KR20200064827A - Mold vivrated apparatus - Google Patents

Abstract

The present invention provides a mold vibrating apparatus which comprises: a mold vibrating means applying vibration at a set cycle to a mold through which molten steel passes; and a load increasing means applying a compressive force to the mold so that a tensile force does not act on the mold vibrating means. The mold vibrating apparatus of the present invention can cut down on maintenance costs by reducing damage to facility by load reversal in high-speed casting.

Description

Mold vibration device {MOLD VIVRATED APPARATUS}

The present invention relates to a mold vibration device that reduces maintenance costs.

It should be noted that the contents described in this section merely provide background information about the present invention and do not constitute the prior art.

In order to stably produce high-quality cast iron (slabs) in a continuous casting machine, it is required to grow a solidified shell evenly in a mold where solidification of molten steel begins.

If the coagulation shell is non-uniform, it is difficult to produce high-quality cast iron, and in severe cases, the coagulation shell may tear and cause equipment damage accidents due to spewing.

Therefore, for uniform solidification shell growth in the initial solidification mold, uniform heat transfer is required, and cooling is very important.

In order to realize this physical behavior, a mold powder is used in a general continuous casting machine, and the mold powder must be continuously introduced.

A device for inducing and controlling such mold powder inflow is a mold vibration device, and serves to generate vibrations of a certain amplitude and frequency in the vertical direction.

With the growth of the mini mill market, high-speed casting technology was required, and POSCO developed a player capable of always casting speed of 6.5 m/min. Compared to conventional blast furnace mill, the casting speed is about 6 times faster and boasts the world's highest discharge rate.

However, as the casting speed increases, the frequency of the mold vibrator also increases, requiring a much larger specification than the existing mold vibrator.

For example, when the mold oscillates up and down of an ideal sinusoidal wave, when the frequency increases, the amplitude of the load increases accordingly with the square of the frequency.

For example, when the casting speed is increased 6 times compared to the blast furnace mill, the magnitude of the amplitude of the load increases 36 times.

In addition, the amplitude of the acceleration also increases in proportion to the square of the frequency, especially when the magnitude of the acceleration when the mold descends is 1 g (g=9.81 m/s²) or more, which is fatal to the device.

1(a) and 2(a), a load reversal phenomenon occurs in which a direction of a load acting on an actuator or the like is reversed twice in one cycle, and the component life is shortened due to the load reversal phenomenon. There is a problem in that it is difficult to control the vibration pattern due to the influence of a mechanical tolerance such as a pin.

Of course, with respect to the acceleration standard, the operation was possible with sufficient margin in the conventional blast furnace mill, but there is a problem in that the risk of exceeding the standard is high because the acceleration increases tens of times or more during high-speed casting.

Particularly, in order to improve the inflow of mold powder, if the distortion rate is applied to the vibration waveform, the waveform becomes sharper, and the magnitude of the acceleration is further increased, which increases the risk, and thus, the operational range is also reduced.

KR 10-1105917

As an aspect of the present invention, an object of the present invention is to provide a mold vibration device capable of reducing damage to equipment due to load reversal occurring in high-speed casting, improving operation productivity, and reducing maintenance costs.

As one aspect for achieving the above object, the present invention is a mold vibration means for applying vibration at a set cycle on the mold through which the molten steel passes; And a load increasing means for applying a compressive force to the mold so that the tensile force does not act on the mold vibrating means.

Preferably, the mold vibration means applies vibration in the vertical direction to the mold, and the load increasing means can apply a compressive force in the downward direction to the mold.

Preferably, the load increasing means may apply a compressive force to the mold vibrating means through the mold when a load reversal phenomenon in which a tensile force acts on the mold vibrating means occurs.

Preferably, the load increasing means may be provided as a fixed load member having a fixed default value of the compression force.

Preferably, the fixed load member includes: a coil spring providing an elastic force for applying a load to the mold; And, it is elastically supported by the coil spring, the buffer fixing member is slidably installed on the load bracket of the load increasing means; may include.

Preferably, the load increasing means may be provided with a variable load member that controls the compression force acting on the mold by adjusting the set compression force itself.

Preferably, the load increasing means, the fixed load member is fixed to the default value of the set compression force; And a variable load member that controls the compression force acting on the mold by adjusting the set compression force itself.

Preferably, the variable load member may be composed of a cylinder member whose compression force is set by hydraulic pressure or pneumatic pressure.

Preferably, the load increasing means includes: a load bracket disposed on an upper side of the mold bracket installed in a lower region in the height direction of the mold; And a load application member installed on the load bracket and capable of applying a compressive force to the mold bracket.

Preferably, in response to a change in the amplitude condition of the mold vibration means, it may further include a height adjustment means for adjusting the height of the load increasing means.

Preferably, the height adjustment means, an adjustment frame in which a plurality of the load increasing means is installed; And, it is installed around the mold, the lifting member for elevating the adjustment frame; may be provided.

According to an embodiment of the present invention, it is possible to reduce damage to equipment due to load reversal occurring in high-speed casting to improve operation productivity and reduce maintenance costs.

1 is a view showing the load acting before and after the load increasing means of the present invention is applied.
FIG. 2 is a view comparing the occurrence of a load reversal phenomenon before and after the load increasing means of FIG. 1 is applied.
3 is a perspective view of a mold vibration device according to an embodiment of the present invention.
4A and 4B are views showing a descending and rising state of a mold according to another embodiment of the present invention.
4C is a conceptual diagram showing the behavior of the mold of FIGS. 4A and 4B according to the descending and rising states.
5A and 5B are diagrams illustrating a descending and rising state of a mold according to another embodiment of the present invention.
6 is a view showing a mold vibration device according to another embodiment of the present invention.
7 is a view showing a mold vibration device according to another embodiment of the present invention.
8 is a view showing an arrangement state of a mold vibration device according to another embodiment of the present invention.

Hereinafter, preferred embodiments of the present invention will be described with reference to the accompanying drawings. However, embodiments of the present invention may be modified in various other forms, and the scope of the present invention is not limited to the embodiments described below. In addition, embodiments of the present invention are provided to more fully describe the present invention to those skilled in the art. The shape and size of elements in the drawings may be exaggerated for a more clear description.

Hereinafter, with reference to Figures 1 to 8 will be described in detail with respect to the mold vibration device 10 according to an embodiment of the present invention.

The mold vibrating device 10 according to an embodiment of the present invention may further include a mold vibrating means 100 and a height increasing means 300 for the load increasing means 200.

Referring to FIG. 3, the mold vibrating means 100 for applying vibration at a cycle set in the mold 20 through which the molten steel passes, and the compressive force to the mold 20 so that tensile force does not act on the mold vibrating means 100. It may include a load increasing means 200 for applying.

The mold 20 may include a mold 21 that primarily solidifies molten steel passing therethrough, and a mold table 23 that supports the mold 21.

At this time, the load increasing means 200 may be installed on the mold table 23, the mold table 23 may be formed with a mold bracket 25 to which the load increasing means 200 is connected.

In the mold bracket 25 of the mold 20, a load acting point P in which the load increasing means 200 comes into contact is formed, and when the mold 20 vibrates in the vertical direction, the load acting point P also vibrates in the vertical direction. Can be.

At this time, a downward direction load may be applied through the load increasing means 200.

3, the mold vibration means 100 may be installed on the lower side of the mold (20).

The mold vibrating means 100 may be installed in a direction supporting the load of the mold 20.

The mold vibration means 100 may be configured as an actuator that applies vibration in the vertical direction while supporting the load of the mold 20.

The mold vibrating means 100 is respectively installed on a pair of mold tables 23 of the mold 20, and can apply vibration to the mold 20 at a constant cycle in the vertical direction.

The mold vibration means 100 may be fixed to the ground while the lower side is supported by an installation structure (not shown).

3 to 4B, when a load reversal phenomenon in which a tensile force acts on the mold vibration means 100 occurs, a compressive force is applied to the mold 20 to remove the tensile force by applying a compressive force to the mold vibration means 100. Can be.

The load increasing means 200 is installed in a support structure (not shown) disposed around the mold 20 to apply a compressive force to the mold 20.

The load increasing means 200 serves to prevent the tensile force from being applied to the mold vibration means 100 by increasing the load on the self-weight G of the mold 20.

3 to 4B, the mold vibrating means 100 applies vibration in the vertical direction to the mold 20, and the load increasing means 200 compressive force in the downward direction with respect to the mold 20 Can be authorized.

When the mold vibration means 100 applies vibration to the mold 20 in the vertical direction, when the mold 20 reaches the upper end point of the stroke distance R, the mold 20 and the motion of the mold vibration means 100 The direction can be switched from ascending to descending.

The load increasing means 200 can continuously apply the load in the direction in which the mold 20 descends.

1 (a) and 2 (a), the mold 20 may have a self-weight (G) of the mold 20 and a load (F) of the mold vibration means 100.

1 (b) and 2 (b), the mold 20 has a weight (G) of the mold 20 and the load (F) of the mold vibration means 100 and the load increasing means 200 The load H can act.

1 (a) and 2 (a), in the case of high-speed casting, the mold 20 is raised and then the compression force acting on the mold vibrating means 100 when it is lowered is converted into tensile force, thereby causing vibration. A load reversal phenomenon in which two load reversal regions M are formed in the cycle may occur.

Here, the load reversal phenomenon means that the load acting on the mold vibration means 100 is converted from a compressive force (compressed load) to a tensile force (tensile load).

That is, due to the load reversal phenomenon, the load acting on the mold vibration means 100 may be converted from a compressive force to a tensile force.

When the mold 20 vibrates at high speed in high-speed casting, when the mold 20 descends in the direction of gravity by the mold vibrating means 100, a load reversal phenomenon in which the direction of the load is reversed in the mold vibrating means 100 As it occurs, the tensile force may act on the mold vibration means 100.

In this case, when the mold 20 descends, a tensile force acts on the mold vibration means 100 such as an actuator, and when the mold 20 rises, a compressive force may act on the mold vibration means 100.

As described above, when a load reversal phenomenon repeatedly occurs in the mold vibrating means 100, the mold vibrating means 100 may alternately and repeatedly act on the mold vibrating means 100 and weaken the life of the mold vibrating means 100.

As described above, when the period of maintenance of the mold vibrating device 10 is shortened, there may be a problem of a decrease in productivity due to the operation stoppage and an increase in the maintenance cost of the mold vibrating device 10.

In addition, when the mold vibrating means 100 vibrates the mold 20 at a high speed, when a load reversal occurs in the mold vibrating means 100 and a tensile force acts on the mold vibrating means 100, the mold vibrating means 100 There may be a problem that control of the pain relief pattern may be difficult due to the influence of a part having mechanical tolerances, such as a pin forming a connection point Q between the mold 20 and the mold 20.

1 (b) and 2 (b), the mold oscillation apparatus 10 of the present invention moves the vibration center line L of the load acting on the load increasing means 200 upward, thereby reversing the load. By removing the region M, tensile force acts on the mold vibration means 100.

Accordingly, the mold vibrating device 10 of the present invention reduces the breakage of equipment by preventing the tensile force from acting on the mold vibrating means 100 by applying a load to the mold 20 by the load increasing means 200. It has the effect of improving and reducing maintenance costs.

In addition, the influence of mechanical tolerances such as pins forming a connection point Q between the mold vibration means 100 and the mold 20 may be neglected without tensile force acting on the mold vibration means 100. There is an effect that can be easily controlled pattern.

For example, when the mold 20 vibrates at a high speed and a load reversal occurs, the tensile force may act on the mold vibrating means 100 instead of the compressive force.

That is, when the mold 20 vibrates at a high speed, a load reversal phenomenon may occur in the mold vibrating means 100 as the amplitude A of the load applied from the mold vibrating means 100 composed of an actuator increases.

Specifically, when the frequency increases, the amplitude A of the load acting on the mold vibration means 100 such as an actuator increases, and when the frequency increases above a certain size, the amplitude A of the load increases A load reversal phenomenon occurs while exceeding the size.

3 to 4B, when the load reversal phenomenon in which a tensile force acts on the mold vibrating means 100, the load increasing means 200, the mold vibrating means 100 via the mold 20 A compressive force can be applied to.

4A to 5B, the load increasing means 200 may be provided as a fixed load member 210 in which the default value of the set compression force is fixed.

Referring to Figure 4a, the fixed load member 210 may be composed of a coil spring 211 having a constant elastic modulus.

At this time, the upper end of the coil spring 211 may be fixed to the load bracket 250, and the lower end may be fixed to the mold bracket 25 of the mold 20.

Referring to Figure 4b, the coil spring 211 can be fixed to the lower side of the load bracket 250 of the load increasing means 200, and when the mold 20 is elevated, the coil spring 211 is compressed while the mold 20 ) Can be applied with a larger load.

For example, in the case shown in FIG. 4A, the coil spring 211 is relatively less compressed than the case shown in FIG. 4B.

That is, in the case shown in FIG. 4A, the basic compression amount of the coil spring 211 is present.

Therefore, the coil spring 211 illustrated in FIG. 4B can exert a relatively large compressive force compared to the coil spring 211 illustrated in FIG. 4A.

4A and 4B, a height adjusting means 300 for adjusting the height of the load increasing means 200 may be installed in the load increasing means 200.

Of course, the compression force can be adjusted by adjusting the basic compression amount of the coil spring 211 of the load increasing means 200.

4C is a conceptual diagram showing the behavior of the mold 20 of FIGS. 4A and 4B according to the descending and rising states.

Referring to FIG. 4C, as shown in FIG. 4A, the mold bracket 25 is lowered by R/2 corresponding to half of the stroke distance R based on the center of vibration line L while the mold 20 is lowered. It is disposed at a spaced apart position and can receive relatively small compression force from the coil spring 211.

Referring to FIG. 4C, as shown in FIG. 4B, the mold bracket 25 is spaced upward by R/2 corresponding to half of the stroke distance R with respect to the center of vibration line L in the state where the mold 20 is raised. It can be arranged in a position to receive a relatively large compression force from the coil spring 211.

Referring to FIG. 4C, it can be seen that the coil springs 211 shown in FIGS. 4A and 4B are in a contracted state than the original lengths of the coil springs 211, and both have a basic compression amount.

5A and 5B, the fixed load member 210 is elastically supported by the coil spring 211 and the coil spring 211 providing elastic force for applying a load to the mold 20 And, it may include a buffer fixture 215 that is slidably installed on the load bracket 250 of the load increasing means 200.

Referring to FIG. 5B, the buffer fixing body 215 may apply a load to the mold bracket 25 through the elastic force provided by the coil spring 211 while the coil spring 211 is compressed.

The buffer fixing body 215, a buffer support 216 contacting the mold bracket 25, and a buffer rod connected to the buffer support 216 and installed through the coil spring 211 and the load bracket 250 217 and a buffer stopper 218 installed at a rear end of the buffer rod 217.

For example, in the case shown in FIG. 5A, the coil spring 211 is relatively less compressed than the case shown in FIG. 5B.

Therefore, the coil spring 211 illustrated in FIG. 5B can exert a relatively large compressive force compared to the coil spring 211 illustrated in FIG. 5A.

The buffer support 216 may be formed of an anti-vibration rubber contacting the mold bracket 25.

When the buffer support 216 is made of an anti-vibration rubber or the like having elasticity, the impact when the compressive force is applied to the mold 20 by the buffer support 216 and the coil spring 211 can be buffered.

Referring to FIG. 6, the load increasing means 200 may be provided with a variable load member 230 that controls the compression force acting on the mold 20 by adjusting itself to the set compression force.

The load increasing means 200 may be provided with a variable load member 230 capable of adjusting the set compression force.

The variable load member 230 may be composed of a cylinder member whose compression force is set by hydraulic or pneumatic pressure.

In one example, the cylinder member may be composed of a hydraulic cylinder or an air cylinder.

In this way, the size of the compression force with respect to the mold 20 can be adjusted while the value of the hydraulic pressure or pneumatic pressure set in the cylinder member is adjusted.

Accordingly, in response to the amount of change in the stroke distance R applied by the mold vibration means 100 to the mold 20, the load that the load increasing means 200 starts to exert a compressive force on the mold 20 The height of the working point P can be adjusted.

Referring to FIG. 7, the load increasing means 200 is a fixed load member 210 having a fixed default value of the set compression force, and a variable for adjusting the compression force acting on the mold 20 by adjusting the set compression force itself. A load member 230 may be provided.

For example, the fixed load member 210 is composed of a coil spring 211 having a constant elastic modulus, and the variable load member 230 may be composed of a cylinder member capable of adjusting compression force.

For example, a cylinder member, which is a variable load member 230, is installed under the load bracket 250, and a coil spring 211, which is a fixed load member 210, may be installed under the variable load member 230. .

The upper side of the coil spring 211 is fixed to the lower end of the cylinder rod 233 of the cylinder member, and the lower side of the coil spring 211 may be in contact with the mold bracket 25.

Referring to Figure 6, the variable load member 230 may be composed of a cylinder member whose compression force is set by hydraulic or pneumatic.

The cylinder member may be composed of a hydraulic cylinder or an air cylinder.

The cylinder member may be composed of a cylinder body 231 to which hydraulic or pneumatic pressure is provided and a cylinder rod 233 that can move back and forth from the cylinder body 231.

The compression force may be adjusted while the hydraulic pressure of the hydraulic cylinder or the air pressure of the air cylinder is adjusted by the adjustment control means 400.

As the hydraulic pressure of the hydraulic cylinder or the pneumatic pressure of the air cylinder is adjusted, the load acting point P of the load increasing means 200 in response to the change in the stroke distance R applied by the mold vibration means 100 to the mold 20 The height adjustment of can be adjusted.

Referring to Figure 3, the load increasing means 200, the load bracket 250 and the load bracket 250 disposed on the upper side of the mold bracket 25 is installed in the lower region in the height direction of the mold 20 It is installed on, it may be provided with a load applying member capable of applying a compressive force to the mold bracket (25).

The mold bracket 25 of the mold 20 may be installed in a lower region in the height direction of the mold 20.

The load bracket 250 may be spaced apart in the height direction from the mold bracket 25 and disposed on the upper side.

The load applying member may be composed of at least one of a fixed load member 210 having a fixed default value of a set compression force or a variable load member 230 controlling a compression force acting on the mold 20 by adjusting itself. Can be.

Accordingly, the load acting point (P) in which the load applying member of the load increasing means 200 is in contact with the mold bracket 25 is disposed in the lower region in the height direction of the mold 20, so that the load acting point P is the mold 20 ) And the connection point (Q) of the mold vibration means (100).

For example, by placing the load acting point (P) of the load increasing means 200 in the lower portion in the height direction of the mold 20, the distance between the load acting point (P) and the connecting point (Q) is reduced, thereby increasing the load means ( There is an effect that the load applied to the mold 20 by the 200 can act more stably on the connection point Q between the mold 20 and the mold vibrating means 100 and the mold vibrating means 100.

The load increasing means 200 may adjust the compressive force acting on the mold 20.

8, the mold vibration device 10 is a height adjustment means for adjusting the height (position) of the load increasing means 200 in response to a change in the stroke distance (R) condition of the mold vibration means 100 It may further include (300).

The height adjusting means 300 corresponds to the amount of change in the stroke distance R applied by the mold vibrating means 100 to the mold 20, and the load increasing means 200 can adjust the height.

For example, the load increasing means 200 may be adjusted in height as the load increasing means 200 is elevated by the height adjusting means 300.

Accordingly, in response to the amount of change in the stroke distance R applied by the mold vibration means 100 to the mold 20, the load that the load increasing means 200 starts to exert a compressive force on the mold 20 The height of the working point P can be adjusted.

The height adjustment means 300 may integrally elevate the plurality of load increasing means 200 installed on the mold 20.

Referring to Figure 8, the height adjustment means 300, a plurality of the load increasing means 200 is installed in the control frame 310, and the mold 20 is installed around, the adjustment frame 310 It may be provided with a lifting member 330 to elevate.

Specifically, a plurality of load increasing means 200 is integrally installed on the adjusting frame 310 of the height adjusting means 300, and the lifting member 330 integrally mounts the plurality of loading means by elevating the adjusting frame 310. Can be elevated to

The load increasing means 200 may be respectively installed on a pair of mold tables 23 supporting the lower side of the mold 21 of the mold 20.

In the load increasing means 200, two load increasing means 200 are arranged on the left side of the mold table 23 spaced apart in the front-rear direction, and before and after the two load increasing means 200 on the right side of the mold table 23. It can be arranged spaced apart in the direction.

That is, a total of eight load increasing means 200 may be disposed on the pair of mold tables 23, and the eight load increasing means 200 are integrally elevated by the height adjusting means 300 to adjust the height. Can be.

The eight load increasing means 200 are integrally connected by the adjustment frame 310, and the adjustment frame 310 may be elevated by the lifting member 330 installed around the mold 20.

Of course, although not shown in the drawings, the hydraulic or pneumatic sealer members are individually installed in the eight load increasing means 200, and the eight individually installed cylinder members are synchronized to the control control means 400. Of course it can be controlled by.

Although the embodiments of the present invention have been described in detail above, the scope of the present invention is not limited thereto, and it is possible that various modifications and variations are possible without departing from the technical spirit of the present invention as set forth in the claims. It will be apparent to those of ordinary skill in the field.

10: mold vibration device 20: mold
21: mold 23: mold table
25: mold bracket 100: mold vibration means
200: load increasing means 210: fixed load member
211: coil spring 215: buffer fixed body
216: buffer support 217: buffer rod
218: buffer stopper 230: variable load member
231: cylinder body 233: cylinder rod
250: load bracket 300: height adjustment means
310: adjustable frame 330: lifting member
400: regulating control means A: amplitude
F: Load of mold vibration means G: Self-weight
H: Load of load increasing means L: Vibration center line
M: Load inversion area P: Load action point
Q: Connection point R: Stroke distance

Claims (11)

Mold vibration means for applying vibration at a set cycle on the mold through which the molten steel passes; And,
A mold vibration device comprising; a load increasing means for applying a compressive force to the mold so that the tensile force does not act on the mold vibration means.
According to claim 1,
The mold vibration means applies vibration in the vertical direction to the mold,
The load increasing means is a mold vibration device for applying a compressive force in the downward direction to the mold.
According to claim 1, The load increasing means,
A mold vibration device characterized in that when a load reversal phenomenon in which a tensile force acts on the mold vibration means occurs, a compressive force is applied to the mold vibration means via the mold.
According to claim 1, The load increasing means,
A mold vibration device equipped with a fixed fixed load member with a default value of the set compression force.
According to claim 4, The fixed load member,
A coil spring that provides elastic force to apply a load to the mold; And,
A mold vibration device comprising; a buffer fixing member elastically supported by the coil spring and slidably installed on the load bracket of the load increasing means.
According to claim 1, The load increasing means,
A mold vibration device provided with a variable load member that controls the compression force acting on the mold by adjusting the set compression force itself.
According to claim 1, The load increasing means,
A fixed load member having a fixed default value of the set compression force; And,
And a variable load member that controls the compression force acting on the mold by adjusting the set compression force itself.
The method of claim 6 or 7,
The variable load member is a mold vibration device characterized in that it consists of a cylinder member whose compression force is set by hydraulic or pneumatic.
According to claim 1, The load increasing means,
A load bracket disposed on the upper side of the mold bracket installed in the lower area in the height direction of the mold; And,
It is installed on the load bracket, the mold vibration device having a; load applying member capable of applying a compressive force to the mold bracket.
According to claim 1,
And a mold height adjusting means for adjusting the height of the load increasing means in response to a change in the amplitude condition of the mold vibrating means.
The method of claim 10, wherein the height adjustment means,
Adjustment frame is installed a plurality of the load increasing means; And,
It is installed around the mold, the lifting member for elevating the adjustment frame; provided with a mold vibration device.

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