JPH0373369B2 - - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a roll drive device for a bridle for a tension leveler that corrects the shape of a rolled strip material (hereinafter referred to as a strip) such as a cold rolled steel plate.

Strips rolled in rolling equipment generally have shape defects such as partial elongation or warpage due to temperature irregularities during the manufacturing process, lack of mechanical precision or poor adjustment of the equipment, and the like. Such shape defects not only impair the appearance of the sheet product and lower its commercial value, but also reduce threading efficiency in the strip processing process and impede automation.
There are problems such as the generation of new distortion during secondary processing of the strip. Therefore, a tension leveler is often used as a means to correct this defective shape of the strip.

This tension leveler equipment usually consists of a non-driven leveling mill consisting of a plurality of straightening work rolls arranged vertically in a staggered manner with the strip to be straightened in between, and each on the entry and exit sides of the leveling mill. It consists of one set of bridles. The strip is repeatedly bent by the work rolls of the leveling mill while tension is applied by the bridle, and the strip is passed through the strip while being bent, and permanent elongation necessary for correcting the shape is imparted to the strip, thereby eliminating shape defects. be corrected.

Therefore, while the tension leveler is in operation, it is necessary to maintain a predetermined elongation rate according to the strip specification conditions (width, thickness, mechanical properties such as yield strength, etc.), and this is due to the This can be carried out by maintaining a circumferential velocity difference between the exit bridles in accordance with the set elongation of the strip and passing the strip while applying tension to the strip.

As mentioned above, the leveling mill enters and exits (front and back)
The driving method for the bridle roll, which threads the strip while applying tension to the strip between the bridles, is as follows:
Traditionally, each roll of the bridle was
The so-called independent drive system is driven by a DC motor, and the roll group on the entry side bridle and the roll group on the exit side bridle are driven by one main motor, and the circumferential speed is controlled between both roll groups. So-called mechanical
A tie drive system is used. However, these conventional drive systems have problems such as high equipment costs or insufficient control of roll transmission torque, which adversely affects strip quality.

1 and 2 are explanatory diagrams illustrating the overall configuration of a conventional bridle roll drive device as described above, and FIG. 1 is an explanatory diagram showing the overall configuration of a conventional bridle roll drive device as described above. ), FIG. 2 shows a device using the mechanical tie drive method described above (hereinafter referred to as conventional example 2). Conventional example 1,
In both conventional examples 2, strip 1 is leveling mill 2.
The work rolls 5, 6, and 7 repeatedly bend and correct the shape, and at this time, tension is applied between the bridles 3 and 4 installed on the entry and exit sides (front and rear) of the leveling mill 2. be done. The bridles 3 and 4 are rolls 3a, 3b, 3c, respectively.
3d, 4a, 4b, 4c, and 4d, and the strip 1 is wound around these rolls that rotate in opposite directions.

In the conventional example 1 shown in FIG. 1, each of the rolls 3a, 3b,
3c, 3d and 4a, 4b, 4c, 4d are independent DC (direct current) motors 101, 102,
103,104 and 105,106,107,1
By 08, reducer 109, 110, 111, 1
12 and 113, 114, 115, and 116, respectively. In this case, the speed difference between the entry bridle 3 and the exit bridle 4 (i.e. the set elongation of the strip 1) is determined by the speed difference between a particular roll in the entry bridle 3 (e.g. 3d) and a DC motors 104 and 105 that drive the rolls (for example, 4a) are used as reference motors, and these inlet-side reference DC motor 104 and outlet-side reference
It is set by speed control with the DC motor 105. DC motors 101, 102, 103 and 10 for rolls other than these specific rolls
6, 107, and 108 are controlled in speed according to their respective loads.

Thus, roll group 3 of both bridles 3 and 4
a, 3b, 3c, 3d and 4a, 4b, 4c, 4
It is possible to control the circumferential speed difference between the strips d so as to correspond to the set elongation of the strip 1, and to control the circumferential speed difference between the individual rolls in each roll group so as to correspond to the elastic elongation of the strip 1. It is possible to control the elongation rate accurately and prevent slippage due to elastic elongation between the strip 1 and the bridle rolls 3a, . . . , 4a. This drive system uses a DC motor with high responsiveness in rotation control.
And by controlling the speed using a DDC (direct digital computer) system,
It is possible to control the elongation rate with extremely high precision and prevent slipping, and the shape of the strip can be corrected with high precision.

However, the device of Conventional Example 1 requires a large number of DC motors, and each of these DC motors is operated and controlled independently, resulting in high equipment costs and low power costs. The disadvantage is that it is expensive.

Next, in conventional example 2 shown in FIG.
Roll groups 3a, 3b, 3 of each bridle 3, 4
c, 3d, 4a, 4b, 4c, and 4d are pinion stands 11 consisting of gear means that mesh with each other.
a and 11b, respectively, and the pinion stands 11a and 11b are rotationally driven by one main motor 8. Both bridles 3 and 4
The peripheral speed difference between the roll groups 4a to 4d of the exit bridle 4 (that is, the elongation rate of the strip 1) is
This is achieved by setting the circumferential speed of the roll groups 3a to 3d of the entry side bridle 3 to a lower speed than the circumferential speed of the bridle. This is done by the action of a differential gear mechanism).

That is, the roll groups 4a to 4d of the reference bridle (in the case of this illustrated example, the exit side bridle) 4
are directly driven from the main motor 8 via the bevel gear 10b and pinion stand 11b, while the roll groups 3a to 3d of the other bridle (inlet bridle) 3 are driven directly from the main motor 8 via the bevel gear 10b and pinion stand. 11a. Planetary gear device 12
is composed of a plurality of planetary gears 13, a revolution shaft 14 that outputs the revolution of the planetary gears 13, a ring gear 15, and a sun gear 17, and the ring gear 15 meshes with a pinion 16 on the 8 shafts of the main motor. Driven by main motor 8, sun gear 17
is driven by a stretching motor 9 which is a DC motor, and a revolving shaft 14 of a planetary gear 13 rotationally drives the bevel gear 10a. The stretching motor 9 is controlled by a speed control mechanism using a DDC system (not shown). Thus, the reference bridle (outside bridle) 4 and the other bridle (inside bridle) 3
The circumferential velocity difference (elongation rate) between the stretching motor 9 and the stretching motor 9 can be controlled with extremely high precision by controlling and driving the stretching motor 9.

On the other hand, each roll group 3a of each bridle 3 and 4
~3d and 4a~4d are mechanically coupled to each other by gear means in pinion stands 11a and 11b, respectively, and since the rotational speeds are the same, the strip 1 passes through each roll group by elongation due to its tension. During this time, slippage occurs between the roll surface and the strip surface, damaging the strip surface. To prevent this, pinion stands 11a and 11b and each roll 3a, 3b, 3c
Slip clutches P ₁ , P ₂ , P 3 and P 4 , _{P 5 , P 6 are} provided on the drive shafts between the motors 4b, 4c, and 4d. (Only the reference rolls 3d and 4a are pinion stands 11a and 11b, respectively.
Driven directly from ) Then, the strip tension during operation is detected by a tension meter (not shown), and its fluctuation is detected by each of the slip clutches _P1 to P1.
By controlling the torque of the slip clutches P ₁ to P ₆ so as to correspond to the partial elongation due to the tension of the strip 1 passing through the circumferential speed difference between the individual rolls in each roll group by feedback to P ₆ , the rolls and It is constructed to prevent slipping between the strips.

In the device of Conventional Example 2, the drive motor requires only one main motor 8 and a stretching motor 9 of small capacity (for example, about 1/10 of the main motor), so it is different from that of Conventional Example 1. The equipment cost is significantly lower than that, and the bridles 3 and 4 are mechanically connected, so that part of the driving power of the outlet bridle 4 is fed back to the inlet bridle 3. It also has the advantage of lower power costs. However, the control method for transmitting torque using a slip clutch usually has poor response compared to a DC motor, so it cannot completely prevent slipping between the roll and the strip, and the control range for torque fluctuations is narrow.
For this reason, there is a drawback that it is difficult to cope with the increasingly sophisticated requirements for the quality of the strip shape in recent years, as well as the diversification of the dimensions, materials, etc. of the material to be straightened.

The present invention solves the problems of conventional bridle roll drive devices as described above, and can prevent slippage between the strip and the rolls by controlling the torque of each roll with high precision. This was done for the purpose of providing a drive device with low cost and operating power cost.

That is, the bridle roll driving device of the present invention is a bridle device that continuously applies tension to the strip by passing the strip through the rolls of the two roll groups arranged in front and behind each other while alternately contacting the rolls as described above. , a differential gear mechanism is provided for driving a specific roll of one roll group and a specific roll of the other roll group with a predetermined speed difference by the drive of a main motor; each roll except the specific roll of is connected to a revolving shaft of a planetary gear device,
configuring a transmission mechanism that sequentially meshes a gear provided on a drive shaft of the specific roll with a ring gear of a planetary gear device of each roll to alternately rotate each roll in each roll group in opposite directions; A prime mover such as a DC motor capable of torque control is connected to the sun gear shaft of the planetary gear device of each of the rolls, and means is further provided for controlling the torque of the prime mover in accordance with the torque of each roll. This is a characteristic feature.

DESCRIPTION OF THE PREFERRED EMBODIMENTS The configuration of the apparatus of the present invention will be explained in more detail below based on the embodiments shown in the drawings. FIG. 3 is an explanatory diagram showing the overall configuration of an embodiment of the bridle roll drive device according to the present invention. Note that in FIG. 3, parts with the same reference numerals as in FIGS. 1 and 2 are the same or equivalent parts of the conventional device.

As shown in the figure, roll groups 4a, 4b, 4c of one of the bridles 3 and 4 installed on the inlet and outlet sides of the leveling mill 2, in this case the outlet bridle 4, 4d
(hereinafter referred to as the drive roll group) is configured to be driven by a transmission mechanism of the pinion stand 18b. This pinion stand 18b includes a gear 19b driven by the main motor 8 via a bevel gear 10b, a ring gear 20a that meshes with the gear 19b sequentially, and alternately rotates in opposite directions.
Planetary gear set 20, 2 having 21a, 22a
1 and 22. Among the driving roll groups 4a to 4d, a specific roll (in the illustrated example, the roll that the strip 1 comes into contact with after leaving the leveling mill 2) 4a (reference roll) is connected to the output shaft of the gear 19b, and Other roll 4b,
4c and 4d are the planetary gear devices 20 and 2, respectively.
It is connected to the revolution shafts 20c, 21c, 22c of the planetary gears 20b, 21b, 22b.
The input shafts of the sun gears 20d, 21d, 22d of the planetary gear units 20, 21, 22 are connected to DC motors 23b, 24b, 25b, respectively.

Furthermore, each of the DC motors 23b, 24b, 2
5b is connected to an automatic torque control device using a DDC system (not shown), which calculates and processes tension fluctuations in the strip 1 during threading detected by a tension meter (not shown), and calculates the result based on the output signal. Each of the DC motors 23b, 24b, 25
By controlling the torque of each motor b individually, the torque of each motor can be adjusted to a predetermined set value corresponding to the torque of each roll of the drive roll groups 4a to 4d.

On the other hand, the roll groups 3a, 3 of the entry side bridle 3
b, 3c, 3d (hereinafter referred to as brake roll group) are:
The pinion stand 18a is configured to be driven by a transmission mechanism of the pinion stand 18a.
The configuration is such that a specific roll 3d of the brake roll groups 3a to 3d (in the illustrated example, the roll with which the strip 1 comes into contact immediately before entering the leveling mill 2)
(Reference roll) Gear 19a on the shaft and the gear 19
The reference roll 3 comprises a planetary gear device 20, 21, 22 having ring gears 20a, 21a, 22a which are sequentially engaged with the reference roll 3 and rotate in opposite directions.
Rolls 3a, 3b, 3c other than d are planetary gears 20
b, 21b, 22b revolution axes 20c, 21c, 2
This is similar to the case of the exit side bridle 4 in that it is connected to the bridle 2c. (For convenience, the same symbols as those on the output side are used for the planetary gear device and its constituent parts, such as the ring gear, planetary gear, sun gear, and revolution axis.) Furthermore, the axis of each sun gear 20d, 21d, and 22d is DC motor 23a,
The same applies to the fact that it is connected to 24a and 25a.

However, this braking side roll group 3a to 3d
In this case, the reference roll 3d, that is, the shaft of the gear 19a is connected from the main motor 8 to the pinion 1.
6. Rotationally driven via a planetary gear device 12, which is a differential gear mechanism, and a bevel gear 10a. The sun gear 17 of the planetary gear set 12 is driven by the stretching motor 9. With this configuration, the peripheral speed difference between the reference roll 4a in the drive roll group and the reference roll 3d in the brake roll group is maintained and controlled, and this configuration is different from the conventional example 2 described above. It is similar to In addition,
Regarding the torque control by the DC motors 23a, 24a, 25a, the aforementioned drive roll groups 4a to 4d
Since this is the same as in the case of , the explanation will be omitted.

Since the bridle roll drive device of the present invention is configured as described above, the torque of each roll corresponding to the set tension of the strip between the rolls in the braking and drive roll group is By controlling the torque of the DC motor, it is possible to adjust to a predetermined set value with extremely high precision and over a wide range via the revolution axis.
Slippage between the surface of the strip passing through the roll group and the outer peripheral surface of the rolls can be completely prevented, making it possible to manufacture strips of excellent quality.

In addition, the prime mover in the device of the present invention includes one main motor and multiple small-capacity DC motors for torque control.
Since it is composed of a motor, it has advantages such as being able to significantly reduce equipment costs and operating power costs compared to the device of Conventional Example 1.

[Brief explanation of drawings]

1 and 2 are explanatory diagrams illustrating the overall configuration of an example of a conventional bridle roll drive device;
The figure is an explanatory view showing the overall configuration of an embodiment of the bridle roll drive device of the present invention. In the drawing, 1 is a strip, 2 is a leveling mill, 3 is an entry bridle, 4 is an exit bridle,
3a, 3b, 3c, 3d, 4a, 4b, 4c, 4
d is a roll, 8 is a main motor, 9 is a stretching motor, 10a, 10b are bevel gears, 12
is a planetary gear mechanism (differential gear mechanism), 18a, 18
b is pinion stand (transmission mechanism), 19a, 1
9b is a gear, 20, 21, 22 are planetary gears,
20a, 21a, 22a are ring gears, 20b,
21b, 22b are planetary gears, 20c, 21c, 2
2c is a revolution axis, 20d, 21d, 22d are sun gears, 23a, 24a, 25a, 23b, 24b,
25b is a DC motor.

Claims (1)

[Claims] 1. In a bridle device that continuously applies tension to the strip by passing the strip through each roll of two roll groups arranged in front and behind each other while contacting the strip alternately, a specific roll of one roll group is connected to the other roll. A differential gear mechanism is provided for driving a specific roll of the roll group with a predetermined speed difference by the drive of a main motor, and a planetary gear mechanism is provided for driving each roll other than the specific roll of each roll group. A gear provided on the drive shaft of the specific roll and a ring gear of a planetary gear device of each roll are sequentially meshed to alternately rotate each roll in each roll group in opposite directions. A power transmission mechanism capable of torque control is connected to the sun gear shaft of the planetary gear device of each of the rolls, and means is further provided for controlling the torque of the motor in accordance with the torque of each of the rolls. A bridle roll drive device characterized by: