JPS62237954A - Crusher - Google Patents

Abstract

(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.

Description

DETAILED DESCRIPTION OF THE INVENTION Field of Industrial Application This invention relates to a crushing device, and in particular a crushing device for crushing a raw material stone made of rocks, ores, etc. to a desired particle size for making sand, or for sizing (cutting corners). ) relates to an impact-type crushing device useful for

BACKGROUND OF THE INVENTION Conventionally, this type of impact crushing device is known as shown in FIGS. 6 to 8. Such an impact type crushing device is disclosed in Japanese Patent Publication No. 53-33785.

That is, in FIG. 8, inside a rotor 1 (see FIG. 6) mounted on a vertical shaft via a bearing 2 (see FIG. 6), there is a central distributor provided at the center of the rotor 1. Wings 21, 22 and 25 are arranged to rotate around the center of rotation of the wing 20, and the tip of the wing 25 has, for example, a carbide tip 24. The tip wing 24 to which is attached is integrally fixed.

Therefore, raw material ore (hereinafter referred to as raw material) fed from the raw material supply device 11 shown in FIG. 6 to the central distributor 20 is transferred to the blades 21, 22 and
5, from the tip blade 24 to the outlet 19 (see FIG. 7), from where it is discharged to the outside of the rotor 1.

As shown in FIG. 6, the discharged raw material collides with a dead stock 15 (or a ring liner 16 (two-dot chain line) arranged) formed as a collision part inside the housing 8 that houses the rotor 1. do.

The type in which a dead stock 15 is provided and the raw material collides with the dead stock 15 of the iron is for grain size adjustment (grain shape correction) of the raw material, and the type in which a ring liner 16 is provided and the raw material collides with the ring liner 16. The one is for crushing raw materials.

In such an impact type crushing device, the blades 21, 22, 25, etc. arranged on the rotor 1 are slightly curved so as to surround the central distributor 20 (see Fig. 6), which is the center of the rotor 1. provided. This means that the input raw material is
．． 22 and 25 before reaching the tip blade 24, it accumulates in this curved part and forms a so-called dead stock 17, thereby damaging the inner wall of the rotor 1 or the base material of the tip blade 24 due to collision with the raw material. It is intended to protect against wear.

In the rotor 1 shown in FIG. 8, two outlets 19 are provided around the rotor 1, and in order to form two dead stocks 17 accordingly, each blade 21, 22.
5 and the tip H24 are approximately 180 mm along the circumferential direction of the rotor 1.
“They are located at an angle of .

Problems with the Prior Art By the way, the following technical problems have been pointed out in the impact type crushing device having such a structure.

First, as shown in Fig. 8, the effect of protecting the tip blade 24 by the dead stock 17 is generally considered to be greater as the raw material particles become finer due to the relationship with the angle of repose of the powder. Become. However, most of the raw materials actually supplied to the rotor 1 are relatively large particles with a particle size of 20 to 8011, and when deposited as dead stock as described above, the The surface becomes unstable.

For example, on such a deposition surface, as shown in FIG. 9, the collapse and formation of dead stock 17 locally repeats (the broken line and two-dot chain line in FIG. ), each time the tip base material of the tip wing 24 is exposed.

If the base material of the tip blade 24 that was covered by the dead stock 17 is exposed, wear will occur there due to collision with the raw material.

In the tip blade disclosed in Japanese Utility Model Application Publication No. 58-73347, the carbide tip can be used on both the rotor center side and the rotor outer peripheral side, and the carbide tip is of an inverted type to extend the wear life. However, no consideration is given to preventing the above-mentioned wear of the tip blade base material due to fluctuations in dead stock.

In the tip blade disclosed in Japanese Unexamined Patent Publication No. 59-95945, a carbide tip is attached to the chamfered part of the tip blade, for example,
The collision surface with the raw material is inclined at an angle of approximately 45° with respect to the rotor center side. In this case, the angle formed at the tip of the tip blade is the angle of repose of the raw material (dead stock) (approximately 40°
), and sufficient dead stock is not formed at this tip, for example, hunting portion B in FIG.

As shown in FIG. 2, the base material surface of the tip blade 24 is exposed to the raw material due to the fluctuation of the dead stock 17, and abrasion occurs here due to collision with the raw material.

In this way, conventional impact-type crushing equipment attaches a carbide tip to the tip of the tip blade, and uses this tip to protect the tip of the tip blade base material from wear due to collision with the raw material. In this case, it is not possible to prevent wear at the exposed portion caused by fluctuations in the dead stock of the tip blade base material.

In addition, as shown in FIG. 9, the above-mentioned unstable layer portion of the dead stock is caused by the above-mentioned raw material P.
The particle size r varies by approximately 1/2 of the particle size r (raw material P, -p2'), and this 1/2 particle size r is the sieve opening in the sieving process, which is the preceding process of the crushing process. Determined by dimensions.

In such a situation, as shown in FIG. 9, the solid line indicated material P that rolls on the inclined surface of the dead stock 17 as described above and is ejected in the direction of the arrow A is moved from the center of the rotor to the dead stock 17. It slides outward (arrow A) on the surface (sloped surface) at a certain speed ■.

On the other hand, as can be seen from FIG. 10, since the rotor 1 is rotating at a certain angle ω, the raw material P rolling on the slope of the dead stock 17 has a constant component force 2 against this slope.
mvω works. This is the Coriolis force. As shown in FIG. 9, the raw material P is the carbide tip 2 of the tip blade 24.
4. When it reaches point l, the carbide tip 24. side surface (tip surface 24 of tip wing 24)
The frictional force caused by the raw material acts on the material.

In the tip blade 24 of the type in which a hard member such as a carbide tip is not provided on the tip surface 24 as disclosed in Japanese Patent Application Laid-Open No. 59-95954, the tip blade 24 has a carbide tip 24. A large 1% Etll as shown in the hatched area B2 in FIG. 9 is formed on the tip surface 24t by the raw materials P3 and P4 that have passed through the tip.

Further, in the tip blade disclosed in the above-mentioned Japanese Utility Model Publication No. 58-733478, a hard member is fixed to the entire tip surface to prevent the occurrence of friction as shown in the hunting portion B2 in FIG. However, the relationship between the dimensions of the hard member to be fixed and the particle size of the raw material is not clear.

That is, 5. The length of the raw material sliding surface in the radial direction of the rotor of the cemented carbide chip is made small enough to eliminate the influence of Coriolis, and the raw material is held until the speed of the raw material in the radial direction of the rotor is accelerated. It must be long enough to However, if this length is made too long, the amount of expensive carbide chips increases, which is uneconomical.

■ In the above case, especially in order to solve the problem mentioned in (■) above, an attempt is made to increase the dimension of the carbide tip in the rotor circumferential direction to correspond to the fluctuation range of the unstable layer part of the dead stock. However, as the carbide tip becomes larger, the bending stress applied to the joint of the carbide tip due to the colliding raw materials also increases accordingly.

In this case, an increased concentration of stress will occur at the joint between the carbide tip and the tip blade due to the increased size of the carbide tip, which may cause the carbide tip to be damaged or fall off from the tip blade. Become.

Purpose of the Invention Therefore, the main purpose of the present invention is to avoid stress concentration at the joint between the carbide tip and the tip blade, which is the base material of the carbide tip, and to prevent the carbide tip from falling off the tip blade. It is an object of the present invention to provide a crushing device which prevents wear caused by fluctuations in dead stock on a tip blade base material receiving dead stock, and extends the life of tip blades and carbide tips.

Structure of the Invention In order to achieve the above-mentioned object, the main means adopted by the present invention is to introduce the crushed materials that have been sorted by a sieve into a rotor that rotates at high speed, and to pass the crushed materials through the exit portion of the rotating rotor. Released outward from the carbide tip bonded to the base material,
In the crushing device that crushes the rotor by colliding with a collision surface around the rotating rotor, a groove extending along the joint is provided at or near the joint of the base material with the carbide chip; The dimension in the circumferential direction on the rotor center side is set to be 1/2 or more of the maximum particle size of the crushed material sorted by the sieve.

This is a carbide tip attached to the outlet end of the working rotor, and its dimension in the circumferential direction on the rotor center side is set to be 1/2 or more of the sieve pilot opening dimension during the previous process.

On the other hand, the unstable layer portion of the dead stock formed at the outlet end fluctuates in a width that is approximately 1/2 of the particle size of the raw material passing through the sieve opening during the previous step.

Therefore, the unstable layer portion of the dead stock is received by the carbide tip, and wear caused by fluctuations of the unstable layer portion of the dead stock in that portion is prevented.

Further, stress that tends to concentrate at or near the joint between the carbide tip and the tip blade base material is directed to the groove formed at or near the joint and is diffused there. This avoids stress concentration on the joint.

Effects of the Invention According to the present invention, the unstable layer portion of the dead stock formed near the rotor outlet can be received by the surface of the carbide tip in the circumferential direction on the rotor center side, and this carbide tip can be held. It is possible to prevent wear on the tip blade base material due to this dead stock fluctuation, and to reduce stress concentration at the joint between the carbide tip and the tip blade, which is the base material of the carbide tip. Since this can be avoided, it is possible to prevent the carbide tip 7 from falling off the tip blade.

The above objects, other objects, features and advantages of the present invention will become more apparent from the following detailed description of embodiments with reference to the drawings.

Fig. 1 is a schematic vertical sectional view of an impact crushing device according to an embodiment of the present invention, Fig. 2 is a plan view showing the internal structure of the rotating rotor in Fig. FIG. 4 is a side view showing how the carbide tip shown is attached to the tip blade, FIG. 11 shows a modified example of the carbide tip shown in FIG. 2, and is a side view showing another state of attachment to the tip blade. FIG. 12 are graphs showing the relationship between the radius of curvature of the tip corner of the carbide tip and the tensile stress generated at the collision portion shown in FIG. 11.

In addition, the following example is only one specific example of this invention, and the technical scope of this invention is not limited by this example. Further, the same reference numerals will be used to describe elements common to those described in FIG. 9.

In FIG. 1, the impact crushing bag W30 includes a housing 34 placed on a pedestal 35, and a lid 3 of the housing 34.
A crushing chamber 31 formed by 3 and 3 is provided. Lid 3
As shown by arrow C, there is a crushing chamber 3 approximately in the center of 3.
1 is provided with a raw material supply section 32 for supplying raw materials from above, and a hopper 36 is attached to this raw material supply section 32. Further, the pedestal 35 is formed with a discharge port 37 for dropping the raw material crushed in the crushing chamber 31 downward as shown by the arrow.

A rotor shaft 39 is disposed approximately in the center of the crushing chamber 31 and is vertically and rotatably supported by a bearing box 38 fixed to the upper surface of the pedestal 35. The lower end 39I of this rotor shaft 39 is inserted into the frame 35, and a pulley 40 driven by a drive device (not shown) disposed at a predetermined location is attached to the lower end 39I.

On the other hand, the upper end 39. of the rotor shaft 39 located approximately at the center of the crushing chamber 31. A hollow cylindrical rotating rotor 42 that rotates horizontally about the rotor shaft 39 is attached to the rotor 42 .

A bracket 44 is provided on the inner surface of the side wall of the housing 34, corresponding to the height position of the raw material discharge port 43 of the rotor 41.
A large number of anvils 42 are attached to the platen 44 so that the surface of collision with the raw material surrounds the rotating rotor 41.

In this case, the rotating rotor 41 functions almost in the same way as the rotor 1 explained in FIGS. 6 to 8 above, and the raw material introduced into the rotating rotor is
It is discharged outward from this rotating rotor 41.

That is, as shown in FIG. 2, inside the rotating rotor 4-1, the raw material that has been introduced into the center of the rotating rotor 41 is transferred to the rotating rotor 41, as can be seen from the explanation in FIG. are deposited as dead stock 17 at appropriate angles in the circumferential direction. Then, as the rotor 41 rotates at high speed, the deposited raw material passes through each dead stock 17 and is discharged outward from the raw material discharge port 43 formed in the circumferential side wall of the rotor 41.

Inside the rotating rotor 41, in order to form each dead stock 17, there is a space of about 1 in the circumferential direction of the rotating rotor 41.
Three partition plates 452 oriented in the radial direction of the rotor 41, three side walls 46 extending in an arc shape along the periphery of the rotor 41, and three tip blades 47 are arranged at an angle of 20 degrees.

On the other hand, at the tip of each tip blade 47 of the rotating rotor 41 shown in FIG. 2, as explained in FIG. A carbide tip 50 is fixed.

As can be seen from FIG. 3, this carbide tip 50 has a surface corresponding to the rotating rotor center side 51 of the carbide tip 50, and the dimension of this surface in the rotor circumferential direction is The opening size of the sieve during the sieving process, which is the previous process, is set to 172" or more.

Here, with reference to FIG. 4, a pre-process of such a crushing process will be briefly described. First, the raw material ore collected in a large size is normally put into a large raw material crusher 60 (show crusher) constituting, for example, a secondary crushing step. Here, the above-mentioned large-sized raw material is crushed according to the particle size required by the secondary crushing step 2, which is installed downstream in the flow direction of the raw material (arrow in the figure). In this case, as an example of the crusher constituting the secondary crushing process, for example, the embodiment apparatus shown in FIG.
0 is prepared.

Next, a sieving step M is provided between the first crushing step 1 and the second crushing step 2 to sieve the raw material to the particle size required by the second crushing step 2. The sieving process M+ is usually equipped with a vibrating sieve machine 61, and this vibrating sieve machine 61 is equipped with a vibrating sieve machine 61, which is equipped with a vibrating sieve machine 61, which is equipped with a vibrating sieve machine 61, which is equipped with a vibrating sieve machine 61, which is used to sieve raw materials that meet the above particle size into the secondary crushing process 2. A screen with the corresponding sieve opening size is attached.

In addition, the raw material larger than the above-mentioned particle size that remains after being sieved by this vibrating sieve machine 61 is fed to the upstream side of the second crushing process, and the crushing process is repeated until it reaches a size that can pass through the vibrating sieve machine 61. .

The impact crushing device 30 includes the above-mentioned sieving process M.

Raw materials having a predetermined particle size determined by the opening size of the vibrating sieve 61 inside are sequentially supplied.

On the other hand, for example, as shown in FIG. 3, the unstable layer portion Q (between the two-dot chain line and the broken line in FIG. area) is approximately 1/ of the particle size of the raw materials p, /, p, /, etc. passing through the sieve opening size during the sieving process.
It varies by a width r' (corresponding to the particle diameter radius) of 2.

Therefore, when the carbide tip 50 is configured as described above, the unstable layer portion Q of the dead stock 17 falls within the range of the rotor circumferential dimension t1 of the carbide tip 50, and the tip portion of the tip blade 47 is Not exposed. Here, wear of the base material of the tip blade 47 due to fluctuations in the unstable layer portion Q of the dead stock 17 is prevented.

1. In this embodiment, the dimension p (Fig. 3) of the surface of the carbide tip 50 along the radial direction of the rotating rotor is determined by the sieving machine 61 (Fig. 4), which is a pre-process of this crushing process. 172 (±30%) of the particle size of the dropped raw material P
It is set to 2 (±30%) times.

According to experiments, the end portion 50 of the carbide tip 50 on the rotor center side. If the above-mentioned dimension β indicating the distance between the outer circumferential side end 50b is, for example, 1/2 or less of the particle size of the raw material P, is the distance of the dimension β short for the raw material P rolling between this? That would be too much. The raw material P separates from the carbide tip 50 and comes into contact with the base material of the tip blade before obtaining sufficient acceleration in the rotor radial direction to reduce the so-called Coriolis force (see Figure 9), and the friction of this base material increases. proceed.

On the other hand, if the dimension l is, for example, twice or more the particle size of the raw material P which is sufficient to accelerate the raw material, the carbide tip will be unnecessarily enlarged and the economical efficiency will be deteriorated.

Therefore, when the above-mentioned dimension p is set to 1/2 to 2 times the particle size of the raw material P, the acceleration distance of the raw material P is sufficient, and the so-called friction t of the raw material P on the carbide tip 50 due to Coriolika is reduced. The raw material will be released from the carbide tip 50 after it has become sufficiently small, and no harmful abrasion to the base material will occur.

Incidentally, if necessary, the carbide tip is arranged so as to protrude from the outer periphery of the rotating rotor or beyond it by extending the tip blade. According to this, there is an advantage that collision of the raw material discharged outward from the tip blade with the side wall adjacent to the tip blade can be prevented, and the rotor side wall can be protected from such wear.

By the way, in this embodiment, the surface of the carbide tip 50 on the side opposite to the rotating rotor center side 51 and in the same circumferential direction on the rotating rotor outer peripheral side 52 is aligned with the same circumferential surface on the rotating rotor center side 51. Since there is less wear compared to
2 is set smaller than the dimension t1.

For example, this dimension t has a thickness of 311 which absorbs the difference in thermal expansion and does not crack during use.
degree) is selected. As a result, the carbide tip 50 is formed into a substantially triangular tapered shape, which makes it possible to significantly reduce the amount of material used for the expensive carbide tip, making it extremely economical.

In addition, as for the material of the carbide tip 50, it is necessary to select a material with as much wear resistance as possible, but on the other hand,
The corners and edges of the cemented carbide tip made of such materials are likely to chip or crack due to collision with the raw material.

As shown in FIG. 11, this occurs between the carbide tip 50 and the raw material P that collided with the tip corner of the carbide tip 50.
This is due to the generation of two local stresses, compressive stress T and tensile stress U.

Generally, in →brittle members such as carbide tips, the strength against tensile stress U is 1/3 of the strength against compressive stress T.
In particular, the more acute the shape of the collision part of the carbide tip, the greater the concentration of stress, and the more easily this collision part is damaged.

In other words, the magnitude of the tensile stress here is shown by the relationship between the dimensions of the raw material and the radius of curvature of the tip corner of the carbide tip,
The larger the size of the raw material or the smaller the radius of curvature of the tip corner of the carbide tip.

Therefore, by chamfering the tip corner of the tip or the joint end with the tip blade in advance, and making the roundness at this chamfer larger than R, for example, the tip corner or edge can be chamfered. It is desirable to prevent chipping and cracking.

In particular, as shown in FIG. 3, this is a portion of the surface of the tip blade 47 facing toward the center side 51 of the rotating rotor and along its circumferential direction, and is the inner side portion E of the tip blade 47 where it joins with the carbide tip 50.
This is based on the fact that when the carbide tip 50 is worn out, if the corner F of the carbide tip 50 is rounded, the carbide tip will not be inadvertently chipped or broken.

In addition, Fig. 12 shows the radius of curvature R of the tip corner of the carbide tip,
The relationship with the tensile stress U generated at the collision part is shown. Here, the raw material P (see FIG. 11) is assumed to be spherical, and its diameter dimensions are set to 20Wl, 40n+, and 8Q+n.

As a result, stress concentration suddenly occurs at the collision part (corner) when the radius of curvature R becomes less than the radius of curvature, which is about 1/20 of the diameter of the raw material.
If a radius of curvature R greater than this is adopted for the above-mentioned collision part, chips and cracks occurring at the tip corner of the carbide tip will be reduced.

Furthermore, in this embodiment, grooves 53 and 53' of appropriate depth are formed on the inner sides E and E' of the tip blade 47 where it joins with the carbide tip 50, along the joining line with the carbide tip 50.
is formed. Cut groove 53.53' in this case
This is to prevent the formation of a sharp notch due to the chamfered portions provided at the corners F and F' of the carbide tip 50, and the shear stress (third This is to prevent the concentration of arrows G and G'' in the figure.

That is, for example, as shown in FIG. 3, when shear stress (arrows G, G'') is about to concentrate at or near the joint between the carbide tip 50 and the tip blade 47, the shear stress A cut groove 53 formed at or near the
．． It concentrates at 53' and is diffused here. This avoids stress concentration on this joint.

Further, as a preferred embodiment, the angle between the surface of the rotor outer peripheral side 52 of the carbide chisop 50 and the same outer peripheral side 52 of the tip blade 47 is set to, for example, 90° or more. ing. This is the same as explained in the above-mentioned cut grooves 53 and 53', and is to avoid concentration of shear stress generated in this joint γ.

FIG. 5 ta+ (Simply shows a modified example of the carbide tip and shows another state of attachment to the tip blade.

FIG.
The tip blade 47 is attached so as to face toward the rotor center side 51 and protrude toward the rotor center side from a surface along the circumferential direction thereof. The height H of this carbide tip 50' protruding from the tip blade 47 is the height H of the carbide tip 50'.
This function is similar to the function performed by the above method (see figure), and is to prevent concentration of shearing force generated at the joining line between the carbide tip 50' and the tip wing 47.

Further, the tip blade 47 in FIG. In addition, similar to the tip blade of the embodiment shown in the third figure, cut grooves 54 and 54' are provided at or near the joint with the carbide tip 50'.

According to this, the shear stress generated at the joint portion of the tip blade 47 with the carbide tip 50' is transmitted to the tip blade 47 of the carbide tip 50'.
Due to the cooperation of the height H protruding from the cut groove 54,
This has the advantage of being more effectively prevented.

In addition, in the tip blade 47 of FIG. 5+a+, a second stage notch groove 54'' is formed as necessary in the notch groove 54 formed on the center side 51 of the rotating rotor, as illustrated by the two-dot chain line. be done.

In addition, FIG. 5 (bl, (C1, d) shows the case where the dimension l of each carbide tip 65 attached to the tip surface of each tip blade 47 does not change, and in addition, the particle size of the raw material is Step portions S+, S2, and S3 of appropriate shapes are provided on the rotor center side 51 of each tip blade 47 so that a sufficient dead spot 17 can be formed even when the blade is relatively small.

Next, in FIG. 5 (el), since it is necessary to increase the size of the carbide tip 66 as the particle size of the raw material increases, a large carbide tip 66 is attached to the large tip blade 47. Indicates the case where

In Fig. 5 tl) and [), one carbide chip 2
The rotor is divided into a center side 51 and an outer peripheral side 52, and a pair of small carbide tips 67, 68 and 67' are provided with a constant gap in the dimension l direction.

68' is attached to the tip wing 47.

According to this, even if the weight of each carbide chip is reduced, the acceleration effect of the raw material is not impaired, and especially if the gap between the chips is 1/2 or less of the raw material particle size, as shown in Figure 5 (fl In this case, there is an advantage that dead stock 17 is formed in this gap.

[Brief explanation of drawings]

FIG. 1 is a schematic vertical sectional view of an impact crushing device according to an embodiment of the present invention, FIG. 2 is a plan view showing the internal structure of the rotating rotor in FIG. FIG. 4 is a flow diagram showing the flow state of the raw material supplied to the impact crusher shown in FIG. 1, and FIG. A side view showing a modified example of the carbide tip and showing another state of attachment to the tip wing;
FIG. 6 is a schematic longitudinal cross-sectional view of an impact crushing device which is the background of this invention, FIG. 7 is an overall perspective view of the rotor in FIG. 6,
Fig. 8 is a plan view showing the internal structure of the rotor shown in Fig. 6, Fig. 9 is a schematic explanatory view showing the aspect of dead stock in the tip blade shown in Fig. 8, and Fig. 10 is a raw material P shown in Fig. 9. Figure 11 is an explanatory diagram showing the relationship between the force generated at the collision part of the carbide tip where the raw material collides with the vector diagram of the power, and Figure 12 is the relationship between the radius of curvature of the tip corner of the carbide tip and the area shown in Figure 11. It is a graph showing the relationship with the tensile stress generated in the collision part. (Explanation of symbols) 30... Impact type crushing device 41... Rotating rotor 45... Partition plate 46... Side wall 47...
・Tip wing 50.50'...Carbide chinf. 53.53'... Cut groove.

Claims (1)

[Claims] 1. The material to be crushed that has been sorted by a sieve is put into a rotor that rotates at high speed, and the material to be crushed is passed outward from the carbide tip bonded to the base material at the outlet of the rotating rotor. In a crushing device that crushes the base material by colliding with a collision surface around the rotating rotor, a groove extending along the joint is provided at or near the joint of the base material with the cemented carbide chip; A crushing device characterized in that the dimension of the carbide tips in the circumferential direction on the rotor center side is set to 1/2 or more of the maximum particle size of the material to be crushed selected by the sieve.