JPS62237956A - 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] 3. The invention relates to a crushing device, and particularly to a crushing device for producing raw materials such as rocks, ores, etc. into sand. The present invention relates to an impact-type crushing device useful for crushing or sizing (cutting corners) particles to a desired particle size.

BACKGROUND OF THE INVENTION Conventional wave ejection This type of impact type crushing apparatus is conventionally 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. H21, 22 and 25 are arranged, which rotate around the rotation center 20, and a tip wing 24 with a carbide tip 24& is integrally attached to the tip of the wing 25, for example, in order to protect the tip from wear. is fixed to.

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 an engine liner 16 (two-dot chain line)) formed as a collision part inside the housing 8 that houses the rotor 1. .

The type that is provided with a dead stock 15 and causes the raw material to collide with this dead stock 15 is for sizing (grain shape correction) of the raw material, and the type that is provided with a ring liner 16 and causes the raw material to collide with this 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 I are slightly curved so as to surround the central distributor 20 (see Fig. 6), which is the center of the rotor II. provided. This means that the input raw materials are in each mold 21.
．． 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 stock 17 accordingly, each mold 21, 22.
5 and the tip blade 24 are approximately 180 along the circumferential direction of the rotor 1.
They are separated by an angle of 1°.

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 801 m, 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 tips can be used on both the rotor center side and the rotor outer circumferential side, and the carbide tips are of an inverted type to extend the wear life. , the above-mentioned prevention of wear of the tip blade base material due to fluctuations in dead stock is not considered.

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, the hatched portion Bl 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 diameter r varies by approximately 1/2 of the particle diameter r (raw material PI P2), and the particle diameter r of this 1/2 particle diameter is determined by the sieve opening size of the sieving process, which is the preceding process of the crushing process. be done.

In such a situation, as shown in FIG. 9, the raw material P indicated by the solid line that rolls on the inclined surface of the dead stock 17 and is discharged in the direction of the arrow shown above moves from the center of the rotor to the dead stock 17. It slides outward (arrow A) on the surface (slanted surface) at a velocity V.

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.
When reaching 4a, a frictional force due to the raw material acts on the side surface of the carbide tip 248 (the tip surface 24 of the tip blade 24) due to Coriolika 2mω.

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 24b as disclosed in the above-mentioned Japanese Patent Application Laid-Open No. 51-95954, a carbide tip 24. A large friction as shown in the hatched area B2 in FIG. 9 is formed on this tip surface 24I by the raw materials P and P that have passed through.

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 hatched 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, the length of the raw material sliding surface in the radial direction of the rotor of the carbide tip is made small enough to eliminate the influence of Coriolica, 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 tip knobs increases, which is uneconomical.

OBJECTS OF THE INVENTION Therefore, the main object of the present invention is to provide a crushing device that prevents friction occurring on the tip surface of the tip blade base material along the rotor radial direction.

Structure of the Invention In order to achieve the above-mentioned object, the main means adopted by the present invention is to introduce the material to be crushed, which has been sorted by a sieving machine, into a rotor that rotates at high speed, and to place the material to be crushed near the outlet of the rotating rotor. In a crushing device that, while accumulating the materials, ejects the materials to be crushed outward from the outlet of the rotating rotor by centrifugal force, and crushes the materials by colliding with a collision surface around the rotating rotor,
The dimension in the rotor radial direction of the carbide tip provided at the outlet end of the rotating rotor is set to 172 to 2 times the maximum particle diameter dimension of the crushed material passing through the sieving machine. be.

The carbide tip attached to the outlet end of the working rotating rotor is
The radial dimension of the rotor is set to approximately 1/2 to 2 times the particle diameter of the raw material passing through the sieve opening in the previous step.

Therefore, when the raw material passes through the tip surface of the tip blade base material along the rotor radial direction, the Coriolis force is received by the carbide tip.

Since a distance (172 to 2 times the maximum particle size of the raw material) is secured to obtain sufficient acceleration to almost eliminate the Coriolis force, the maximum effect can be achieved with the smallest economical carbide tip. Obtainable.

Effects of the Invention According to the present invention, since the carbide tip is provided on the tip surface of the tip blade base material along the rotor radial direction, wear occurring there can be prevented.

In addition, since the length of the raw material sliding surface in the radial direction of the rotor is appropriately 1/2 to 2 times the maximum particle diameter of the material to be crushed, when the raw material is discharged to the outside of the rotor, the size of the carbide chips is This provides sufficient acceleration, during which the Coriolis force disappears, which prevents wear of the tip blade and is also economical.

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. A side view showing how the illustrated carbide tip is attached to the tip blade, FIG. 4 is a flow diagram showing the flow state of the raw material supplied to the impact crushing device shown in FIG. 1, and FIGS. 5 f, t) to (Kago shows a modified example of the carbide tip shown in the second figure, and a side view showing another state of attachment to the tip wing;
Fig. 11 is an explanatory diagram showing the relationship between the force generated at the collision part of the carbide tip that has collided with the raw material, and Fig. 12 is an explanatory diagram showing the relationship between the curvature radius of the tip corner of the carbide tip and the tensile stress generated at the collision part shown in Fig. 11. It is a graph showing the relationship between

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 device 30 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 the 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 39b.

On the other hand, a hollow cylindrical rotating rotor 42 is attached to the upper end 39a of the rotor shaft 39 located approximately in the center of the crushing chamber 31, and rotates horizontally around the rotor shaft 39. .

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 this bracket 44 so that the collision surface with the raw material does not go around 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 41, the raw material that has been introduced into the center of the rotating rotor 41 is transferred to the rotating rotor 4, as can be seen from the explanation in FIG.
1 are deposited as dead stock 17 at appropriate angles in the circumferential direction. Then, the deposited raw materials are transferred to each dead stock 1 according to the high speed rotation of the rotating rotor 41.
7, and is discharged outward from a raw material discharge port 43 formed in the circumferential wall of the rotor 41.

Inside the rotating rotor 41, partition plates 451 are provided which are oriented in the radial direction of the rotating rotor 41 at an angle of about 120° in the circumferential direction of the rotating rotor 41 in order to form such de-nod stocks 17. Three side walls 46 and three tip blades 47 are arranged along the circumference of the rotating rotor 41 in an arc shape.

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 knob 50 is fixed.

As shown in FIG. 3, this carbide tip 50 has a surface corresponding to the rotor center side 51 of the carbide tip 50, and the dimension of this surface in the rotor circumferential direction is 1. is set to 1/2 or more of the opening size of the sieve during the sieving process which is a pre-process of this crushing process.

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 crushing number 60 (jijikurasocha) which constitutes, for example, a second crushing step. Here, the large-sized raw material is crushed to the required particle size in a secondary crushing process installed downstream in the flow direction of the raw material (arrow in the figure). In this case, as an example of the crusher that constitutes 2 in the secondary crushing process, for example, the embodiment apparatus shown in the first figure, that is, the impact type crusher 30
will be prepared.

Next, a sieving step MI is provided between the first crushing step 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 61, which is used to sieve raw materials that meet the above particle size to the secondary crushing process 2. A screen with a sieve opening size that corresponds to the size of the sieve 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, an unstable layer portion Q (area between the two-dot chain line and the broken line in FIG. 3) of the dead stock 17 (see FIG. 2) formed on the tip wing 47 teeth,
Approximately 1/2 of the particle size of the raw materials p, /, p2/, etc. that pass through the sieve opening size during the sieving process described above.
It varies with the width r' (corresponding to the particle diameter radius).

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,
The tip portion of the tip wing 47 is not exposed. Here, the tip i[47
Abrasion of the base material is prevented.

Further, 1. As a characteristic component of this embodiment, the dimension of the surface of the carbide tip 50 along the radial direction of the rotating rotor is 7!
(Fig. 3) is 1/2 (±30%) to 2 (±30%) of the particle size of the raw material P sieved by the sieve 61 (Fig. 4), which is a pre-process of this crushing process. It is set to double.

According to experiments, the above-mentioned dimension e indicating the distance between the rotating rotor center side end 503 and the outer peripheral side end 50I of the carbide tip 50 is, for example, 1/2 or less of the particle size of the raw material P. In this case, the distance of dimension l is too short for the raw material P rolling between them. 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.

So, the above dimensions! When is set to 1/2 to 2 times the particle size of the raw material P, the acceleration distance of the raw material P becomes sufficient and the so-called frictional force of Coriolika against the carbide tip 50 of the raw material P becomes sufficiently small. is released from the carbide tip 50, and no harmful abrasion to the base material occurs.

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, a surface of the carbide tip 50 opposite to the rotating rotor center side 51 and in the same circumferential direction on the rotating rotor outer peripheral side 52 is located at the rotating rotor center (IIJ 51
Since the wear is less than that of the surface in the same circumferential direction, the dimension t2 is the dimension 1. is set smaller.

For example, for this dimension t2, a thickness of about 31 mm is selected so that the brazing can absorb the difference in thermal expansion and will not break during use. As a result, the carbide tip 50 is formed into a substantially triangular tapered shape, and the material used for the expensive carbide tip can be significantly reduced, 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 a brittle member such as a carbide tip, 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, for example, IR, it is possible to prevent defects at the tip corner or edge. It is desirable to prevent cracking.

In particular, as shown in FIG. 3, this is the part of the surface of the tip N47 facing toward the rotor center side 51 and along its circumferential direction, and is the inner side E where the tip blade 47 joins 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 is 2On+, 40B, and 80fl.

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 intended to prevent concentration of arrows G and G' in the figure.

That is, for example, as shown in FIG. 3, if 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 will be concentrated at this joint. 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 tip 50 and the same outer peripheral side 52 of the tip blade 47 is set to, for example, 90° or more. . This is to avoid the concentration of shear stress generated at this joint γ, which is the same as explained in connection with the above-mentioned cut grooves 53 and 53'.

Figs. 5 fa) to (gl) show modified examples of the carbide tip and other attachment states to the tip blade.

In the tip blade 47 shown in FIG. 5 (al), the carbide tip 50'
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 method (see figure), and is to prevent concentration of shearing force generated at the joining line of the carbide tip 50' with the tip wing 47.

Furthermore, a carbide tip 50' is provided on the tip blade 47 of FIG. In addition, similar to the tip blade of the embodiment shown in the third figure, cut grooves 54, . 54' is provided.

According to this, the shear stress generated at the joint portion of the tip blade 47 with the carbide tip 50' is
There is an advantage that the height I (which protrudes from the wall) and the notch a54 cooperate with each other to more effectively prevent this.

In addition, at the tip N47 of FIG. be done.

In addition, Fig. 5 (bl, (cl, (di) shows the case where the dimension p 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 compared. In order to form a sufficient dead stock 17 even when the target is small, each tip blade 470 has an appropriately shaped stepped portion S, , S2.S on the rotor center side 5].

is provided.

Next, FIG. 5 (tel) shows a case where a large-sized carbide tip 166 is attached to a large-sized tip N41, since it is necessary to increase the size of the carbide tip 66 as the particle size of the raw material increases.

In FIG. 5 (fl and ()), one carbide tip is divided into a rotating rotor center side 51 and an outer peripheral side 52,
A pair of small carbide tips 67, 68 and 67' 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 will not be impaired, and especially if the gap between the chips is less than 1/2 of the raw material particle size, as shown in Fig. 5ffl. In terms of degree, there is an advantage that dead stock 17 is formed in this gap portion.

[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 side view showing how the chips are attached to the tip blade; FIG. 4 is a flow diagram showing the flow of raw materials supplied to the impact crusher shown in FIG. 6 is a side view showing a modified example of the carbide tip and shows another state of attachment to the tip blade, FIG. 6 is a schematic vertical sectional view of an impact crushing device that is the background of this invention, and FIG. FIG. 8 is a plan view showing the internal structure of the rotor shown in FIG.
The figure is a schematic explanatory diagram showing the aspect of dead stock in the tip blade shown in Fig. 8, Fig. 10 is a vector diagram of <@+) 3 on the raw material P shown in Fig. 9, and Fig. 11 is a diagram of the Fig. 12 is a graph showing the relationship between the radius of curvature of the tip corner of a carbide tip and the tensile stress generated at the collision part shown in Fig. 11. be. (Explanation of symbols) 30... Impact type crushing device 41... Rotating rotor 45... Partition plate 46... Side wall 47...
・Tip (Ili! Wing 50.50'...Carbide tip/knob.

Claims (1)

[Claims] 1. The materials to be crushed that have been sorted by the sieve are put into a rotor that rotates at high speed, and while the materials to be crushed are deposited near the outlet of the rotating rotor, the materials to be crushed are subjected to centrifugal force. In a crushing device that ejects outward from an outlet of the rotating rotor and causes it to collide with a collision surface around the rotating rotor to crush it, the size of the carbide tip provided at the outlet end of the rotating rotor in the rotor radial direction is A crushing device characterized in that the particle size is set to 1/2 to 2 times the maximum particle size of the crushed material passing through the sieve. 2. The crushing device according to claim 1, wherein the carbide tip is located at or outside the outer periphery of the rotating rotor. 3. The crushing device according to claim 1 or 2, wherein the carbide tip is divided into a center side and an outer peripheral side of the rotating rotor and joined together.