JPS607575B2 - Roll spacing adjustment device in continuous casting equipment - Google Patents

Description

DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a roll spacing adjustment device in continuous casting equipment.

It is known that if the distance between the upper and lower rolls, which are supported by both the upper and lower frames of the segment that makes up the coin conveyance path in continuous casting equipment, is not maintained correctly, internal cracks in the coins, surface cracks, and deflection of the center may occur. It is being

Conventionally, devices for maintaining the correct spacing include a hydraulic cylinder that presses the upper frame against the side frame on the lower frame to maintain the upper and lower roll spacing, or a screw that moves the upper frame up and down to maintain the upper and lower roll spacing. There is a type that does. However, these conventional devices require an employee to go between the rolls and check each roll before casting preparation or during periodic maintenance.

Therefore, it has been considered to insert an automatic measuring device into the coin conveyance path and move it to check the interval between each roll.

However, even this method has the following drawbacks. [1] The roll spacing is checked when the rolls are cold and under no load, but the core gap, deflection, thermal elongation, etc. This occurs in a loaded state where the roll is under a load, and this method cannot measure the roll interval in such a loaded state. Ideally, the correct roll spacing should be maintained under load.

'2) Furthermore, even if the roll spacing is measured in the same state as the loaded state and the roll spacing is maintained appropriately, the following problems will occur.

In other words, the casting speed of the coin coins varies depending on the ladle, the state of pouring from the tundish to the mold, the temperature of the molten steel, the lotus coin operation, etc., and the conditions for pulling out the rust pieces in each segment also change. The bulging force will vary. Therefore, it is necessary to change the roll spacing to follow the fluctuations in the bulging force, but with the conventional equipment described above, it is not possible to change the roll spacing during casting, or even if it is possible to change the roll spacing, it is difficult to change the roll spacing due to fluctuations in the bulging force. The roll interval can only be adjusted after a considerable delay. For example 1. If the speed is reduced from high-speed casting at shoe/min to lm/min due to some condition, the final unsolidified end of the coin will recede, that is, it will get closer to the mall, so 1. arc/
There is a gap between the roll of the segment that supported the final end of the coagulation in the min state and the coin in the lm/mjn state, which causes center deflection.

SUMMARY OF THE INVENTION The present invention provides a method and apparatus that can immediately adjust the roll spacing in response to fluctuations in bulging force during continuous casting.

An embodiment of the present invention will be described below with reference to the drawings.

1 is a lower frame of the segment, 2 is an upper frame, 3 is a side frame erected at both ends of the lower frame 1, and a vertical slit 4 is formed in the center;
Projections 2a protruding from both ends of the upper frame 2 are inserted into the slit 4 so as to be movable in the vertical direction.

5 is a pedestal 6 fixed to the upper end of both side frames 3.
The piston stem 5a of the cylinder 5 is inserted into the hole 8 formed in the protrusion 2a through the hole 7 of the pedestal 6.

Reference numeral 9 denotes a pin inserted into a hole at the tip of the piston stem 5a and a hole in the protrusion 2a. Therefore, the upper frame 2 is rotatable about nine turns of the pin. 10 is upper frame 2
A smooth rod that passes through the square of the
11 is a sub-sa rod 10 fixed on the upper frame 2.
A worm gear mechanism for vertically moving the
It is operated via a drive shaft 12 by a drive motor (not shown).

Reference numeral 13 denotes a ram cylinder fixed on a pedestal 14 on the lower frame below each of the displacement rods 10, and the upper surface of the piston stem 13a is in contact with the lower end of each of the displacement rods 10.

Note that the stroke S of this piston sum 13a is 1 Yanagi to 3
It is about the side. 14, 145, 15, 155 are support rolls for the coins 16 supported by the upper and lower frames 1 and 2, respectively, and the center rolls 143 and 153 are drive rolls and are rotated by a drive shaft 17. .

Further, among both rolls 143 and 153, the upper drive roll 143 is moved up and down by the cylinder device 18,
It is pressed against the coin piece 16. 16a is an unsolidified portion of the twill piece 16.

In addition, the pressing force of the clamp cylinder 5 is set to be larger than the bulging force in a steady state of the coin 16 passing through this segment, and the weight of the upper frame 2 is calculated by subtracting a predetermined bulging force from the pressing force of the clamp cylinder 5. The pressing force of the ram cylinder 13 is set so as to overcome this.

Next, the operation of the above configuration will be explained.

To explain based on FIG. 4, first, the clamp cylinder 5
The scale pressure is set.

In this case, each roll of 5 bears 14, ~ 145, 151
If the bulging force applied to ~155 in the steady state of pulling out is 1 bear f = 5, and the total is F = 5 x 5 = 250t, then the pressing force of the clamp cylinder 5 is set with a margin of, for example, 5M. Let P, = 30 melons. Then, during casting preparation and when inserting and withdrawing the dummy bar, no bulging force acts, so that P,=30 weights and the weight of the upper frame 2 (for example, 2 weights) are applied to the ram cylinder 13 via the sub-saddle rod 10. For example, considering a margin of 25 tons, the pressing force of this ram cylinder 13 is P,=3
0 mountains, 12 enemies, 25 tons = breasts are set. During preparation for casting and when inserting and pulling out a tummy bar, the worm gear mechanism 11 is activated via the drive shaft 12 from the outside of the motor to move the subaper rod 10 up and down, thereby adjusting the distance between the upper and lower rolls 14, - 145, 151 - 155. Q is set in advance.Next, when continuous casting is started from the above state and the key piece 16 is drawn into the segment, the pressing force of the ram cylinder 13 is automatically switched as follows.

That is, the mirror piece 16 is the roll 14.~145,15,~1
55, a bulging force (F = 25) acts on the ram cylinder 13, so the ram cylinder 13 is affected by the pressing force (P, = 30) of the clamp cylinder 5 and the weight of the upper frame 2 (P, = 30).
2) minus the bulging force, that is,
30 enemies, 12 melons - 25 = 7 enemies will be added. Therefore, the pressing force of the ram cylinder 13 is set to P with a margin of 1.
2 = 7 enemies, 11 = 8 skins You can switch automatically. However, as the casting speed decreases from the steady state,
The final end of the unsolidified portion 16a of the rust piece 16 approaches the mold, and the rolls 141 to 145, 15, to 155 and the coin piece 1
There may be a gap between the two.

As a result, the bulging force decreases, so it is necessary to reduce the roll interval Q, but according to the device of this embodiment,
The roll interval Q is automatically reduced and the blind pieces 16 can be supported appropriately. That is, if the bulging force in this unsteady state is, for example, F = 20 melons, then the ram cylinder 13 has a force of 30 to 12 - 20 melons = 12
The enemy will be added, and the pressing force of the ram cylinder 13 (P
2 = 8 enemies) is 12M - 8 enemies = 4 enemies. Therefore, the piston rod 1 of the ram cylinder 13
3a is lowered slightly, and the upper rolls 14, .

Then, the gap with the coin piece 16 disappears, the bulging force increases again, and the rust piece 16 is properly supported. Next, as shown in FIG. 5, consider the segment in which the final end A of the unsolidified portion 16a of the coin coin 16 is located. Assuming that the final end A is located at the center roll 14, a large bulging force (for example, f, = 5) is applied to the first roll 14 on the inlet side, and A slightly smaller bulging force (for example, f3=45t) is applied to the roll 142, and an even smaller bulging force (for example, f3=35t) is applied to the third roll 143.
takes the fourth and fifth rolls 144,145
The bulging force will not act on . Therefore, in this case, it is necessary to maintain the roll interval Q in a steady state at the first roll 141, but
~5th point, it is necessary to narrow the roll interval Q according to the shrinkage of the coin. On the other hand, according to the configuration of this embodiment, it is possible to deal with this as follows.

In other words, the pressing force of the clamp cylinder 5 (P, = 30)
acts on the four smoothing rods 10, so each rod acts on 75 tons, and a total of 15 rods act on the two smoothing rods 10a on the inlet side. On the other hand, since the bulging force acting on both the smoothing rods 10a on the inlet side is considered to be all of 5 and f2 = 45, and half of f3 and 35t, that is, 17.5, the bulging force acting on both the smoothing rods 10a on the inlet side is two ram cylinders 1
The force acting on 3 is 15 mountains - 5 - 45t - 17.5t
=27.5t. Assuming that the pressing force of all the ram cylinders 13 has a ratio of 8 as described above, the pressing force of each ram cylinder 13 will be 2, and the total pressing force of the two ram cylinders 13 in the inlet example will be 4M. Since the ratio is 27.5t<4, the piston stems 1 of the two ram cylinders 13 on the inlet side
3a is not pushed down and maintains a steady state.

If we consider the force that acts on the two smoothing rods 10b on the exit side, this smoothing rod 10b.

The head lob has half of f3=35t, or 17.5
Since only a bulging force of t acts on the two ram cylinders 13 on the outlet side, the force is 15 m - 17.5 t = 132.
5 will come into play. Therefore 132.5>4
Since it is an enemy, the piston stems 13a of the two ram cylinders 13 on the exit side are lowered, and the fifth roll 145
is lowered, and the twill piece 16 is pressed against the twill piece 16 in an attempt to prevent a gap from forming between the coin piece 16 and the twill piece 16. What should be noted here is that the piston stem 5a of the clamp cylinder 5 and the upper frame 2 are connected by a pin 9, and the upper frame 2 is rotatable around the pin 9 times.

Therefore, in the above case, the upper frame 2 rotates about 9 pins in the direction of arrow A, and all of the first to fifth rolls 141 to 145 come into contact with the mirror piece 16 with appropriate pressure. The reason why the ram cylinder 13 with a stroke of 1 to 3 strokes is used in this embodiment is to prevent the upper rolls 14 to 145 from pushing down the uncoagulated coins too much.

As described above, according to the present invention, even if the final end of the unsolidified portion of the coin is located at the center of the segment, the piston stems of the two second cylinder devices on the entrance side are not pushed down by the bulging force. , Only the piston stems of the two second cylinder devices on the entry/exit side are pushed down by the first cylinder device because there is no bulging force, and the upper frame rotates around the pin as a fulcrum and is supported by the upper frame. Each roll is pressed against the coin with appropriate pressure.

Therefore, it is possible to immediately follow fluctuations in the bulging force and maintain an appropriate roll spacing at all times.

[Brief explanation of drawings]

The figures show one embodiment of the present invention, in which Fig. 1 is a side view, the left half of Fig. 2 is a front view, the right half of Fig. 2 is a sectional view taken along the low D line of Fig. 1, and Fig. 3 4 is an enlarged sectional view of the ram cylinder portion, and FIGS. 4 and 5 are schematic explanatory views showing how the roll interval is adjusted. 1... Lower frame, 2... Upper frame, 3... Side frame, 5... Clamp cylinder (first cylinder device),
9...pin, 10...subasa rod, 11...
Worm gear mechanism (interval adjustment device), 13... Ram cylinder (second cylinder device), 14, ~ 145, 15
・~155... Roll, 16... Money piece, 16a... Unsolidified portion, Q... Roll interval. Figure 1 Figure 5 Figure 2 Figure 3 Figure 4

Claims (1)

[Claims] 1. In a segment constituting a slab conveyance path, side frames are erected at both ends of the lower frame of the segment, a first cylinder device supported by the side frames is provided, and a piston stem of the first cylinder device is provided. The upper frame is rotatably connected to the upper frame via a pin, and a second cylinder device is provided in the square of the lower frame. A spacer rod is provided that comes into contact with the upper surface of the piston stem, and a distance adjustment device is provided that adjusts the distance between the upper and lower rolls supported by both the upper and lower frames by moving the spacer rod up and down. The pressing force of the first cylinder device is set larger than the bulging force, and the second cylinder device is set so as to overcome the force obtained by subtracting a predetermined bulging force from the pressing force of the first cylinder device and the weight of the upper frame. A roll spacing adjustment device for continuous casting equipment, characterized in that the pressing force is set.