JPH0562003B2 - - Google Patents

Description

[Detailed description of the invention]

[Field of Application of the Invention] The present invention relates to a roll drive device for a plate rolling mill. [Background of the Invention] Conventionally, as a roll drive system in a rolling mill, a system in which work rolls are driven to rotate has been widely adopted, as shown in, for example, Japanese Patent Laid-Open No. 59-30409. Such a driving device for a rolling mill that drives work rolls is generally shown in FIGS. 10 to 12.
It has the structure shown in the figure. The drive device shown in FIGS. 10 and 11 is of a so-called twin drive system in which the upper work roll and the lower work roll are driven by different electric motors. 10 and 11, an upper intermediate roll 102 and an upper reinforcing roll 104 are arranged above an upper work roll 100, and a lower work roll 2
Below 00, a lower intermediate roll 202 and a lower reinforcing roll 204 are arranged. Upper and lower work roll 10
0 and 200 are connected to the spindle 10 via the roll side spindle couplings 106 and 206, respectively.
8,208. The other ends of the spindles 108, 208 are connected to pinions 112, 212 via spindle couplings 110, 210 on the driving machine side. These pinions 112, 212 mesh with gears 114, 214, which are fixed to extension shafts 118, 218 of electric motors 116, 216. Extension shaft 118 and extension shaft 218 are coupled to the output shafts of motors 116 and 216 by shear pin type joints 120 and 220, respectively.
Note that in the drive device shown in FIG.
The rotational speeds of the upper work roll 100 and the lower work roll 200 are matched. FIG. 12 shows a drive device using a so-called pinion stand method. In FIG. 12, a pinion 212 is connected to the output shaft of the electric motor 216 via a shear pin type joint 220, and this pinion 212 meshes with the pinion 112, and the electric motor 216 is connected to the output shaft of the electric motor 216.
6 can be transmitted to the upper work roll 100 and the lower work roll 200 via the spindles 108, 208. A shear pin joint is generally constructed as shown in FIG. 13, using a shear pin joint 120 as an example. That is, the output shaft 124 of the electric motor 116,
Inner cylinders 126 and 128 are attached to the ends of the extension shaft 118, which is the input shaft, and gears 130 and 132 are mounted on the outer peripheral surfaces of the inner cylinders 126 and 128, respectively.
is formed. The gears 130 and 132 mesh with internal gears provided on the output shaft side outer cylinder 134 and the input shaft side outer cylinder 136, respectively. Further, the output shaft side outer cylinder 134 and the input shaft side outer cylinder 136 are fastened together by a plurality of shear pins 138. This shear pin 138 is notched at the mating surfaces of the respective outer cylinders 134 and 136, and the notched portion breaks when a load greater than a set load is applied. Note that numerals 140 and 142 shown in FIG. 13 indicate gears 130 and 1, respectively.
This is a sealing member that prevents leakage of the lubricant sealed in the portion 32. Shear pin joint 12 configured as described above
0, the power is transferred from the output shaft 124 to the inner cylinder 12.
6. It is transmitted to the output shaft side outer cylinder 134 via the gear 130. The power received by the output shaft side outer cylinder 134 is
It is transmitted to the input shaft side outer cylinder 136 via the shear pin 138, and further transmitted to the extension shaft 118, which is the input shaft, via the gear 132 and the outer cylinder 128. The maximum torque applied to the spindle coupling in the event of an accident due to breakage of rolled material, etc. is determined by the set torque of the shear pin. According to experiments, the strength at which the shear pin breaks when subjected to a large force at once (one-shot strength) has a relationship with fatigue strength as shown in FIG. 14. In other words, the single shot strength of the shear pin is approximately 2.5 per fatigue strength of 1.
Between ~3.5. Therefore, when considering the protection of the spindle coupler in the event of an accident, it is necessary to consider the shear pin's one-shot strength to be approximately 4.
Motor output torque, shear pin setting torque,
The relationship between the spindle coupling and the torque must be set to be greater than or equal to the magnitude shown in Table 1.

[Purpose of the invention]

SUMMARY OF THE INVENTION An object of the present invention is to provide a driving device for a rolling mill that can downsize a spindle coupling and use a small-diameter work roll. [Summary of the Invention] The present invention provides a slip clutch joint between the output shaft of the drive motor and the spindle coupling, detects the load condition of the drive motor with a load detector, and detects abnormal loads on the drive motor. When the spindle coupling is damaged, the slip clutch joint immediately releases the connection between the output shaft of the drive motor and the spindle coupling, which prevents a large load from being applied to the spindle coupling and makes it possible to use a small spindle coupling. The structure is such that the work roll can be made smaller. [Embodiments of the Invention] Preferred embodiments of the rolling mill drive device according to the present invention will be described in detail with reference to the accompanying drawings. Note that the same reference numerals are given to the parts corresponding to those explained in the prior art, and the explanation thereof will be omitted. FIG. 1 is an explanatory diagram showing an embodiment of a rolling mill drive device according to the present invention. In FIG. 1, the output shaft 124 of the electric motor 116
is adapted to be coupled to a gear 146 via a friction clutch 144. In addition, the electric motor 216
Similarly to the electric motor 116, the output shaft 224 can be coupled to a gear 246 via a friction clutch 244. Gears 146 and 246 mesh with pinions 112 and 212, respectively. One end of the shaft of the pinion 112 is connected to the motor-side spindle coupling 110, and a gear 148 is fixed to the other end. This gear 148 is coupled to the shaft of the pinion 212 via a friction clutch 250 provided on the shaft of the pinion 212.
It meshes with 48. The above pinion 112, 212 and gear 146,
148, 246, 248 are incorporated in the casing 300 as shown in FIG. 2, and the friction clutches 144, 244,
250 is provided to form a sliding clutch joint. The gear 246 has a shaft formed in a sleeve shape around the output shaft 224, and is rotatably supported by the housing 300 via bearings 252, 254. Further, the pinion shaft 256 on which the pinion 212 is formed is rotatably supported by the housing 300 by bearings 258 and 260. Note that the pinion 112 side that guides the power of the electric motor 116 to the upper work roll 100 has the same configuration as the pinion 212 side. Gear 148 is fixed to the end of pinion shaft 156 on which pinion 112 is formed, as shown in FIG. The gear 248 meshing with the gear 148 is formed in the shape of a sleeve around the pinion shaft 256 of the pinion 212, and the gear 248 meshes with the gear 148.
2,264, it is rotatably supported by the pinion shaft 256 and rotatably supported by the casing 300. The friction clutch 250, as shown in FIG.
A plurality of friction discs 268 are provided within the clutch case 266. The friction disk 268 is a center plate 2 attached to a boss portion 270 provided at the end of the pinion shaft 256.
72 are arranged alternately. These friction disks 268 and center plate 272 receive the pressing force of the pusher plate 274,
It is designed to be able to move in the axial direction. A cover 276 covering the opening of the clutch case 266
An air tube 278 made of synthetic rubber or the like is disposed between the pusher plate 274 and the pusher plate 274. A joint 280 is provided on the outer surface of the cover 276.
is provided, and this joint 280 connects to the air hose 28
2 and communicates with the funnel coupling 284 so that compressed air can be introduced into the air tube 278. The funnel coupling 284 communicates with a source of compressed air through a control valve 302 and a pressure reducing valve 304, as shown in FIG.
Control valve 302 is controlled by controller 306. Then, the control device 306 controls the spindle 2
A detection signal from a torque detector 308 provided in 08 is inputted. Note that the reference numeral 310 shown in FIG. 5 is a pressure gauge that detects the pressure of compressed air. In addition, other friction clutches 144, 2
44 also has a similar structure to the friction clutch 250. The operation of the embodiment configured as described above is as follows. When applying rolling power to the upper work roll 100 and the lower work roll 200, the electric motor 116 and the electric motor 2
16 is activated, the control valve 302 is opened, and compressed air is supplied to the air tube 278 through the rotary coupling 284 of each friction clutch, the air hose 282, and the fitting 280. Therefore, the pusher plate 274 moves to the left in FIG. 4, bringing the friction disk 268 and center plate 272 into close contact. Therefore,
The power of the electric motors 116, 216 is transmitted through the output shafts 124,
224 to gears 146, 246 via friction clutches 144, 244. gear 146,
246 is the pinion 112, 21 that is engaged
Rotate 2. The rotation of the pinions 112, 212 is caused by the spindle couplings 110, 21 on the driving machine side connected to one end of the spindle shafts 156, 256.
0, is transmitted to the upper work roll 100 and the lower work roll 200 via the spindles 108, 208 and the roll-side spindle couplings 106, 206, and rotates these work rolls. The rotation of the spindle 112 is caused by the rotation of the spindle shaft 15.
A gear 148 fixed to the other end of 6 is rotated. On the other hand, the rotational force of the pinion 212 is
The transmission is transmitted to a gear 248 through a friction clutch 250 provided at the other end of the gear 14.
8, pinion 112 and pinion 212
The rotation is matched and synchronized with the The relationship between the compressed air pressure in the friction clutches 144, 244, 250 and the transmitted torque is expressed by the sixth
As shown in the example shown in the figure, there is a linear relationship.
Therefore, by adjusting the supply pressure to each friction clutch, any desired transmission torque can be obtained depending on the set torque required as rolling power. Further, the relationship between static transmission torque and dynamic transmission torque in the friction clutch is as shown in FIG. The fluctuation range for static transmission torque is about ±10% with respect to the set value, and the dynamic transmission torque has a similar fluctuation range. When using such a friction clutch as an overload safety device,
The static transmission torque is the set load, and if a torque larger than the predetermined static transmission torque is applied,
In a friction clutch, slippage occurs between the friction disk and the center plate, resulting in dynamic transmission torque. This dynamic transmission torque is smaller than the static transmission torque as shown in Fig. 7, so when using it as an overload safety device, it is necessary to use the static transmission torque as a reference and consider its fluctuation range. Since the variation range is generally about ±10% as described above, the set torque may be set to 1.2 times the required transmission torque. The load applied to the electric motors 116, 216 by the upper and lower work rolls 100, 200 rolling the material to be rolled is detected by a torque detector 308 provided on the spindle 208, and is input to the control device 306. If an excessive load is applied to the spindle coupling due to abnormal phenomena during rolling operations, such as breakage of the rolled material,
The friction clutch slips and reduces excessive loads on the spindle coupling. Additionally, the control device 306 detects this excessive load via the torque detector 308, switches the control valve 302 to stop supplying compressed air to the friction clutch, and also directs the compressed air in the air tube 278 to the outside. discharge. Therefore, the power of the electric motors 116, 216 is no longer transmitted to the spindle coupling.
The torque generated in the spindle coupling becomes zero. In this way, if an accident such as plate breakage occurs during rolling work and excessive torque is loaded on the spindle coupling due to the output of the electric motors 116, 216 and the inertia of the drive system including the electric motor, the friction clutch Since the torque does not exceed the set torque, damage to the spindle coupling can be prevented and downsizing can be achieved. As a result, it is possible to reduce the diameter of the work roll, which was limited by the size of the spindle coupling. Furthermore, there are no parts that are damaged even when an abnormal load occurs, which not only shortens the recovery time of the equipment, but also eliminates the need to prepare spare parts, making it possible to provide an economical rolling mill. Furthermore, the use of a friction clutch allows calibration of the safety device. For example, in the drive device shown in FIG. 1, one of the electric motors is stopped,
By driving the other electric motor, it is possible to easily check whether the set torque can be achieved. FIGS. 8 and 9 show other embodiments of the rolling mill drive device according to the present invention. 8th
The illustrated embodiment shows another example of the twin drive system, in which the upper work roll 100 and the lower work roll 200 are each independently controlled. Further, the embodiment shown in FIG. 9 is a pinion stand type embodiment, and the electric motor 216
The power is transmitted to the pinion 2 via the friction clutch 286.
Guided by 12. Pinion 212 is spindle 2
The lower work roll 200 is rotated via the spindle 24, and power is transmitted to the pinion 112, which drives the upper work roll 100 via the spindle 124. Calibration of the safety device in the embodiment shown in FIG. 9 can be easily performed by locking the work roll.

〔Effect of the invention〕

As explained above, according to the present invention, it is possible to downsize the spindle coupling.
It becomes possible to use small diameter work rolls.

[Brief explanation of the drawing]

FIG. 1 is an explanatory diagram of an embodiment of a rolling mill drive device according to the present invention, FIG. 2 is an explanatory diagram, partially cut away, showing an example of a slip clutch joint applied to the drive device, and FIG. FIG. 4 is a cross-sectional view showing an example of a friction clutch, FIG. 5 is a control system diagram of the friction clutch, and FIG. 6 is a longitudinal sectional view of a sliding clutch joint applied to the embodiment shown in FIG. A characteristic diagram showing the relationship between compressed air pressure and transmission torque, FIG. 7 is a characteristic diagram showing the variation range between static transmission torque and dynamic transmission torque in a friction clutch, and FIGS. 8 and 9 are according to the present invention. A schematic configuration diagram showing another embodiment of a rolling mill drive device, FIGS. 10 to 12 are schematic configuration diagrams of a rolling mill drive device having a conventional shear pin type joint, and FIG. 13 shows a conventional shear pin type joint. FIG. 14 is a sectional view showing an example of the present invention, and FIG. 14 is a characteristic diagram showing the relationship between fatigue strength and one-shot strength of the shear pin. 100...Top work roll, 106,206...
Roll side spindle coupler, 108, 20
8...Spindle, 110,210...Drive machine side spindle coupling, 112,212...Pinion, 116,216...Electric motor, 124,2
24...Output shaft, 114, 244, 250, 28
6...Friction clutch, 146, 148, 246,
248...Gear, 200...Lower work roll, 30
2... Control valve, 306... Control device, 308...
Torque detector.

Claims (1)

[Scope of Claims] 1. A driving device for a rolling mill that includes a drive motor, a spindle that transmits the power of the drive motor to a roll, and a spindle coupling that connects the spindle and the output shaft of the drive motor, a sliding clutch joint provided between the output shaft of the drive motor and the spindle coupling;
A driving device for a rolling mill, comprising: a load detector that detects a load state of the drive motor; and a control circuit that controls an output of the drive motor based on a detection signal from the load detector. 2. The rolling mill drive device according to claim 1, wherein the load detector is a torque detector that detects torque generated in the spindle. 3. The rolling mill drive device according to claim 1, wherein the load detector is a tension detector that detects the tension of the material to be rolled that is rolled by the rolls. 4. The drive motor consists of an upper roll drive motor that drives the upper roll and a lower roll drive motor that drives the lower roll, and the slip clutch joint is provided on the output shaft of the upper roll drive motor. a first gear driven through a first friction clutch; a first pinion in mesh with the first gear; one end connected to the spindle coupling of the upper roll; It has a first pinion shaft, a second gear driven through a second friction clutch provided on the lower roll drive motor, and a second pinion that meshes with the second gear, one end of which is engaged with the second gear. a second pinion shaft connected to the spindle coupling of the lower roll; a second pinion shaft and the first pinion shaft;
a third gear fixed to the other end of one of the pinion shafts; and a fourth gear rotatably provided to the other end of the other pinion shaft and meshing with the third gear. and a third friction clutch connecting the fourth gear and the other pinion shaft. Machine drive unit.