydraulic cylinders 28 and 28.
The lower surface of the cylinder body is attached to the roll chock 7,
The upper end of the piston rod is attached to a roll chock 8. This hydraulic cylinder 28 may be installed upside down.

Also, the command signal from the control 3'II device 27 is sent to the servo valve 2.
9, and the amount of pressure fluid flowing into and out of the hydraulic cylinder 28 can be controlled by a servo valve 29.

When the roll gap of the 20th roll gap 22 deviates from the target value, the deviation between the detection signal detected by the roll gap detector 25 and the target value is compared and calculated by the control gJ device 27, and the control is performed according to the deviation. a device 27 to servo valve 29
A command signal is output to the servo valve 29 and the hydraulic cylinder 2.
The roll gap of the 20th roll gap 22 is adjusted by controlling the inflow and outflow of pressurized liquid to the roll gap 22. Law Luga;
When y reaches the target value, the control device 27 does not output a command signal, so the servo valve 29 closes and the hydraulic cylinder 28 stops.

FIG. 3 shows a third embodiment of the present invention, in which the lower surface of the cylinder body of the hydraulic cylinder 28 is supported by a support portion 30 provided on the window 4 of the housing post 3, and the upper end of the piston rod is connected to the roll chock 8. . The hydraulic cylinder 28 may be turned upside down, the piston rod tip supported by the support part 30, and the cylinder body may be attached to the yoke 8, or the piston rod tip of the hydraulic cylinder 28 may be placed on the roll chock 7 side. Alternatively, the cylinder body may be attached. The control for maintaining the roll gap of the 20th roll gap 22 constant in such a configuration is the same as in the case of FIG. 2, so the explanation will be omitted.

FIG. 4 shows an example of a roll gap detector used for the above control, and is an example in which a displacement meter is provided inside the hydraulic cylinder 28.

As this displacement meter, an analog differential transformer or a digital magnetic scale is used. FIG. 4 shows an example of a differential transformer, in which numeral 31 is a piston slidably fitted into a cylinder body 32, and 33 is a piston 31 and a piston rod 3.
4 is a hollow part bored in the axial center part, 35 is a ring-shaped electromagnetic coil fitted in the hollow part 34, and 36° is a cylinder body 3.
It is an iron rod with one end fixed to the bottom surface of 2 and the other end inserted into the electromagnetic coil 35. With such a configuration, the amount of displacement of the piston rod 34 is equal to that of the electromagnetic coil 35.
It is detected as a change in the field voltage, and the roll gap can be determined from this.

FIG. 5 shows another example of the roll gap detector, in which an eddy current type non-contact displacement meter is used. In the figure, 37 is a support member that fixes the detection head 38 to the roll chock 8 of the work roll 14, and 39 is fixed to the chock 7 of another work roll 13 forming the 20th wheel gap 22, and faces the detection head 38. It is a metal plate. A coil is housed in the detection head 38, and when a high frequency current is passed through the coil to generate an alternating magnetic field, an eddy current is generated in the metal plate 39. As a result, a magnetic field is generated in the metal plate 39, and the inductance of the coil within the head 38 changes.

This change varies depending on the distance between the head 38 and the metal plate 39, so by detecting the change in the inductance of the coil,
The distance between the head 38 and the metal plate 39 can be determined. In other words, the roll gap 22 can be determined.

FIG. 6 shows another example of a roll gap detector, which is an example of an optical non-contact displacement meter. In the figure, 40 is a light source arranged so that light can pass through the gap between the roll jocks 7 and 8, 41 is a lens 42 that condenses the light from the light source 40, and a lens 42 for forming an image of the light that has passed through the lens 42. The light receiver is composed of a large number of element groups 43 arranged at equal intervals. The light emitted from the light source 40 passes between the roll chocks 7 and 8, is focused by the lens 42, and is imaged on the element group 43.

Then, by determining the number of elements on which the light is imaged (the blacked out areas in Figure 6), the roll chock 7 is determined.
．． 8, the roll gap between the work rolls 13, 14 can be determined.

In the embodiments of the present invention, a 1-stand 3-bus mill has been described, but it is applicable not only to 3-bus mills but also to 1-stand multi-bus mills, and wrapping can be applied not only to rolling but also to rolling mills with pull-out rolls. The roll gap can be kept constant at any position where the work rolls are facing each other, the roll gap can be kept constant at multiple locations instead of just one, and rolling Depending on the conditions, a rolling mill without backup rolls may be used (in this case, the final load bearing roll will be the outer work roll), and other various changes may be made within the scope of the gist of the present invention. Of course, it is possible to add .

[Effects of the Invention] According to the rolling mill of the present invention, since rolling is performed while keeping the roll gear gap between at least one work roll constant, the rolling blades in each gap can be changed separately. This makes it easier to control the plate thickness, and it also makes it easier to control the tension between each gap, making it possible to stabilize operations and improve yields, among other excellent effects. obtain.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram of a first embodiment of a rolling mill of the present invention, FIG. 2 is an explanatory diagram of a second embodiment of a rolling mill of the present invention, and FIG. 3 is a diagram of a third embodiment of a rolling mill of the present invention. FIG. 4 is an explanatory diagram of an example of a roll gap detector used when controlling the roll gap between work rolls in the rolling mill of the present invention, and FIG. 5 is an explanatory diagram of an example of the same. Fig. 6 is an explanatory diagram of another example of the same, Fig. 7 is an explanatory diagram of a conventional RD rolling method, Fig. 8 is an explanatory diagram of a conventional one-stand multi-bus rolling mill, and Fig. 9 is an explanatory diagram of a conventional one-stand multi-bus rolling mill. FIG. 10 is an explanatory diagram of the conventional one-stand multi-pass rolling mill provided, and FIG. 10 is an explanatory diagram of the case where loosening occurs in the rolled material wrapping in the rolling mill of FIG. 8. In the figure, 12.13.14.15 are work rolls, 19.2
0 is a hydraulic cylinder, 21 is a 10th gap, 22 is a 20th gap, 23 is a 30th gap, 24
25 is a drive mechanism, 25 is a roll gap detector, 2G is a target value, 21 is a control device, 28 is a hydraulic cylinder, 29 is a servo valve, and 30 is a support part.

Claims (1)

[Claims] 1) In a rolling mill in which one stand is equipped with three or more work rolls and a rolled material is passed between two or more work rolls and rolled at the same time, a liquid for pressurizing the work rolls is used. A pressure cylinder is provided between a roll chock that supports the final loaded roll and a rolling mill housing post, and a drive mechanism that adjusts a roll gap at at least one location among the roll gaps of the work rolls, and a drive mechanism that adjusts the roll gap between the rolls. A rolling mill characterized in that it is provided with a control mechanism that gives commands to keep the rolling mill constant. 2) The drive mechanism is a hydraulic cylinder, and the control mechanism is a detector that directly or indirectly detects the roll gap, and a servo valve that controls the piston position of the hydraulic cylinder according to the detected amount from the detector. A rolling mill according to claim 1, comprising an electro-hydraulic servo control device. 3) The rolling mill according to claim 2, wherein the hydraulic cylinder is provided between roll chocks of work rolls whose roll gap is kept constant. 4) The piston rod tip of the hydraulic cylinder or the opposite end of the cylinder body is fixed to the housing, and the opposite end of the cylinder body or the piston rod tip of the hydraulic cylinder is connected to the roll chock of the work roll. A rolling mill according to claim 2). 5) The rolling mill according to claim 2), 3) or 4), wherein the detector for detecting the roll gap is a displacement meter provided in a hydraulic cylinder. 6) Claim 1) or 2, wherein the detector for detecting the roll gap is an eddy current type non-contact displacement meter.
), or 3) or 4). 7) The rolling mill according to claim 1), 2), 3), or 4), wherein the detector for detecting the roll gap is an optical non-contact displacement meter.