JP2003334459A - Mechanical crusher - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a mechanical crusher which can efficiently produce a crushed product having a small particle size, being free from the contamination of coarse particles, and showing a sharp particle size distribution width, and is suitable for pulverizing a resin or a powder mainly comprising the resin. <P>SOLUTION: The grooves of at least one of a rotor supported by a rotating shaft and having a plurality of grooves formed in its outer peripheral surface, and a liner arranged with a desired gap between it and the outer peripheral surface of the rotor and having a plurality of grooves formed in its inner peripheral surface are inclined to the direction parallel to the rotating shaft so as to disturb the flow of a material to be crushed. The groove interval of at least one of the rotor and the liner is set to a value calculated from formula p=kD+1 (mm) based on the particle size of the material to be crushed, wherein p is the groove interval of the rotor or the liner; k is a coefficient of 2-3; and D is a maximum diameter of the material to be crushed (mm). <P>COPYRIGHT: (C)2004,JPO

Description

Detailed Description of the Invention

[0001]

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a mechanical crushing apparatus suitable for producing a resin or a powder containing a resin as a main component, particularly for a dry pulverizing process in producing a dry toner or a powder coating material.

[0002]

2. Description of the Related Art In the production of dry toner, powder coating, etc., a dry mechanical pulverization process is carried out to adjust the particle size of the final product and the particle size distribution. Have been proposed.

Conventionally, as a rotary type mechanical crushing device for finely crushing such an object to be crushed, Japanese Patent Laid-Open No. 59-105.
The fine pulverizers described in Japanese Patent No. 853 and Japanese Patent Publication No. 3-15489 are known. As shown in FIG. 16, this fine crusher 50 has a large number of uneven parts 5 parallel to the generatrix on the outer peripheral surface.
A cylindrical rotor (rotor) 54 in which 4 is continuous in the circumferential direction.
Is supported by a rotating shaft 56, and a cylindrical stator having a large number of concavo-convex portions 60 parallel to the generatrix on the inner peripheral surface in the circumferential direction with a minute gap 58 between the outer peripheral surface of the rotor 54 ( Liner)
62 is fitted on the outside of the rotor 54, and the gap 58 is used as a crushing chamber.

In the fine crusher 50, the rotor 54 is rotated at a high speed, and the casing 51 is sucked by a suction blower (not shown) or the like from a product discharge port 64 provided on the upper right side surface in the figure. As a result, the material to be ground supplied from the supply port 66 for the material to be ground provided in the lower left portion of the casing 51 in the figure is sent together with the air flow into the grinding chamber composed of the minute gaps 58, and at this time, the rotor 54 and the stator. A vortex flow generated by the unevenness of 62 effectively collides with this uneven surface, or grinds between both convex portions of the rotor 54 and the stator 62 to perform a pulverizing process to obtain fine particles, and then a fine gap. The fine particles flowing out from the product are discharged from the product discharge port to the outside of the machine. In such a fine pulverizer 50, in order to prevent the coarse particles from flowing out from the gap 58 and to flow only the fine particles, the classification ring that closes the concave portion of the concave and convex portion 60 at the upper end portion of the stator 62. 68 is provided.

In the fine crusher 50, the gap between the crushing chambers 58 is set to 1 mm or less, and the rotor 54 is rotated at a high speed.
The crushed objects collide with each other by the vortex flow that is constantly generated in these concave portions from both the uneven surfaces of 4 and receive the shearing force,
It is said that fine pulverization is effectively carried out and a pulverized product having a relatively narrow particle size distribution range of the order of microns to the order of ten and several microns can be obtained.

In such a fine crusher 50, the rotor 54
17A, 17B, 17C, and 17D are proposed as a combination of the uneven portion 52 and the uneven portion 60 of the stator 62. In these drawings, the uneven portion 52a and the uneven portion 60a have a rectangular cross-sectional shape, and the uneven portion 52b and the uneven portion 60b have a triangular cross-sectional shape. The triangular uneven portion 52b and the uneven portion 6 shown in (d)
It is known that excellent crushing performance can be obtained by the combination of 0b.

Further, in Japanese Unexamined Patent Publication No. 7-155628, as shown in FIGS. 18 (a) and 18 (b), the outer peripheral surface of the rotor 54 and the stator (cylindrical body) such as the above-mentioned fine pulverizer 50 are disclosed. ) In addition to a large number of uneven portions parallel to the generatrix of the inner peripheral surface of 62, a large number of them in the direction orthogonal to the generatrix on the outer peripheral surface of the rotor 54 and on the outer peripheral surface of the rotor 54 and the inner peripheral surface of the stator 62. There is proposed a mechanical crushing device 70 and 71 in which the uneven portion 72 and the uneven portions 72 and 74 are continuously formed in the direction of the generatrix. These mechanical grinding devices 70 and 71
, By forming the uneven portion in both the direction parallel to the generatrix and the direction orthogonal to this, it is possible to generate a vertical vortex in addition to the horizontal direction, thereby improving the crushing function, It is said that a pulverized product having a particle size of several tens of microns can be obtained.

In addition to this, as a rotary mechanical crushing device, for example, Japanese Patent Publication No. 4-12190 and 4
Various minerals and ceramics described in -12191
Crushing device for crushing hard material such as soybean, stone and gravel, JP-B-58-14822 and 58-14822
Fine pulverizer for obtaining fine particles of carbon or pigment for copying described in JP-B No. 61-36457 and 61-
An ultrafine pulverizer described in Japanese Patent No. 36459 to obtain ultrafine particles on the order of several microns and a pulverizer described in Japanese Patent Application Laid-Open No. 5-184960 are known.

[0009]

By the way, a resin or a powder containing a resin as a main component, more specifically, a dry toner, a powder coating material, or the like, has a smaller particle size in order to achieve high quality. A powder having uniform particle size, that is, having a sharp particle size distribution is required.

However, in the above-mentioned conventional mechanical crushing device, in order to obtain a crushed product having a small particle size, the rotational speed of the rotor must be increased, resulting in energy efficiency, bearing life, and
It causes problems such as noise, vibration, and rise in air exhaust temperature. In addition, there is a limit to increase the rotation speed of the rotor, and there is a problem that it cannot be crushed to a target particle size.

Further, for example, in the case of dry toner, particles which are excessively finer than the target particle diameter are removed by a classifying means to improve the product quality, and the particle size distribution is adjusted, but when the rotation speed of the rotor is high, Since many particles are excessively pulverized to exceed the target particle diameter, there are many unnecessary particles and the yield is poor, which is a problem.

Further, the fine crusher 50 described in JP-A-59-105853 and JP-B-3-15489.
In order to prevent passage of coarse particles, a mechanism for narrowing the grinding chamber between the rotor 54 and the stator 62 is adopted.
For example, the gap 58 serving as the crushing chamber is set to 1 mm or less.

However, in addition to the problem that the processing capacity decreases and the processing amount decreases when the crushing chamber is narrowed in this way, depending on the supply amount of the raw materials, particularly when the supply amount exceeds the processing capacity, it is There is a risk that the temperature of the crushing chamber will rise excessively due to frictional heat or the like.
In such a case, there is a problem that the raw material powder is fused in the crushing chamber, and it becomes difficult or impossible to continue the crushing process any further.

Further, in the mechanical crushing device disclosed in Japanese Patent Application Laid-Open No. 7-155628, in addition to the concavo-convex portion parallel to the generatrix on the outer peripheral surface of the rotor 54 and the inner peripheral surface of the stator 62, concavo-convex orthogonal to the generatrix. Due to the formation of the portions 72 and 74, vortices are generated not only in the horizontal direction but also in the vertical direction by these convex portions, so that excessive vortices are generated and particles collide excessively. In particular, there is a problem in that the particles collide excessively with the concave portions of the rotor 54, excessive pulverization occurs, and the air exhaust temperature rises excessively.

The object of the present invention is to solve the above-mentioned problems of the prior art, to have a small particle size, and to prevent the inclusion of coarse particles,
Another object of the present invention is to provide a mechanical crushing device suitable for finely crushing a resin or a powder containing a resin as a main component, which is capable of producing a crushed product having a sharp particle size distribution width with high efficiency.

[0016]

In order to solve the above-mentioned problems, the present invention provides a rotor supported on a rotating shaft and having a plurality of grooves formed on its outer peripheral surface, and an outer periphery of the rotor on the outer side of the rotor. A mechanical crushing device for crushing an object to be crushed in the gap, the liner having a surface and a liner having a plurality of grooves formed on an inner circumferential surface thereof, the rotor and the liner having a desired gap. At least one of the grooves of the liner is inclined in a direction that impedes the flow of the material to be crushed with respect to a direction parallel to the rotation axis, and at least one of the groove interval of the rotor and the groove interval of the liner, The present invention provides a mechanical crushing device having a predetermined interval calculated by the following formula based on the particle diameter of the crushed object. p = kD + 1 (mm) where p: groove spacing of the rotor and groove spacing of the liner (mm) k: coefficient (2 to 3) D: maximum diameter of object to be ground (mm)

Further, according to the present invention, a rotor supported by a rotary shaft and having a plurality of grooves formed on an outer peripheral surface thereof is arranged outside the rotor with a desired gap from the outer peripheral surface of the rotor. A liner having a plurality of grooves formed on an inner peripheral surface thereof, the mechanical crushing device crushing an object to be crushed in the gap, wherein the groove of at least one of the rotor and the liner is the rotary shaft. Parallel to the direction parallel to the direction in which the object to be crushed is prevented from flowing, and at least one of the intervals between the grooves of the rotor and the grooves of the liner is from the supply port side of the crushed product to the discharge port. Provided is a mechanical crushing device characterized in that the size is gradually reduced toward the side.

Here, with respect to the distance between the grooves of the rotor,
Preferably, the liner groove spacing ratio is 1-2. In addition, it is preferable that the gap between the grooves of the liner is 4 mm to 8 mm.

Further, on the inner peripheral surface of the liner, a groove inclined in a direction that impedes the flow of the object to be ground with respect to the direction parallel to the rotation axis, and the object to be ground with respect to the direction parallel to the rotation axis. It is preferable that both a groove that is inclined in the opposite direction and a direction that obstructs the flow are formed, and the outer peripheral surface of the rotor is
Both the groove inclined to the direction parallel to the rotation axis in the direction of impeding the flow of the object to be ground, and the groove inclined in the direction opposite to the direction parallel to the axis of the flow of the object to be ground and the opposite direction It is preferably formed.

[0020]

BEST MODE FOR CARRYING OUT THE INVENTION The mechanical crushing apparatus according to the present invention will be described below in detail with reference to the preferred embodiments shown in the accompanying drawings, but the present invention is not limited thereto. FIG. 1 is a schematic sectional view of an embodiment of the mechanical crushing device of the present invention. In these drawings, hatching is partially omitted for simplification.

As shown in the figure, the mechanical crushing device (hereinafter referred to as crushing device) 10 is a horizontal crushing device,
A casing 11, a rotating shaft 12 rotatably supported by the casing 11, a rotor 16 composed of a plurality of rotor units 14 supported and fixed to the rotating shaft 12, four rotor units 14 in the illustrated example, and a rotor supported by the casing 11. An outer peripheral surface of the rotor 16 and a liner 18 that is fitted and inserted so as to have a desired constant gap are provided on the outer side of the rotor 16. Casing 1
1, a raw material supply port 20 for supplying a crushing raw material (object to be crushed) is provided on the left side of the drawing, and a product discharge port 22 for discharging a crushed crushed product is provided on the right side of the drawing.

In the mechanical grinding device 10, the rotary shaft 12
Is parallel to the mounting surface of the mechanical grinding device 10,
That is, it is arranged horizontally and is supported on the left and right wall surfaces of the casing 11 in the figure via bearings 24a and 24b.
Then, one end portion of the rotating shaft 12, that is, the right end portion (bearing 2
4b side) is connected to a driving device such as a motor through a winding transmission mechanism such as a pulley and a transmission belt, a gear transmission mechanism, and the like, which are not shown.

The four rotor units 14 are fixed to the rotary shaft 12 by a key (not shown), and circular side plates 26a and 26 which sandwich the four rotor units 14 from both sides.
The rotor 16 is integrated by b. In the illustrated example, the rotor 16 is composed of four rotor units 14 divided in the lengthwise direction, but this is for the convenience of manufacturing, and the present invention is not limited to this, and is constituted. It goes without saying that the number of the rotor units 14 is not limited, and it is also possible to configure the entire rotor unit 14 as one rotor.

A liner 18 is fitted on the outer side of the rotor 16 with a certain gap from the outer peripheral surface of the rotor 16. The liner 18 is fitted between the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18. The formed gap 28 serves as a raw material crushing chamber. The liner 18 is fitted and fixed in the cylindrical body portion at the center of the casing 11.

Both sides of the casing 11 have liner 1
8 (and the rotor 16), the volume and shape are set so as to form a space of appropriate size on both outer sides,
The space on the left side of the drawing communicates with the raw material supply port 20, and the space on the right side of the drawing communicates with the product (crushed product) discharge port 22. And
The product discharge port 22 is sucked by an air suction device such as a blower (not shown). The product to be ground supplied from the raw material supply port 20 is sucked together with air, and the product obtained by crushing in the device is manufactured together with air. It is discharged from the discharge port 22.
Further, the lower surface of the casing 11 has legs and is attached to an installation stand (not shown).

The basic structure of the mechanical crushing device 10 of the present invention is as described above, but the present invention is not limited to the horizontal crushing device shown in FIG. 1. For example, as shown in FIG. And a rotor 16 supported by the liner 18 and a liner 18 fitted into the rotor 16 with a predetermined gap,
At the lower part of the casing below the liner 18, a raw material supply port 20,
Any crushing device having the same basic constituent elements, such as a vertical crushing device 30 having a structure in which the product discharge port 22 is provided on the upper casing of the liner 18, may be used. Alternatively, it can be appropriately modified based on the structure of known technology.

Next, the structure of the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18, which is one of the characteristic parts of the crushing device of the present invention, will be described in detail.

In the crushing apparatus 10 of the present invention, a plurality of grooves are formed on one or both of the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18, and these grooves are parallel to the rotary shaft 12. It is inclined in such a direction as to impede the flow of the material to be ground. For example, as shown in the example of the liner 18 in FIG.
With respect to the direction parallel to the rotation center (center line) 12a of 2,
A groove 32 is formed which is inclined in the direction opposite to the rotation direction of the rotor 16 (indicated by an arrow b in the drawing) whose only envelope is indicated by a dotted line.

Here, in FIG. 3, in the liner 18, only a liner unit constituting one sixth of the liner 18 is shown, and the other parts are shown by the envelope with dotted lines. Of course, in the present invention, the number of liner units forming the liner 18 is not limited, and it goes without saying that the liner 18 can be formed of one circular tubular body. In the present invention, the direction parallel to the rotary shaft 12 means the direction parallel to the rotation center 12a of the rotary shaft 12 and the direction of the air flow indicated by the arrow a in the figure, and thus the rotor 16 or Equal to the longitudinal direction of the liner 18 and its generatrix direction.

As described above, in the present invention, the rotor 16
At least one of the groove 34 on the outer peripheral surface and the groove 32 on the inner peripheral surface of the liner 18 is inclined with respect to the direction parallel to the rotation axis 12 in a direction that impedes the flow of the object to be ground (particles). As developed and schematically shown in FIG. 4, the moving velocity vector (the velocity vector of the flow of particles) of the crushed object moving in the gap 28 between the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18 is , And a velocity vector of rotation of the rotor 16 (direction: rotation direction b, length: velocity) and a velocity vector of air flow (direction: flow direction a, length: velocity).

Therefore, the groove 32 on the inner peripheral surface of the liner 18 is provided in a direction intersecting with the direction of the velocity vector of the obtained particle flow (indicated by an arrow c in the figure), preferably in a direction orthogonal thereto. That is, in FIG. 4, the groove 32 is provided so as to be inclined with respect to the air flow direction a. here,
The inclination angle θ of the groove 32 with respect to the air flow direction a is not particularly limited as long as the groove 32 is inclined at an acute angle in the direction that hinders the particle flow, but is preferably 5 degrees or more and less than 90 degrees, more preferably 5 degrees. Degrees to 60 degrees, more preferably 5 degrees to 45 degrees
The degree is most preferably 10 to 30 degrees.

As described above, the shape of the groove (hereinafter, referred to as an inclined groove) 32 inclined to the air flow direction a (see FIG. 4) on the inner peripheral surface of the liner 18 and dimensions including width, depth, pitch, etc. are particularly The shape of the inclined groove 32 in the cross section orthogonal to the direction of the groove 32 of the liner 18 may be, for example, a sawtooth shape, a trapezoidal shape, a rectangular shape, an arc shape, or the like. As shown in FIG. 5 (a), one side faces the center of the rotor 16 and the other side forms an angle of 45 to 60 degrees with this side, and the rotation direction b of the rotor 16 is lower in the rearward direction.
-15489).

For example, FIGS. 5B and 5C show typical examples of the cross-sectional shape of the inclined groove 32 of the liner 18 in the cross section orthogonal to the direction of the inclined groove 32 of the liner 18. Figure 5
As shown in (b) and (c), groove 32 of liner 18
In the cross-sectional shape, the front surface 32a with respect to the rotation direction b of the rotor 16 is inclined by a predetermined angle α in the rotation direction b of the rotor 16 with respect to the center direction of the rotor 16, that is, the direction indicated by the one-dot chain line R in the figure, The rear surface 32b with respect to the rotation direction b is inclined with respect to the center direction R in the rotation direction b or the opposite direction by a predetermined angle β.

Here, the sectional inclination angles α and β of the groove 32 are
Are preferably in the ranges of 30 degrees to 70 degrees and -30 degrees to 30 degrees (from 30 degrees in the direction opposite to the rotation direction b to 30 degrees in the rotation direction b) with respect to the rotation direction b. In addition, in FIGS. 5B and 5C, the liner 1
The bottom 32c of the groove 32 of No. 8 and the projection 32d of the liner 18 between the adjacent grooves 32 are both 1 of the pitch p of the grooves 32.
It is preferably / 2 or less. In addition, the groove 3 of the liner 18
The bottom 32c of 2 does not form a straight line portion as shown in FIGS. 5 (b) and 5 (c) but forms a triangular vertex or is rounded, and for example, has an arc shape as shown in FIG. 5 (a). More preferred is eggplant.

As described above, by forming such an inclined groove 32 on the inner peripheral surface of the liner 18, the liner 18 is crushed in the gap 28 between the rotor 16 and the liner 18 constituting the crushing chamber, and the liner 18 is crushed. The particles to be crushed that have entered the inclined groove 32 of 18 are less likely to move in the direction of the flow of the air sucked by the blower or the like from the product discharge port 22, and enter the crushing chamber while keeping the space of the crushing chamber wide. The residence time can be extended.

In the present invention, the inclined groove is not limited to the inclined groove 32 formed on the inner peripheral surface of the liner 18, and the rotor 1
It may be formed on either one of the outer peripheral surface of 6 and the inner peripheral surface of the liner 18, but may be formed on both peripheral surfaces. As shown in FIG. 6, when the inclined groove 34 is formed on the outer peripheral surface of the rotor 16, the position of the inclined groove 34 on the joining surface of the adjacent rotor units 14 of the four rotor units 14 forming the rotor 16 is set. Key grooves (not shown) of the four rotor units 14 for fixing to the rotating shaft 12 so that the inclined grooves 32 are smoothly continuous without any deviation.
Is preferably aligned accurately.

The inclination angle of the inclined groove 34 of the rotor 16 is not particularly limited as in the inclined groove 32 of the liner 18, and the preferable conditions are also the same. In addition,
Regarding the shape and size of the inclined groove 34 of the rotor 16,
Similar to the inclined groove 32 of the liner 18, there is no particular limitation and it may have any shape, but in particular, as shown in FIG. 5A, the inclined groove in a cross section orthogonal to the groove direction of the rotor 16 The shape of 34 is 5 to 25 degrees on one side on the rear side in the rotation direction b of the rotor 16 with respect to the radius toward the center of the rotor 16.
It is preferable that the other side has a triangular shape with an angle of 45 to 60 degrees.

For example, FIGS. 5D and 5E show typical examples of the sectional shape of the inclined groove 34 of the rotor 16 in a cross section orthogonal to the direction of the inclined groove 34 of the rotor 16. Figure 5
As shown in (d) and (e), the groove 34 of the rotor 16 is
In the sectional shape of FIG. 3, the front surface 34a with respect to the rotation direction b is inclined by a predetermined angle γ with respect to the radial direction of the rotor 16, that is, the direction indicated by the one-dot chain line R in the figure, or the rotation direction b of the rotor 16 or the opposite direction. The surface 34b on the rear side with respect to the rotation direction b is inclined with respect to the radial direction R by a predetermined angle δ in the rotation direction b.

Here, the sectional inclination angles γ and δ of the inclined groove 34 are respectively −30 degrees to 30 with respect to the rotation direction b.
That is, in the range of 30 degrees in the direction opposite to the rotation direction b to 30 degrees in the rotation direction b and in the range of -70 degrees to -30 degrees, that is, in the range of 30 degrees to 70 degrees in the direction opposite to the rotation direction. Is preferred. Further, in FIGS. 5D and 5E, the bottom portion 34 c of the groove 34 of the rotor 16 and the convex portion 34 d of the rotor 16 between the adjacent grooves 34 are both 1/2 or less of the pitch p of the grooves 34. Is preferred. It should be noted that the bottom portion 34c of the groove 34 of the rotor 16 does not form a straight line portion as shown in FIGS. 5 (d) and 5 (e), but forms a triangular vertex or is rounded, for example, as shown in FIG. It is more preferable to form an arc shape as shown.

The reason for limiting the cross-sectional shapes of the grooves 32 and 34 will be described below as a preferred embodiment of the present invention.

In the crushing apparatus of the present invention, in order to prevent an excessive rise in exhaust gas temperature, that is, an increase in pulverization temperature and an increase in pulverization power, the flow of the rotor is not disturbed excessively and the flow of FIG.
As shown in the schematic diagram of (a), it is necessary to form vortices of appropriate strength in the grooves 32 and 34 of the liner 18 and the rotor 16 in order to improve the grinding performance. Here, the reference numeral 32 s indicates the image of the streamline in the groove 32 of the liner 18 generated by the rotation of the rotor 16, and the reference numeral 3 s.
4s shows an image of streamlines in the groove 34 of the rotor 16.

The particles to be crushed put into the crushing chamber 28 are
Due to the vortex generated in the groove 34 of the rotor 16, the groove 3 of the rotor 16
4 and hit the surface 34b, the liner 18
Is blasted in the direction of, and collides with the surface 32a of the liner 18 to be crushed (see FIG. 5 (f)). Coarse particles of the crushed particles are discharged to the crushing chamber 28 again without riding on the flow of the vortex in the groove 32 of the liner 18 and undergo the same action. On the other hand, finer particles may be generated in the grooves 32 of the liner 18 or the rotor 16
Staying in the grooves 32 and 34 in the flow of the grooves 34 of the rotor 16 and the grooves 32 and 34 of the rotor 16 and the liner 18.
It is crushed to a certain fineness by the fluctuation of pressure caused by the alternating peaks and valleys at high speed. Considering the above pulverization process, the preferable groove cross-sectional shape is determined as follows.

The rear side surface 34b of the groove 34 of the rotor 16 is inclined so as not to disturb the flow excessively, prevent the temperature of the exhaust gas from rising, and repel crushed material particles colliding with the surface toward the liner 18. The angle δ is preferably 30 degrees or more and 70 degrees or less in the direction opposite to the rotation direction b of the rotor 16.

The front side surface 32a of the groove 32 of the liner 18 has an inclination angle α of 30 degrees or more in the rotational direction, so that an appropriate impact is given when the crushed object particles repelled by the rotor 16 collide. A degree of less than is preferable.

It is important that the vortices in the grooves 34 of the rotor 16 and the grooves 32 of the liner 18 have appropriate vorticity magnitudes, a large space, and stability. The inclination angle γ of 34a and the inclination angle β of the rear side surface 32b of the groove 32 of the liner 18 are 0 degrees or more and 0, respectively.
The space of the grooves 32 and 34 can be widened by setting it to be equal to or less than 10.

However, the front side surface 34 of the groove 34 of the rotor 16 is
In the case of “a”, when the inclination angle γ is set to be large contrary to the rotation direction “b”, vortices other than the main vortex are generated, and large particles to be discharged from the groove 34 also remain in the groove 34 and become coarse in the product. Particles are mixed in.

Here, the main vortex is a vortex that mainly gives the action of crushing to the particles, and is denoted by reference numerals 32s and 34 in FIG. 5 (a).
This is indicated by s (see FIG. 5 (g)).

When the inclination angle γ is increased in the rotation direction b, the vortex generated in the groove 34 is discharged into the main flow and becomes unstable, or the main flow enters the groove 34 and the size of the vortex is increased. It gets smaller. In consideration of these, the inclination angle γ is −30 degrees or more and 30 degrees or less in the rotation direction b, that is, 30 degrees in the direction opposite to the rotation direction b to 30 in the rotation direction b.
It is preferably within the range up to degrees.

For the same reason, the inclination angle β of the rear side surface 32b of the groove 32 of the liner 18 is not less than −30 degrees and not more than 30 degrees in the rotation direction b, that is, in the direction opposite to the rotation direction b from 30 degrees to the rotation direction b. It is preferably within the range of up to 30 degrees.

Next, the preferable pitch of the grooves in the present invention will be described.

With the same diameter of the rotor 16, if the groove pitch p is reduced, the number of grooves (32, 34) increases and the groove (3
2, 34) wall surfaces (32a, 32b, 34a, 34b)
This is preferable for obtaining a finer grain size because the probability of collision with is high. However, since the depth of the grooves (32, 34) has a suitable range for generating a vortex with stable and appropriate strength and suppressing the generation of vortices other than the main vortex, reducing the groove pitch p There is a problem that the space of the groove becomes narrow and the processing capacity is lowered.

The groove pitch p depends on the type of material to be crushed, the particle size of the raw material, the desired product particle size, etc., but in the case of the crushing apparatus 10 of the present invention, it is preferably about 2 mm to 10 mm. For example, the relationship between the groove pitch p and the raw material particle size will be described as an example. It is preferable that the groove pitch p be an interval defined by the following (Formula 1) based on the maximum raw material diameter. . p = kD + 1 (mm) (Equation 1) where p: gap between groove of rotor 16 and groove of liner 18 (mm) k: coefficient (2 to 3) D: maximum diameter of raw material (mm) groove of rotor 16 By setting the pitch of at least one of the grooves of the liner 18, and preferably both of the grooves, to satisfy the above (formula 1), the grinding efficiency of the grinding raw material can be improved.

The depth of the grooves (32, 34) is preferably not less than 1/5 times and not more than 3 times the pitch. The groove pitch p and the groove depth are determined by the groove 34 of the rotor 16 and the liner 18.
It is preferable that the groove 32 is the same as the groove 32, but both grooves 32
And 34 may be different.

By the way, the housing 11 of the crushing device 10
While passing through the gap 28 between the rotor 16 and the liner 18, the powder that has entered the inside is gradually pulverized and the particle size thereof becomes gradually finer. As described above, since there is an optimum crushing groove interval according to the particle size of the crushing raw material, the crushing efficiency can be improved by changing the crushing groove interval depending on the position of the crushing section. More specifically, it is preferable to set the groove interval in a stepwise manner from the raw material supply port 20 side to the product discharge port 22 side. It should be noted that the groove interval may be set in a stepwise manner only in one of the groove of the rotor 16 and the groove of the liner 18, but it is most preferable to set the groove interval of both in a stepwise manner.

Further, in terms of grinding efficiency, the rotor 16
There is also a dependency relationship between the groove spacing of the liner and the groove spacing of the liner 18. According to the results of research and experiments conducted by the present inventors, the ratio of the groove spacing of the liner 18 to the groove spacing of the rotor 16 is 1
It has been found that the crushing efficiency can be maximized when it is set between 2 and 2. For example, when the groove spacing of the rotor 16 is 4 mm, it is preferable that the groove spacing of the liner 18 be 4 mm to 8 mm, which is one to two times that range.

As described above, by forming such inclined grooves 34 on the outer peripheral surface of the rotor 16, the inclined groove 34 is formed between the rotor 16 and the liner 18 forming the crushing chamber, and the rotor 16 of the rotor 16 is inserted. The object particles to be crushed which collide with the convex portion 34d formed by the inclined groove 34 (see FIGS. 5D and 5E) are different from the flow direction of the air sucked by the blower from the product discharge port 22. Since it is repelled in the opposite direction (raw material supply port 20 side), it is possible to take a long time to stay in the crushing chamber.

Further, as described above, when the inclined groove is formed only on one of the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18, the other peripheral surface is formed on the rotary shaft 12.
The groove may be parallel to the center line 12a. Furthermore, one or both of the peripheral surfaces should be attached to the rotary shaft 1
A plurality of inclined grooves intersecting with the center line 12a of the two (longitudinal direction) at the same or different inclination angles, that is, FIG.
Like the liner 18 shown in FIG. 7A and the rotor 16 shown in FIG. 7B, the inclined groove 3 has a mesh shape in a front view.
It can be set to 6.

When the slanted groove 36 is formed in a mesh shape in a front view as in the example shown in FIG. 7, when viewed in the opposite direction, the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 18 are diamond-shaped. Alternatively, it can be considered that a plurality of columnar protrusions each having a square cross section are formed at a predetermined interval.

The method of forming such an inclined groove is not particularly limited, and any known forming method such as a method of forming a concave portion on the peripheral surface by cutting or a method of forming a convex portion by casting or the like is used. The method can also be applied,
In that case, abrasion resistance treatment may be performed as necessary.

Incidentally, also in the present invention, the gap 28 between the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 20 which serves as the crushing chamber.
Is not particularly limited, it can be appropriately selected according to the type of material to be crushed or the raw material and the particle size distribution of the product,
In the present invention, in particular, due to the presence of the characteristic inclined groove, the groove can be made larger than the conventional one, and can be set to a maximum width of 3 mm.

The mechanical crushing device of the present invention is basically constructed as described above, and its operation will be described below with reference to FIG.
And it demonstrates in detail based on FIGS.

First, the blowing operation of the air suction device (not shown) connected to the product discharge port 22 through the crushed product recovery filter is started. As a result, the air that flows in from the raw material supply port 20 becomes an air flow that flows in the casing 11 from left to right in FIG. Next, the rotor 16 is rotated in the direction of arrow b in FIG.

Next, a desired amount of raw material powder is continuously or intermittently supplied from the raw material supply port 32. Raw material supply port 32
The raw material powder supplied from is sucked together with the air flow, and reaches the gap 28 between the rotor 16 and the liner 18 which is a crushing chamber. Then, due to abrasion between the convex portions of the inclined grooves 32 and 34, collision with the convex surface of the inclined grooves 32 and 34 and collision with the concave surface due to vortex generated in the concave are repeated, Repeated collisions, while being appropriately crushed, gradually move to the right, become a crushed product, are sucked and discharged from the product discharge port 22, and are caught by the crushed product collecting filter outside the apparatus.

In this crushing process, the inclined grooves act as shown in FIG. That is, as indicated by the arrow in FIG. 4, the rotation direction b of the rotor 16 is a direction orthogonal to the direction a of the air flow, so that the air flow causes the gap 28 between the rotor 16 and the liner 18 to travel. The raw material powder particles that have entered will flow in the direction of rotation b and will proceed approximately in the direction c. Therefore, the raw material powder particles are drawn into or taken into the inclined groove 32 of the liner 18 or the inclined groove 34 of the rotor 16 directly or by the vortex flow generated in these inclined grooves 32 or 34, or collide with each other in the opposite direction. It is repelled and prevented from moving in the direction a of the air flow.

Therefore, the smooth movement of the air flow in the direction a is hindered, and the residence time in the crushing chamber formed by the gap 28 can be lengthened. Thus, the inclined grooves 32 and 34
Acts to hinder the flow of the raw material powder particles in the crushing chamber, the volume of the crushing chamber (gap 28) can be made large (gap is 3 mm at maximum), and even when the processing amount is increased, it is sufficient. The crushing time can be secured. By thus widening the space of the crushing chamber, the inclined grooves 32, 3
4 does not include excessively intense or irregular turbulence, and the raw material powder particles can be gently pulverized. It is possible to prevent excessive crushing of the body.

In the mechanical crushing device 10 of the present invention, the suction force of the air suction device and the rotation speed of the rotor 16 are set so that the raw material powder (object to be crushed) to be crushed can be smoothly crushed. It is preferable to appropriately select and set the type, particle size, throughput, size and shape of the rotor 16 and the liner 18, the shape and size of the inclined groove, and the interval of the gap to be the grinding chamber. For example, in a mechanical pulverizer having a rotor diameter of about 250 mm and an axial length of about 250 mm, the suction blower has an air flow rate of about 4 to 6 m ³ / min, and the rotation speed of the rotor 16 is about 6,000 to 13,000 rpm. Is appropriate.

[0067]

EXAMPLES Example 1 Using a mechanical pulverizer 10 having the structure shown in FIG. 1, pulverization was performed under the following conditions using a single-component toner having an average particle size of 500 μm as a raw material powder. here,
A plurality of inclined grooves 32 are formed on the inner peripheral surface of the liner 18 as shown in FIGS. 3 and 4, and the inclination angle θ is 10 degrees. On the other hand, a groove parallel to the generatrix direction of the rotor 16 (hereinafter, this groove is referred to as a “parallel groove”) is formed. Further, the sectional shapes of the inclined groove 32 and the parallel groove are as shown in FIG. 5, and the pitch of the inclined groove 32 and the parallel groove is set to 4 mm and the depth of the groove is set to 2 mm. The rotor 16 has a diameter of 242 mm and a length of 2
40 mm, the distance between the rotor 16 and the liner 18 is 2 mm
And A suction blower was connected to the product discharge port 22 of the mechanical crushing device 10 through a crushed product recovery filter, and the raw material toner was supplied from the raw material supply port 20 by a screw feeder.

The mechanical crushing apparatus 10 was equipped with a rotor 16 rotating at 10,000 rpm and a suction blower air volume of 4 m ³ /
Operate at min, and set the processing amount (supply speed) of raw material toner to 1
The crushing treatment was carried out by changing to 0, 20 and 30 kg / h. The powdered pulverized product discharged from the product discharge port 22 was captured and collected as a pulverized product by a pulverized product recovery filter having an average pore diameter of about 3 μm. The average particle size of the pulverized product thus obtained was measured, and the results plotted against the feeding rate are shown in FIG.

(Comparative Example 1) As a comparative example, the same mechanical crushing device as in Example 1 was used except that the inner peripheral surface of the liner 18 was formed into parallel grooves (the groove is described in JP-B-3-15489). The same pulverization was carried out under the same conditions as in Example 1 using the same apparatus as in Example 1.). The results are also shown in FIG.

As is apparent from FIG. 8, in the case of using the mechanical crushing apparatus of the present invention, it is found that a crushed material having an average particle size smaller than that of Comparative Example 1 can be obtained. In addition, in Example 1, no increase in the power of the mechanical pulverizer and no increase in the pulverization temperature due to the inclination of the grooves for pulverization were observed.

(Example 2 and Comparative Example 2) As Example 2, the same mechanical crushing apparatus as in Example 1 was used, and as Comparative Example 2, the same mechanical crushing apparatus as in Comparative Example 1 was used. Supply speed) is fixed at 10 kg / h, and the rotation speed of the rotor 16 is 10,000 rpm to 13,000 rp.
The raw material toner was crushed in the same manner as in Example 1 except that m was changed to obtain a crushed product. The average particle size of the obtained pulverized product and the volume ratio of particles of 5 μm or less contained in the pulverized product were measured. The result is shown in FIG. As is clear from FIG. 9, in the pulverized product having the same average particle diameter, the pulverized product produced by the mechanical pulverizing device of Example 2 has a content ratio of particles of 5 μm or less as compared with the pulverized product produced by the pulverizing device of Comparative Example 2. Was small. From this result, it can be seen that the mechanical crushing device of the present invention reduces over-milling.

(Example 3, Example 4 and Comparative Example 3) Using the mechanical pulverizer 30 shown in FIG.
The mono-component toner of μm was used as the raw material powder and pulverized under the following conditions. Here, as Example 3, a plurality of inclined grooves 34 were formed on the outer peripheral surface of the rotor 16 as shown in FIGS. 4 and 6, and the inclination angle θ was 10 degrees. Next, as Example 4, a plurality of inclined grooves 36 are formed in a mesh shape on the outer peripheral surface of the rotor 16 as shown in FIG. 7B, and the angle θ of the intersecting inclined grooves is set with respect to the generatrix direction of the rotor 16. ± 10
I took it. As Comparative Example 3, parallel grooves parallel to the generatrix direction were formed on the outer peripheral surface of the rotor 16. On the other hand, in any case, parallel grooves parallel to the generatrix direction were formed on the inner peripheral surface of the liner 18. Furthermore, these inclined grooves 34 and 3
The cross-sectional shape and dimensions of the parallel groove 6 and the groove parallel to the groove direction were the same as in Example 1.

In this mechanical crushing device 30, the number of rotations of the rotor 16 is 10,000 rpm, 11,000 rpm, 1
Change to 2,000 rpm and change the air volume of the suction blower to 4 m ³
/ Min, and the pulverization process was performed with the processing amount (supply speed) of the raw material toner set to 10 kg / h. The other crushing conditions and the crushed product after crushing were the same as those in Example 1. The average particle size of the pulverized product thus obtained was measured, and the results plotted against the rotor rotation speed are shown in FIG.

As is apparent from FIG. 10, in the case of crushing by the mechanical crushing device of the present Example 3, compared with the case of crushing by the mechanical crushing device of Comparative Example 3, at any rotor rotational speed, It can be seen that a ground product with a small particle size is obtained. It can be seen that the difference from Comparative Example 3 becomes more remarkable when pulverized by the mechanical pulverizer of Example 4. Also in the third and fourth embodiments, the power of the mechanical pulverizer is increased by inclining the groove for pulverization,
No increase in grinding temperature was observed.

(Embodiment 5) Using a mechanical crushing device 30 having a structure shown in FIG. 2, pulverization was carried out under the following conditions using a one-component toner having a maximum particle diameter of 2 mm as a raw material powder. Here, as Example 5, a plurality of parallel grooves are formed on the inner peripheral surface of the liner 18 in a direction parallel to the rotation axis, and the cross-sectional shape is such that one side faces the center of the rotor 16 and the other side defines this one side. A triangular shape (as disclosed in Japanese Examined Patent Publication No. 3-15489) having an angle of 45 degrees and a rear portion in the rotation direction of the rotor 16 becoming lower is formed. On the other hand, the outer peripheral surface of the rotor 16 is provided with both grooves that are inclined in a direction that impedes the flow of the material to be crushed and a direction that is opposite to the direction parallel to the rotation axis, and the inclination angles are 5 degrees and 10 degrees, respectively. The degrees were 20 degrees and 45 degrees. That is, FIG.
As in the rotor 16 shown in (b), the inclined groove is formed so that the front view has a mesh shape. The pitch of the parallel groove and the inclined groove was set to 4 mm, and the depth of the groove was set to 2 mm. The rotor 16 has a diameter of 242 mm and a length of 24.
The distance between the rotor 16 and the liner 18 was 0 mm, and the distance was 2 mm. A suction blower is connected to the product discharge port 22 of the mechanical crushing device 30 through a crushed product collecting filter,
The raw material toner was supplied from the raw material supply port 20 by a screw feeder. Air volume of suction blower 4m ³ / min
The operating amount of the raw material toner (supply speed) is 20 kg /
As h, the rotation speed of the rotor 16 was adjusted so that the particle size of the pulverized product was 12 μm.

(Comparative Example 4) As Comparative Example 4, a test was also conducted under the same operating conditions with a rotor 16 having a groove inclination angle of 0 ° on the outer peripheral surface, that is, a rotor 16 provided with a groove parallel to the rotation axis. .

In order to pulverize the raw material toner to an average particle diameter of 12 μm, the rotational speed of the rotor 16 was adjusted as follows according to the groove inclination angle of the outer peripheral surface of the rotor 16. That is,
When the tilt angle is 0 degree, the rotor speed is 11,000 rpm.
When the tilt angle is 5 degrees, the rotor speed is 10,500r
pm, the rotor speed was adjusted to 10,000 rpm when the tilt angle was 10 degrees and 20 degrees, and the rotor speed was adjusted to 9,800 rpm when the tilt angle was 45 degrees. The results of plotting the relationship between the volume ratio of so-called coarse particles of 18 μm or more contained in the pulverized product thus obtained and the inclination angle of the rotor groove are shown in FIG. 11. In addition, 8 included in crushed products
FIG. 12 shows the result of plotting the relationship between the volume ratio of so-called over-milled particles of not more than μm and the inclination angle of the rotor groove.

As is clear from FIGS. 11 and 12, when the crushing is performed by the mechanical crushing device of the fifth embodiment, the outer peripheral surface of the rotor 16 is smaller than that when the crushing is performed by the mechanical crushing device of the comparative example 4. It can be seen that when the groove inclination angle is in the range of 5 degrees to 45 degrees, the effects of both over-pulverization prevention and coarse particle contamination prevention are large.

Example 6 Using the mechanical crushing device 30 having the structure shown in FIG. 2, a test was conducted by using a one-component toner having a maximum particle diameter of 2 mm as a raw material powder. On the inner peripheral surface of the liner 18, a plurality of grooves 3 are formed in a direction parallel to the rotation axis direction of the rotor 16.
2, the groove pitch is 4 mm, the groove depth is 2 mm, and FIG.
In (c), the angle α is 45 degrees, the angle β is 15 degrees, and 32d is 1
mm.

On the other hand, the rotor 16 has a diameter of 242 mm and a length of 240 mm, and is 10 degrees in a direction that impedes the flow of the material to be ground with respect to the direction parallel to the rotation axis, and 10 degrees in the opposite direction.
5 (d) has an angle δ of 45 degrees, an angle γ of 15 degrees, and 34d of 1.4 mm. A pitch of 4 mm and a groove depth of 2 mm were used. Liner 18 and rotor 16
The gap 28 between them is 2 mm.

With this device 30, the number of rotations of the rotor is 10,000.
The raw material powder was pulverized at a target average particle diameter of 12 μm at a flow rate of rpm, a suction blower air volume of 4 m ³ / min, and a raw material supply rate of 10 kg / h. The crushed product was collected by a bag filter. When the particle size of the obtained pulverized product was measured, the average particle size was 11.8 μm, the volume ratio containing particles of 18 μm or more was 0.8%, and the volume ratio containing particles of 7 μm or less was 2.1%. .

Comparative Example 5 For comparison, a plurality of grooves 32 and 34 are formed on the inner peripheral surface of the liner 18 and the outer peripheral surface of the rotor 16 in a direction parallel to the rotational axis direction of the rotor 16,
The cross-sectional shapes of the grooves 32 and 34 are the same as those of the liner 18 of Example 5 (as described in Japanese Patent Publication No. 3-15489), and the other parts are the same as those of Example 6 and the same as those of Example 6. The crushing process was performed under the conditions. The average particle size of the obtained pulverized product was 12.8 μm, which was 1 μm coarser than that of Example 6, and the volume ratio containing particles of 18 μm or more was 6.4%.
The volume ratio was 8 times that of Example 6, and the volume ratio containing particles of 7 μm or less was 3.6%, which was a 1.7 times increase.

(Embodiment 7) The cross-sectional shape of the groove of the liner 18 is the same as in Embodiment 6 except that the angle α in FIG. 5B is 60 degrees and the angle β is 15 degrees. Different raw materials were treated under the same conditions. The obtained product was similar to the product of Example 6, and had an average particle size smaller than that of Comparative Example 5 and a sharp particle size distribution.

(Embodiment 8) The shape of the cross section of the groove 34 of the rotor 16 which is perpendicular to the groove cutting direction is shown in FIG. 5 (e) where the angle δ is 50 degrees, the angle γ is 15 degrees, and the other cases are carried out. Using the same equipment as in Example 6, the same raw material was treated under the same conditions.
The obtained pulverized product was the same as the pulverized product of Example 6, and as compared with Comparative Example 5, the average particle size was smaller and the particle size distribution was sharper.

(Embodiment 9) A crushing device 3 having the structure shown in FIG.
0 was used as a pulverization raw material, and pulverization was performed under the following conditions using a styrene acrylic resin having an average diameter of 500 μm as a main component. On the outer peripheral surface of the rotor 16 having an outer diameter of 150 mm, columnar protrusions having a rhombic cross section and a height of 2 mm are arranged at intervals of 4 mm in the rotation direction. Also, the liner 18
Grooves having a substantially triangular cross section parallel to the generatrix were formed at a predetermined interval on the inner peripheral surface of, and the gap 28 between the rotor 16 and the liner 18 was set to 1.5 mm. This crusher 30
Was operated at a rotation speed of the rotor 16 of 14000 min ⁻¹ and an air flow rate of the suction blower of 1.5 m ³ / min, and the raw material toner was supplied at 5 kg / h for pulverization. The average particle size (50% diameter) of the pulverized product thus obtained was measured, and the ratio of the groove of the liner 18 to the groove of the rotor 16 (the groove interval of the liner 18 / the arrangement interval of the protrusions of the rotor 16) The result plotted against is shown in the graph of FIG. As shown in this graph, it was found that the crushing effect is enhanced when the groove spacing of the liner 18 is 1.0 to 2.0 times the groove spacing of the rotor 16.

(Examples 10 and 11 and Comparative Examples 6 and 7)
Using the crushing device 30 having the structure shown in FIG. 2, the maximum diameter is 2 mm.
1 containing styrene acrylic resin having an average diameter of 500 μm and a maximum diameter of 0.08 mm (average diameter of 20 μm) as a main component
The pulverization treatment was performed under the same conditions as in Example 9 except that the component toner was used as the pulverization raw material and the supply amount of the raw material toner was 3 kg / h. Results obtained by using the liner 18 provided with the grooves having the groove intervals defined by the above (Equation 1) (50
% Diameter) is shown in Table 1 of FIG. For comparison, Table 1 also shows the results when the liner 18 having the groove spacing outside the range defined by the same (formula 1) is used.
As is clear from Table 1, there is an optimum crushing groove interval according to the particle size of the crushed raw material, and it is possible to improve the crushing efficiency by selecting the groove interval according to the maximum particle size of the raw material. I understood.

(Examples 12 and 13 and Comparative Example 8) FIG.
Using the crushing device 30 having the structure shown in FIG. 2, the liner 18 is divided into two parts in the height direction by using a one-component toner having an average diameter of 500 μm and a styrene acrylic resin as a main component as a crushing raw material. The grinding process was performed under the same conditions as in Examples 10 and 11, except that the liner 18 divided into the liner on the side was used. Table 2 in FIG. 15 shows the test results obtained by changing the groove spacing of the liner 18 between the liner on the supply port side and the liner on the discharge port side. For comparison, Table 2 also shows the results of tests using the liner 18 having the same groove spacing on the upper and lower sides. From Table 2, it is clear that there is an optimum crushing groove interval according to the particle size of the crushing raw material, and it was found that the crushing efficiency can be improved by changing the crushing groove interval in the crushing section. .

Although the mechanical crushing device of the present invention has been described in detail above, the present invention is not limited to the above-mentioned embodiments.
It goes without saying that various improvements and changes may be made without departing from the scope of the present invention.

[0089]

As described in detail above, according to the present invention,
On the outer peripheral surface of the rotor, the inner peripheral surface of the liner, or both, there are provided a plurality of grooves that are inclined with respect to the direction parallel to the rotation axis of the rotor in a direction that impedes the flow of the raw material powder to be ground. Since these grooves prevent the raw material powder from passing through the pulverizing chamber formed by the gap formed between the rotor and the liner, the residence time of the raw material powder in the pulverizing chamber can be lengthened. It is possible to obtain fine high-quality fine powder that does not include coarse particles, has a small average particle size, for example, an average particle size of the order of 5 to 15 μm, and has a narrow particle size distribution width and sharpness.

Further, according to the present invention, since coarse particles are prevented from being generated and the particles are crushed under mild crushing conditions, excessive crushing is prevented, and the particle size is smaller than necessary, for example, 5 μm or less or a few. It is possible to reduce the generation of fine particles of μm or less. Furthermore, according to the present invention, the volume of the crushing chamber can be increased, the groove interval between the rotor and the liner can be optimized according to the maximum diameter of the raw material powder, and the groove interval between the two can be adjusted so that the material to be ground is supplied. Since the crushing efficiency can be improved by setting the value gradually smaller from the mouth side toward the discharge side, and further by setting the ratio of the groove interval of the liner to the groove interval of the rotor to 1 to 2, the treatment efficiency can be improved. The amount can be increased and the productivity can be improved. Therefore, the mechanical crushing device of the present invention is suitable for crushing a resin and a powder containing the resin as a main component,
In particular, it is suitable for pulverizing dry toner and powder paint.

[Brief description of drawings]

FIG. 1 is a schematic sectional view of an embodiment of a mechanical crushing device according to the present invention.

FIG. 2 is a schematic sectional view of another embodiment of the mechanical crushing device according to the present invention.

FIG. 3 is a perspective view of an example of a liner used in the mechanical crushing device shown in FIG.

FIG. 4 is a schematic diagram for explaining a forming angle of an inclined groove on a rotor or a liner of a mechanical crushing device according to the present invention.

5 (a) is a view taken along line VV in FIG.
FIG. 3B is a partial cross-sectional arrow view in a cross section orthogonal to the groove direction including a schematic image of streamlines in the grooves of the rotor and the liner, and FIGS. 6B and 6C are views of the groove of the liner shown in FIG. FIG. 3D is a partial cross-sectional view showing an example of a cross-sectional shape orthogonal to the groove direction, and (d) and (e) are parts showing an example of a cross-sectional shape of the rotor groove shown in (a) orthogonal to the groove direction. It is a sectional view, (f) is a schematic diagram showing an example of the crushing action of the object to be crushed by the groove of the rotor and the liner,
(G) is a schematic diagram showing an example of a vortex generated in the groove of the rotor.

FIG. 6 is a perspective view of an embodiment of a rotor used in the mechanical crushing device shown in FIG.

7 (a) and 7 (b) are schematic front views of another embodiment of the liner and the rotor used in the mechanical crushing device of the present invention.

FIG. 8 is a graph showing the results of Example 1 and Comparative Example 1.

9 is a graph showing the results of Example 2 and Comparative Example 2. FIG.

10 is a graph showing the results of Example 3, Example 4 and Comparative Example 3. FIG.

11 is a graph showing the results of Example 5 and Comparative Example 4. FIG.

FIG. 12 is a graph showing the results of Example 5 and Comparative Example 4.

13 is a graph showing the results of Example 9. FIG.

FIG. 14 is a table showing the results of Examples 10 and 11 and Comparative Examples 6 and 7.

15 is a table showing the results of Examples 12 and 13 and Comparative Example 8. FIG.

FIG. 16 is a schematic cross-sectional view of a conventional rotary mechanical crushing device.

17 (a), (b), (c) and (d) are:
FIG. 17 is a partial cross-sectional view showing another structure of each of the rotor and the casing in the conventional crushing device shown in FIG. 16.

18 (a) and 18 (b) are partial cross-sectional views showing still another structure of the rotor and the casing in the conventional crushing device shown in FIG. 16, respectively.

[Explanation of symbols]

10,30 Mechanical crusher 11 casing 12 rotation axes 12a Center of rotation (center line) 14 rotor unit 16 rotor 18 liner 20 Raw material supply port 22 Product outlet 24a, 24b bearing 26a, 26b circular side plates 28 Gap 32, 34, 36 inclined groove 32a, 32b, 34a, 34b Wall surface of inclined groove 32c, 34c Bottom of inclined groove 32d, 34d Convex part of inclined groove 32S, 34S main vortex α, β, γ, δ Inclined groove sectional inclination angle a Airflow direction (direction parallel to the axis of rotation) b Rotor rotation direction c Direction of movement of crushed particles (object to be crushed)

   ─────────────────────────────────────────────────── ─── Continued front page    (72) Inventor Kazuzo Ozawa             5-3-1 Tsurugaoka, Oi-cho, Iruma-gun, Saitama Prefecture               Nisshin Seifun Group Headquarters Production Technology             In the laboratory F-term (reference) 2H005 AB04                 4D063 FF14 FF28 FF37 GA10 GC05                       GC12 GC21 GD02 GD24                 4D065 AA07 BB02 BB11 EB14 EB20                       ED06 ED14 ED27 EE02 EE19

Claims (6)

[Claims] 1. A rotor supported by a rotary shaft and having a plurality of grooves formed on its outer peripheral surface, and a rotor provided on the outer side of the rotor with a desired gap from the outer peripheral surface of the rotor. A liner having a plurality of grooves formed therein, which is a mechanical pulverizing device for pulverizing an object to be pulverized in the gap, wherein at least one of the grooves of the rotor and the liner is parallel to the rotation axis. With respect to the direction of impeding the flow of the object to be crushed, at least one of the interval of the groove of the rotor and the groove of the liner is calculated by the following formula based on the particle diameter of the object to be crushed A mechanical crushing device characterized in that the intervals are. p = kD + 1 (mm) where p: groove spacing of the rotor and groove spacing of the liner (mm) k: coefficient (2 to 3) D: maximum diameter of object to be ground (mm) 2. A rotor supported by a rotating shaft and having a plurality of grooves formed on its outer peripheral surface, and a rotor provided outside the rotor with a desired gap from the outer peripheral surface of the rotor. A liner having a plurality of grooves formed therein, which is a mechanical pulverizing device for pulverizing an object to be pulverized in the gap, wherein at least one of the grooves of the rotor and the liner is parallel to the rotation axis. With respect to the direction of impeding the flow of the material to be crushed, at least one of the interval of the groove of the rotor and the interval of the groove of the liner as the crushed object from the supply port side to the discharge port side. A mechanical crushing device characterized by being set small in stages. 3. The mechanical crushing device according to claim 1, wherein the ratio of the groove spacing of the liner to the groove spacing of the rotor is 1 to 2. 4. The mechanical crushing device according to claim 3, wherein the gap between the grooves of the liner is 4 mm to 8 mm. 5. The inner peripheral surface of the liner has a groove inclined in a direction that impedes the flow of the object to be ground with respect to the direction parallel to the rotation axis, and the object to be ground with respect to the direction parallel to the rotation axis. 5. The mechanical crushing device according to any one of claims 1 to 4, wherein both grooves that are inclined in the opposite direction and the direction that obstructs the flow are formed. 6. A groove on the outer peripheral surface of the rotor, the groove being inclined in a direction that impedes the flow of the object to be ground relative to the direction parallel to the rotation axis, and the flow of the object to be ground relative to the direction parallel to the rotation axis. The mechanical crushing device according to any one of claims 1 to 5, wherein both grooves that are inclined in the opposite direction and in the opposite direction are formed.