JPS58196114A - Controlling device of hoop tension in continuous rolling mill - Google Patents

Abstract

PURPOSE:To reduce the generation of a defective rolled material caused by the fluctuation of a hoop tension, by restraining and relaxing the fluctuation of hoop tension at the time of shearing a hoop, in rolling a hoop, etc. by a continuous rolling mill. CONSTITUTION:A material to be rolled, such as a hoop, is rolled by a continuous rolling mill equipped with a coiling reel through bridle rolls 4, a rolling stand 5 at the inlet side and bridle rolls 9, flying shear 10 at the outlet side. In this case, the minimum length of the hoop to be coiled required to reduce a hoop tension to the tension at the time of a prescribed shearing by the shear 10 is calculated in accordance with the changing rate of the prescribed maximum allowable tension of the hoop by detecting the tension of the material to be coiled with the aid of a tensio-meter 6. At the same time, the coiled length of the material is detected to calculate the remaining length of the hoop to be coiled by using the prescribed target hoop length to be coiled, and a reference taper rate is exchanged to an allowable maximum taper rate when the remaining hoop length coincides with the minimum coiling length.

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a method for controlling the tension of a rolled material in a continuous rolling mill, and particularly to a method for controlling the tension in a continuous rolling mill equipped with a split shear.

As an example of continuous rolling, a water type rolling system as shown in FIG. 1 has been known.

As shown in Fig. 1111, the rolled material taken out from the take-out reel l is transferred to the melt II! 63
The rolling stock is guided to the rolling stand 5 via the defroll roll 2 and the entry side priddle roll 4t. The rolled material rolled by the rolling stand 5 is guided to the exit priddle roll 7 via a tension meter 6t which detects the tension applied to the rolled material.

The rolled material sent out from this exit side priddle roll 7 is
It is guided to the side trimmer 8 via the differential gear 2t. The rolled material sent out from this side trimmer 8 is wound up through an exit side priddle roll 9 and a flying shear 10. This winding reel 11 is generally equipped with two reels called a carousel reel.

In a continuous rolling mill configured in this way, the two take-up reels can be used alternately to divide the coil (shear), unload the welding point, or sample without stopping the rolling process. It is possible to take out, etc.

However, when the rolled material is cut by 7 line shears while being continuously rolled, the tension (take-up) is applied to the rolled material by the take-up reel 11 at the same time as the cutting.
tension) is lost, which causes the flying shear 1
0 Upper R @ A sudden change occurs in the tension acting on the rolled material. This tension fluctuation may cause the rolling stand 5 to reduce the pressure, make side trimming unnecessary at the side trimmer 8, and cause off-gauge (defective products).

As a method to prevent the occurrence of defective products due to tension fluctuations during blow-cutting, a method has been proposed in which the tension of the rolled material in the side trimmer sVc is controlled to a constant level (% Publication No. 85-13815 and Publication No. 55). -3B81@), but it is not possible to suppress tension fluctuations exerted on the rolling stand! However, it has the disadvantage that it cannot reduce the number of defective products because it cannot eliminate sudden changes in number.

An object of the present invention is to provide a tension control method capable of suppressing and mitigating tension changes in a rolled material during shear cutting and reducing the occurrence of defective products.

The present invention detects the winding coil diameter of a rolled material and calculates the winding tension according to the coil diameter and a predetermined reference taper rate or an allowable maximum taper rate given by switching.
The take-up reel is driven according to the take-up tension, and the minimum take-up length P required to detect the tension of the rolled material and reduce the tension to the predetermined cutting tension according to the predetermined maximum allowable tension change rate. is calculated, the winding coil length of the rolled material is detected, and f! is calculated from the winding coil length and a predetermined target winding coil length. Calculate the winding length of 11 of 4>, and when the winding length of the armpit residue reaches the minimum winding length, switch from the standard taper rate to the maximum allowable taper rate, and then apply the winding tension. is reduced to a predetermined minimum cutting tension within the maximum allowable tension change rate and in a minimum time, thereby suppressing and mitigating the tension fluctuation rate of the rolled material during shear cutting, and minimizing the change time. The purpose is to reduce the occurrence of non-defective products and to adjust the shape of the wound coil to a desired shape.

In addition, the present invention detects the load amount of each priddle roll, compares the detected load amount with the allowable maximum load amount, calculates the amount of change in tension from the detected load amount, and calculates the amount of change in tension and a predetermined optimum change in tension. By comparing the ranges, the load margin of each prydle roll is calculated, and the load distribution ratio between each of the prydle rolls is calculated, and the tension on the exit side of the rolling stand is detected, and the wrinkle tension detection value and a predetermined tension target are calculated. By controlling the driving force of each priddle roll according to the tension difference with the value and the load margin and according to the negative distribution ratio j), the IQ tension t - the tension at cutting is reduced. Efforts are made to compensate for the accompanying tension fluctuations and maintain the tension in the rolling stand and side trimmer at predetermined values.

Furthermore, the present invention detects the rolling speed and calculates the tension propagation response time during which the loss of winding tension during freshening is propagated to the rolling stand and the night trimmer based on the rolling speed, and also calculates the tension propagation response time during which the loss of winding tension during freshening is propagated to the rolling stand and the night trimmer, and the cutting operation of the flying shear. is detected and the driving force of each priddle roll is controlled by the tension correction value delayed according to the tension propagation response time and determined according to the predetermined load distribution ratio. This is intended to reduce the tension caused by the loss of *mt@, and to suppress and alleviate tension fluctuations in the rolling stand and side trimmer.

Hereinafter, the present invention will be explained based on nine preferred embodiments shown in the drawings.

Fig. 2 shows a control system diagram of an embodiment of the control method for reducing winding tension during cutting according to the present invention, and Fig. 3 shows an embodiment of the tension fluctuation absorption control method of the present invention. A control system diagram is shown. Items in the figure with the same reference numerals as in FIG. 1 are turtles having the same configuration and the same mm.

As shown in FIG. 2, the exit side idle rolls 7, 9
DC motors 13A to 130 are respectively engaged with the 1,1171L reels 11 as driving machines.

Pulse transmitters 12A and 12B that output pulse signals depending on the number of revolutions are respectively provided on the inlet defrol 2 of the flying shear 10 and the DC motor 13C. Motor control devices 14 to 14C are connected to the DC motors 13A to 13C, respectively. A rolling speed detector 415 is engaged with the rolling stand 5 . Pulse signals are input to the coil diameter calculator 16 from the pulse transmitters IKA and 12B, and this calculation! The output of 16 is input to taper tension calculation 4!617. In addition, this computing unit 17
The reference taper rate 18 or the allowable maximum taper rate 20 is manually controlled via the switch tI19, and the output is controlled by the motor control device 14C of the winding wheel 11.
has been entered. A pulse signal from the pulse transmitter 12A is input to the pulse integrator 11, and the output of the integrator 21 is subtracted by 112 mAK. A tracking device 22 is connected to the other input terminal of the subtracter 23C, and the output is input to the subtractor 23C. The tension detection signal TP on the exit side of the rolling stand detected by the tension meter 6 is input to a subtracter 23B, and the other input terminal of this subtractor 23B receives a predetermined cutting tension setting signal T. cut 26A is input. The output of the subtracter 23B is input to a divider 24k, and the other input terminal of this divider 24A receives a predetermined lll! F volume wax large tension change rate 27 is input. The output of the division 1iF24A is input to the multiplier 25A, and this multiplication 1i2
The other input terminal of 5A is the rolling speed detection! A speed detection signal of +15 is input. This multiplication! The output of 25A is input to the subtractor It) 23C, and the output of this subtractor 23C is the switch i! ! )19.

With the above structure, the winding tension applied to the rolled material by the take-up reel 11 is high at the beginning of winding, and as the coil diameter increases, in order to lose the shape of the winding coil. The winding tension is controlled to be reduced at a predetermined rate, but if the winding tension is reduced more than necessary, the winding shape will deteriorate, so the winding tension is controlled to be reduced to the cutting tension as short as possible. .

Below, to explain more quietly, coil diameter calculation! 616
Now, the pulse signal station wave numbers Pay and Ptm output from each of the 12 pulse transmitters and 12B, and the def.
From DDv, the coil diameter is calculated using the following formula value), and the amount of increase in coil diameter from the start of control is output to the taper tension calculator 17.

D = Dot X Pot / Ptm
...” (1) The taper tension calculator 17 calculates the nine winding tension according to the coil diameter by multiplying the coil diameter increase amount by the reference chi (15) 18, and based on this winding tension. The winding tension control signal is output to the motor control device 14CK.On the other hand, the subtraction -j13B
In , the tension difference between the input tension detection signal TP and the cutting tension setting signal Tcoy is calculated. Divider 24
For humans, the input tension difference is #'! The time required to reduce the winding tension at the maximum permissible tension change rate is calculated by dividing by the large tension change rate 21. Multiply! ! ! By multiplying 5A by the lever time and rolling speed, the length of the 9th roll area is calculated according to the time.
That is, the minimum turn 1/i required to reduce tension during cutting.
L length Lmtw is calculated. Also, pulse integration @21
Here, the length of the winding coil of the rolled material is integrated by calculating the pulse signal station wave number Por. The tracking device 22 stores the target winding coil length up to the next cutting point.

The subtractor 23A calculates the remaining winding length Lm from the manually input winding coil length and the target winding coil length.

The subtractor 230 compares the inputted small winding length LMX)I with the remaining winding plate length Lm, and when they are negative, the switching command signal is set as above. Output to switch 4119. As a result, the tension taper rate manually applied to the taper tension calculation 4!117 is the maximum allowable chirage) 2
0, and the winding tension is rapidly reduced to the predetermined cutting tension at the maximum allowable reduction rate.

Therefore, according to this embodiment, the winding tension can be reduced to the predetermined minimum cutting tension within the maximum allowable tension variation rate and in the minimum time, so the tension variation rate of the rolled material during shear cutting can be significantly reduced. This has the effect of suppressing and alleviating the fluctuations and significantly minimizing the fluctuation time.

Further, according to this embodiment, since the tension change JIll can be significantly suppressed and alleviated, the occurrence of defective products is reduced and the winding coil shape can be seen as an i-shape.

Next, the n9 embodiment shown in FIG. 3 will be described.

As shown in FIG. 3, the rolling tension detection signal Tp and the rolling tension target value Tyo26B are input to the subtraction #11I23D, and the outputs are input to the switching devices 29A and 19B, respectively. One of the switching outputs of the switching devices 29A and 29B is sent through the multiplier 25B and 25Ct, respectively, and the other is sent directly to the motor control device 14A.

It is input in 14B. The comparison 628 is inputted with the detected load amount (motor current) of the drive DC motors 13A, 13B+2) of the priddle roll. In response to the output of this comparator 28, the switch 29 is switched.

29B switching is performed. Further, the detected load amount is added by addition@83, and this total load amount is input to the dividers 24B and 24C, respectively. Each of these dividers 24B and 24C is connected to a DC motor 13.
The detected load amounts are input from A and 13B, and each is divided! 24B! The output of 4C is the multiplication 525B, 25C
has been entered. The flying shear IO has a cell signal that can detect the blade position t11! 3G is provided, and this sershin transmitter 30 detects shear cutting and outputs a cutting operation signal. A cutting operation signal and a rolling speed signal are input to the position detector 31, and the output command from the position detector 31 causes the switching 4129C to be switched.

The tension correction value 32 is input to this switch 290)
, the tension correction value 32t is determined by the command from the position detector 31.
- K is set to output to the motor control device 14B.

The system is configured as described above, detects the tension force during cutting, detects the load amount of each prydle roll, and adjusts the tension based on the load margin of each prydle roll and a predetermined optimum tension change range. The amount of fluctuation is absorbed by assigning it to each priddle roll, the tension in the rolling stand and side trimmer is kept constant, and the cutting operation is detected and the tension fluctuation caused by the loss of winding tension during cutting is absorbed. There is.

This will be explained in more detail below.

The comparator 28 stores in advance set values such as the permissible large load amount of the &IfL motors 13A and 13B, the optimum tension change range between the priddle rolls 7 and 9, and the optimum tension change range for the rolling stand 5. . Therefore, the comparator 28 compares the input load amount (motor current) of the two Prydle rolls 7.9 with the upper Tl12 set value to determine the load margin of each Prydle roll. The switch 29A calculates whether or not the tension is within the suitable tension change range d, and changes the driving force control signal based on this.

, 29BK output. On the other hand, the subtracter 23D calculates the deviation between the rolling tension detection signal TF and the rolling tension target value TPO, and also calculates the deviation between the rolling tension detection signal TF and the rolling tension target value TPO.
．． A decision is made as to whether to give a command to distribute the load to the rolls 9 or only to one of the priddle rolls. When giving a command to only one priddle roll, the multiplier 25B or 25C is bypassed,
The driving force control signal is transmitted to the motor control device 14A or 14B.
Output to. Note that the dividers 24B and 24C calculate the load distribution ratio of each Prydle roll to the total load of the two Prydle rolls, and the inputs are input to multipliers 25B and 250 in correspondence with each other. . Therefore, when the load distribution command is output from the subtracters 2 and 3D, the driving force control signal for the priddle roll is multiplied! 1iir25B.

25C according to the distribution ratio and inputted to each motor control device 14A, 14B.

Further, the tension correction value 32 is determined based on the winding tension lost at the time of cutting, taking into account the amount of tension variation in the rolling stand and side trimmer in advance, and according to this predetermined value. However, there is a time lag in trenches where tension fluctuations occur in the rolling stand and side trimmer after the cutting is actually made. This time is called the tension propagation response time), and the tension propagation response function is fitted by the following equation.

In addition, in equation (2), ΔT is tensile strength, E is the Young's bow, the cross-sectional area is, Ma is the rolling speed, and L is the propagation distance 1Ill!
(fIA interinstrument distance*).

A: Other delays aS include simple control system delays, but since control system delays can be treated as constants, delay correction is easy.1゜However, the delay associated with the tension propagation response increases depending on the rolling speed. Therefore, the timing at which the tension correction value 32 is output is corrected by switching the switch 29C according to the timing at which the first-order lag is corrected according to the degree of rolling after the cutting operation signal is input.

Therefore, according to this embodiment, the amount of load on the prydle roll is controlled in response to tension fluctuations without imposing an excessive load on a specific prydle roll.
Rolling stand exit tension can be maintained constant,
In addition, the effect is that tension fluctuations in the side trimmer can be suppressed and relaxed within a certain range.

Further, according to this embodiment, the tension J due to the loss of winding tension is
There is an effect that the tension wave-IIb can be absorbed in accordance with the timing when RllIll is propagated to the rolling stand or the side trimmer.

Here, using the tension control operation t-FIG. 4 of the embodiment in which the embodiments shown in FIGS. 2 and 3 described above are combined, i,
I will explain.

The time t is shown on the horizontal axis of FIG.
mm1 is shown in the same figure (-) shows the tension cover turn T1- of the pridle roll 9, and FIG.

#! As shown in FIG. 4(C), the taper force control is started at tt according to the coil value and the reference taper rate, and the winding NRII and the cover turn T are being squeezed. With this, Pride Roll's cover turn Tm
m1. Tang is increased and the rolling stand exit tension is kept constant. At t, xl, Fig. 4 (C
), the maximum allowable taper rate reduces the L winding tension to the cutting W# tension. On the other hand, this t,
In response to the tension fluctuation between t4 and t4,
As shown in 9, when the tension is turned T1, Tm- is increased, but in 'l, the priddle roll 9 exceeds the range of change in the force of the moth, and Tmm1 is held constant;
Between 'a' and '14, tension correction -at is performed only by the priddle roll 7. The cut is made at t, and the resulting loss of IIk tension is caused by the priddle roll 9
It is absorbed by correcting the cover turn Tmal. t. indicates that the rolled material has been wound onto the next take-up reel.

Significantly suppresses tension waves 111b in the rolled material during cutting.
i.
It has a beneficial effect.

[Brief explanation of the drawing]

#1 #A is a system configuration diagram of an example of a continuous rolling mill to which the present invention is applied; FIG. 2 is a control system diagram of an embodiment of the present invention; #I
Figure 3 is a control system diagram of another embodiment of the present invention, Figure II4 (
a) to (C) are diagrams for explaining the operation. 5... Rolling stand, 6... Tension meter, 7
゜9...Pride a-ru, 8...Side trimmer,
lO... Flying shear, 11... Take-up reel,
12A. B...Pulse 4111! , 1 mA-C...DC motor, 14A-C...Motor control device, 15...Rolling speed detector, 16...Coil diameter calculator, i7...
・Taper tension calculator, 18...Reference taper rate, 1
9...Switcher, 20...Allowable high-temperature valley)
21...Pulse 41 [device, 22...Tracking device, 23A-D...Subtractor, 24A-C...Dividing hot water, 25A-C...Multiplier, target value, 27...・Maximum eaves tension change rate, 28...Comparator, 29A-C...Switcher, 30...Selsin transmission-1 procedural amendment (method) Showa (7〃 Part 2 Commissioner of the Japan Patent Office Kazuo Wakasugi) Description of the case 1982 Patent Application No. 78361 Name of the invention Relationship to the case of a person who corrects tension control waves of a continuous rolling mill Special H'f (11 people f) Location: 5-1 Marunouchi-chome, Chiyoda-ku, Tokyo given name
Name + S + O + Representative of Hitachi, Ltd.
3 1) Osamu Katsu Shigeyo Residence Address: 5-5-1, Marunouchi-chome, Chiyoda-ku, Tokyo Subject of amendment @ Contents of amendment to simple IT column of drawings of application Attachment 0) (1) Missing description page 18 Irises “4th E (
a) to (C) are the ninth 0. II drawings etc. spring 〒
'' is corrected to ``4th E is a rounding diagram exposure 1i explaining the operation''. that's all

Claims (1)

[Claims] 1. *A rolling stand that rolls the rolled material, a number of pridle rolls including a pridle roll that reduces the tension of the rolled material sent out from the rolling stand, and a take-up reel that winds the rolled material into a coil shape. and a shaft provided on the inlet side of the take-up reel, the coil pole of the front winding coil is detected and a predetermined reference taper rate given by the coil diameter and switching is performed. Alternatively, the tension of i#ll1L is calculated according to 1lV-volume and forging large taberate, and the take-up reel is driven according to the winding and loading force, and the tension of the rolled material is detected and a predetermined moth eave is The amount of winding required to reduce the cough tension to a predetermined cutting tension according to the rate of change in volume tension is calculated, and the winding coil of the rolled material is also detected, and the winding coil and the predetermined tension are calculated. Calculate the remaining winding length 9 from the target winding coil length,
The winding length of the remaining sheet is 9! A tension control method for a continuous rolling mill in which the standard taper rate is switched to the allowable large-scale taper rate when k is equal to 9.