JPH09201543A - Mechanical crusher - Google Patents

Abstract

PROBLEM TO BE SOLVED: To efficiently produce a crushed product of a small particle size which is free from the contamination of coarse particles and has sharp particle size distribution by slanting the grooves of a rotor and/or a liner in the direction to hinder the flow of a material to be crushed to a parallel with a rotary shaft. SOLUTION: In a mechanical crusher 10, grooves are formed on the outer surface of a rotor 16 and/or the inner surface of a liner 18. The grooves are formed by slanting in the direction to hinder the flow of a material to be crushed to the parallel direction to a rotary shaft 12. The passing velocity toward a discharge opening 22 of crushed particles which entered the clearance between the rotor 16 and the liner 18 is reduced, and the particles are scattered to the supply port side by the recessions of the grooves of the rotor 16. Accordingly, the generation of an excessive vortex is prevented to prevent excessive collision and crushing, and the long retention time of the particles decreases the particle size and prevents the generation of coarse particles at the same time.

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 mechanical crushing device for finely crushing such an object to be crushed, Japanese Patent Laid-Open No. 59-105853 and Japanese Patent Publication No.
A fine pulverizer described in Japanese Patent No. 15489 is known. As shown in FIG. 13, the fine crusher 50 supports a cylindrical rotor (rotor) 54, which has a large number of concavo-convex portions 54 parallel to the generatrix on the outer peripheral surface in the circumferential direction, by a rotating shaft 56. A cylindrical stator (liner) 62 in which a large number of concavo-convex portions 60 parallel to the generatrix are circumferentially continuous on the inner peripheral surface of the rotor 54 with a minute gap 58 from the outer peripheral surface of the rotor 54 is mounted on the rotor 54. It is fitted to the outside 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 at 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 pulverizer 50, the gap between the gaps 58 corresponding to the pulverizing chamber is set to 1 mm or less, and the rotor 54 is rotated at a high speed, so that the stator 6
2 and the rotor 54, the crushed objects collide with each other due to the vortex flow constantly generated in these recesses from both the uneven surfaces,
It is said that fine pulverization is effectively performed by receiving a shearing force, and a pulverized product having a relatively narrow particle size distribution range of micron order to 10's of micron order is obtained.

In such a fine crusher 50, the rotor 54
14A, 14B, 14C, and 14D are proposed as a combination of the uneven portion 52 and the uneven portion 60 of the stator 62. In these figures, 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. 15 (a) and 15 (b), the outer peripheral surface of a rotor 54 and a stator (cylindrical body) such as the above-described 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.

[0007]

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 rotation speed of the rotor must be increased, and energy efficiency, bearing life, noise, vibration, and air exhaust temperature rise. Etc. is a problem. 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. Also, for example, in the case of dry toner,
Particles that are excessively finer than the target particle size are removed by classifying means to improve product quality, and the particle size distribution is adjusted.However, if the rotation speed of the rotor is high, many particles that are excessively crushed will be generated. Therefore, 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, if the crushing chamber is narrowed in this way, the processing capacity decreases, and the processing amount decreases. In addition, depending on the supply amount of the raw material, especially when the supply amount exceeds the processing capacity, frictional heat during crushing, etc. This may cause a problem that the temperature of the crushing chamber rises excessively. 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 described in Japanese Patent Laid-Open No. 7-155628, in addition to the uneven portion parallel to the bus bar on the outer peripheral surface of the rotor 54 and the inner peripheral surface of the stator 62, the uneven surface orthogonal to the bus bar is provided. 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.

[0011]

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 liner having a plurality of grooves formed on an inner peripheral surface thereof, the liner being fitted to have a desired gap. Further, the present invention provides a mechanical crushing device, wherein at least one of the grooves of the liner is inclined in a direction that impedes the flow of the object to be crushed with respect to the direction parallel to the rotation axis.

Here, it is preferable that the liner further has a groove on its inner peripheral surface, which is inclined in a direction opposite to a direction in which the flow of the material to be ground is impeded with respect to a direction parallel to the rotation axis. Further, it is preferable that the rotor further has a groove on its outer peripheral surface, which is inclined in a direction opposite to a direction that impedes the flow of the object to be ground with respect to a direction parallel to the rotation axis. It is preferable that an inclination angle of one of the groove of the rotor and the groove of the liner with respect to the direction parallel to the rotation axis is 5 degrees or more and less than 90 degrees.

Further, the groove of the rotor has both a direction that impedes the flow of the material to be ground with respect to the direction parallel to the rotation axis and a groove that is inclined in the opposite direction, and the inclination angle is 5
It is preferably not less than 45 degrees and not more than 45 degrees. The cross-sectional shape of the groove in the direction perpendicular to the direction of the groove of the rotor is such that the surface on the front side with respect to the rotation direction of the rotor is from 30 degrees in the direction opposite to the rotation direction of the rotor with respect to the radial direction of the rotor. Inclining at an angle within a range of up to 30 degrees in the rotation direction of the rotor, a surface on the rear side with respect to the rotation direction of the rotor is from 30 degrees in a direction opposite to the rotation direction of the rotor with respect to the radial direction of the rotor. It is preferably inclined at an angle within the range of up to 70 degrees.

Further, the groove of the liner has a groove inclined to a direction parallel to the rotation axis of the rotor in a direction of impeding the flow of the material to be crushed and a groove inclined to the opposite direction, The inclination angle is preferably 5 to 45 degrees.
Further, the cross-sectional shape of the groove in the direction perpendicular to the direction of the groove of the liner is such that the front surface with respect to the rotation direction of the rotor is from 30 degrees to 70 degrees in the rotation direction of the rotor with respect to the center direction of the rotor. Inclining to an angle within the range, the rear surface with respect to the rotation direction of the rotor is in a range from 30 degrees in the direction opposite to the rotation direction of the rotor to 30 degrees in the rotation direction of the rotor with respect to the center direction of the rotor. It is preferable to incline at an angle within.

[0015]

In the mechanical crushing device of the present invention, the raw material powder is finely crushed in the crushing chamber formed by the gap between the rotor and the liner, but is sucked from the product discharge port for discharging the product during operation. The air that has flowed in together with the raw material powder supplied from the raw material supply port is in the bus line direction of the rotor or liner,
That is, since the raw material powder is flowing in a direction parallel to the rotation axis of the rotor, the raw material powder that has entered the air flow into the gap between the rotor and the liner, which is the grinding chamber, is orthogonal to this air flow due to the rotation of the rotor. It receives a force in the direction of rotation and is made to flow in the rotation direction of the rotor. However, in the pulverizer of the present invention, in order to prevent the flow of the raw material powder in the flowing direction,
Since a plurality of grooves inclined in the direction of the rotation axis are formed on the rotor or the liner or on the peripheral surfaces of both, the passing speed of the pulverized particles entering the gap between the rotor and the liner to the discharge port decreases, and Since the protrusions of the groove of the rotor blow the particles toward the supply port side, it is possible to lengthen the time during which the crushed particles stay in the crushing chamber, even if the space between the gaps, that is, the space of the crushing chamber is kept wide. Therefore, according to the present invention, it is possible to prevent the generation of excessive eddy currents, it is possible to prevent excessive collision, it is possible to prevent over-milling, it is possible to take a long residence time of the crushed particles, small particle size At the same time, it is possible to prevent the generation of coarse particles.

[0016]

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 FIG. 1, the mechanical crusher (hereinafter referred to as crusher) 10 is a horizontal crusher,
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 1
2 is arranged parallel to the mounting surface of the mechanical crushing device 10, that is, horizontally, and is supported on the left and right side wall surfaces of the casing 11 in the figure via bearings 24a and 24b. One end of the rotary shaft 12, that is, the right end (on the bearing 24b side in the illustrated example) is connected to a driving device such as a motor via a winding transmission mechanism such as a pulley and a transmission belt (not shown) or a gear transmission mechanism. Has been done.

The four rotor units 14 are fixed to the rotary shaft 12 by a key (not shown), and circular side plates 26a and 26 for sandwiching 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 constant 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. In addition, the liner 18 is provided on both sides of the casing 11.
The volume and shape are set so that a space of appropriate size is formed on both outer sides of (and the rotor 16), 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 is the product. The (crushed material) is connected to the discharge port 22. The product discharge port 22 is sucked by an air suction device such as a blower (not shown), sucks the object to be crushed supplied from the raw material supply port 20 together with the air, and crushes the product obtained in the device with the air. Along with this, the product is discharged from the product 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.

The most characteristic parts of the mechanical crushing device 10 of the present invention are the outer peripheral surface of the rotor 16 and the liner 1.
A plurality of grooves are formed on either one or both of the inner peripheral surfaces of 8, and these grooves are 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. is there. That is, as shown in FIG. 3, only the envelope of the inner peripheral surface of the liner 18 is shown by a dotted line with respect to the direction parallel to the rotation center (center line) 12a of the rotary shaft 12 shown by a dashed line. Direction of the rotating rotor 16 (arrow b in the figure)
The groove 32 is formed so as to incline in the opposite direction.
Here, in FIG. 3, the liner 18 is
Only the liner units that make up are shown, and the others are shown with their envelopes in dotted lines. Of course, in the present invention,
It is needless to say that the number of liner units forming the liner 18 is not limited, and 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.

By the way, in the present invention, at least one of the groove 34 on the outer peripheral surface of the rotor 16 and the groove 32 on the inner peripheral surface of the liner 18 flows in the direction parallel to the rotating shaft 12 of the object to be crushed (particles). Must be inclined in the direction that prevents As shown schematically in FIG.
Of the crushed object moving in the gap 28 between the outer peripheral surface of the rotor 18 and the inner peripheral surface of the liner 18 (the velocity vector of the flow of particles) is the velocity vector of the rotation of the rotor 16 (direction:
It is given as a composite vector of the rotation direction b, length: velocity) and the velocity vector of the 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 drawing), 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 including the width, depth, pitch and the like of the groove (hereinafter referred to as an inclined groove) 32 inclined to the air flow direction a on the inner peripheral surface of the liner 18 is not particularly limited. , The shape of the inclined groove 32 in the cross section orthogonal to the direction of the groove 32 of the liner 18 is a sawtooth shape, a trapezoidal shape, a rectangular shape,
It may have any shape such as an arc shape, but in particular, as shown in FIG.
As shown in (a), one side faces the center of the rotor 16 and the other side forms an angle of 45 to 60 degrees with the one side, and the rotor 16 rotates in the direction of rotation (b) The rear side becomes a triangular shape (Japanese Patent Publication 3-1.
(As disclosed in Japanese Patent No. 5489).

For example, FIGS. 5B and 5C show typical examples of the sectional shape of the inclined groove 32 of the liner 18 in a cross section orthogonal to the direction of the inclined groove 32 of the liner 18. FIG.
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. Where the groove 32
The cross-sectional inclination angles α and β are in the range 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. Preferably within. Further, in FIGS. 5B and 5C, the bottom 32 c of the groove 32 of the liner 18 and the convex portion 32 d of the liner 18 between the adjacent grooves 32 are both 1/2 or less of the pitch p of the groove 32. Is preferred. The bottom portion 32c of the groove 32 of the liner 18 is shown in FIG.
It is more preferable not to form a straight line portion as shown in (b) and (c) but to form a vertex of a triangle or be rounded, for example, to form an arc shape as shown in FIG. 5 (a).

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, but 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. Regarding the inclination angle of the inclined groove 34 of the rotor 16, the liner 18
Similar to the inclined groove 32, there is no particular limitation, and the preferable conditions are exactly the same. The shape and size of the inclined groove 34 of the rotor 16 are not particularly limited as in the inclined groove 32 of the liner 18, and may have any shape, but as shown in FIG. On the rotor 16
The shape of the inclined groove 34 in a cross section orthogonal to the direction of the groove is such that one side is 5 to 25 degrees and the other side is 45 to 45 degrees rearward in the rotation direction (b) of the rotor 16 with respect to the radius toward the center of the rotor 16. 60
It is preferably triangular with an angle of 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. FIG.
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 − with respect to the rotation direction b, respectively.
30 degrees to 30 degrees, that is, within a range from 30 degrees in the direction opposite to the rotation direction b to 30 degrees in the rotation direction b and -70 degrees to
It is preferably −30 degrees, that is, in the range of 30 to 70 degrees in the direction opposite to the rotation direction. 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. In addition, the bottom portion 34c of the groove 34 of the rotor 16 is shown in FIG.
It is more preferable not to form a straight line portion as shown in (d) and (e), but to form a triangular vertex or be rounded, for example, to form an arc shape as shown in FIG. 5 (a).

The reason why the cross-sectional shapes of the grooves 32 and 34 are limited will be described below as a preferred embodiment of the present invention. In the crusher of the present invention, in order to prevent an excessive increase in exhaust gas temperature, that is, an increase in pulverization temperature and an increase in pulverization power, the flow is not excessively disturbed by the rotation of the rotor, as shown in the schematic diagram of FIG. To form vortices of suitable strength in the grooves 32 and 34 of the liner 18 and rotor 16,
It is necessary to improve the crushing performance. Here, the reference numeral 32 s indicates the liner 18 generated by the rotation of the rotor 16.
The reference numeral 34 s shows an image of streamlines in the groove 32 of the rotor 16, and reference numeral 34 s 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
In the direction of, and collides with the surface 32a of the liner 18 to be crushed (see FIG. 5f). 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, the fine particles stay in the grooves 32 and 34 by riding on the flow in the grooves 32 of the liner 18 or the grooves 34 of the rotor 16, and the peaks and valleys of the grooves 32 and 34 of the rotor 16 and the liner 18 alternate at high speed. It is crushed to a certain fineness due to pressure fluctuations caused by passing each other. 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 and 70 degrees or less in the rotational direction so that an appropriate impact is given when the pulverized material particles repelled by the rotor 16 collide. preferable. Groove 34 of rotor 16 and liner 18
It is important that the vortex in the groove 32 of the rotor 16 has an appropriate vorticity, a large space, and stability.
4, the inclination angle γ of the front side surface 34a and the groove 32 of the liner 18
By setting the inclination angle β of the rear side surface 32b to be 0 degrees or more and 0 degrees or less, respectively, the spaces of the grooves 32 and 34 can be widened.

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 applies the action of crushing to particles, and is denoted by reference numerals 32s and 34 in FIG. 5a.
s (see FIG. 5g). Further, 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 becomes small. To do. Considering these things, the inclination angle γ is −30 degrees or more and 30 degrees or less in the rotation direction b, that is, 3 degrees in the direction opposite to the rotation direction b.
It is preferably within the range of 0 degrees to 30 degrees in the rotation direction b. The inclination angle β of the rear side surface 32b of the groove 32 of the liner 18
For the same reason, the rotation direction b is −30 degrees or more and 30 degrees or more.
It is preferably within a range of 30 degrees or less, that is, 30 degrees in the direction opposite to the rotation direction b to 30 degrees in the rotation direction b.

Next, the preferable pitch of the grooves in the present invention will be described. If the groove pitch p is reduced with the same rotor 16 diameter, the number of grooves (32, 34) increases,
Wall surfaces (32a, 32b, 34a, 3) of the grooves (32, 34)
4b) is more likely to collide with and is preferable for obtaining a fine grain size. 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 present invention, it is preferably about 2 mm to 10 mm. Also, the groove (32, 3
The depth of 4) is preferably ⅕ or more and 3 or less times the pitch. The groove pitch p and the depth are preferably the same for the groove 34 of the rotor 16 and the groove 32 of the liner 18, but may be different for both grooves 32 and 34.

Further, as described above, by forming such an inclined groove 34 on the outer peripheral surface of the rotor 16,
The object to be crushed which has entered the gap 28 between the rotor 16 and the liner 18 forming the crushing chamber and has collided with the convex portion 34d (see FIGS. 5D and 5E) formed by the inclined groove 34 of the rotor 16 Since the particles are repelled in the direction opposite to the direction of the flow of the air sucked by the blower or the like from the product discharge port 22 (the side of the raw material supply port 20), 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. The method for forming such an inclined groove is not particularly limited, and any known forming method such as a method for forming a concave portion on the peripheral surface by cutting or a method for forming a convex portion by casting is applied. Further, in that case, an abrasion resistance treatment can be carried out if necessary. By the way, in the present invention as well, the gap 2 between the outer peripheral surface of the rotor 16 and the inner peripheral surface of the liner 20 which serves as the crushing chamber.
The interval of 8 is not particularly limited and can be appropriately selected according to the type of material to be crushed, the raw material and the particle size distribution of the product, but in the present invention, in particular, due to the presence of the characteristic inclined groove, It can be made larger than before, up to 3
It can be set to mm width.

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 suction blower (not shown) connected to the product discharge port 22 through the crushed product recovery filter starts the blowing operation, and the air flowing in from the raw material supply port 20 flows through the inside of the apparatus from the left side in FIG. It becomes an air flow that flows to the right. Then, the rotor 16 is installed in FIG.
Rotate in the direction of arrow b inside. Next, a desired amount of raw material powder is continuously or intermittently supplied from the raw material supply port 32. Then, the supplied raw material powder is sucked together with the air flow, and reaches the gap 28 between the rotor 16 and the liner 18, which is the 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 the vortex generated in the concave are repeated, and Repeatedly colliding with each other, gradually moving to the right while being appropriately crushed, and becoming a crushed product.
It is sucked and discharged from 0, and is captured by a filter for collecting crushed products outside the apparatus.

In this crushing process, the inclined groove acts 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. In this way, the inclined grooves 32 and 34 act so as to obstruct the flow of the raw material powder particles in the crushing chamber,
The volume of the crushing chamber (the interval between the gaps 28) can be made large (the interval between the gaps is 3 mm at maximum), and a sufficient crushing time can be secured even when the processing amount is increased. By thus widening the space of the crushing chamber, the raw powder particles can be gently crushed without excessively disturbing or irregularly disturbing the vortex generated by the inclined grooves 32 and 34. Despite the long residence time in the crushing chamber, it is possible to prevent over-crushing of the raw material powder. In the mechanical crushing device 10 of the present invention, the suction force by the suction blower and the rotation speed of the rotor 16 are such that the kind and particle size of the raw material powder (object to be crushed) to be crushed can be smoothly crushed. It is preferable to appropriately select and set the processing amount, the size and shape of the rotor 16 and the liner, the shape and size of the inclined groove, the interval of the gap to be the crushing chamber, and the like. 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 volume of about 4 to 6 m ³ / min and the rotor 16 has a rotation speed of about 6,000.
0 to 13,000 rpm is suitable.

[0038]

【Example】

(Example 1) Using a mechanical pulverizer 10 having a structure shown in FIG. 1, pulverization was carried out under the following conditions using a one-component toner having an average particle size of 500 μm as a raw material powder. Where the liner 18
As shown in FIGS. 3 and 4, a plurality of inclined grooves 32 were formed on the inner peripheral surface of the, and the inclination angle θ was 10 degrees. on the other hand,
A groove parallel to the generatrix direction (hereinafter, this groove is referred to as a “parallel groove”) is formed on the outer peripheral surface of the rotor 16. further,
The cross-sectional shapes of the inclined groove 32 and the parallel groove are both shown in FIG.
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. Also, the rotor 16 has a diameter of 242 mm and a length of 240 mm.
The distance between 6 and the liner 18 was 2 mm. 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 is equipped with a rotor 16 rotating at 10,000 rpm and a suction blower having an air flow rate of 4 m ³ / min.
Operating at a feed rate of 10 or 2 for the raw material toner.
The crushing treatment was carried out by changing it to 0 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 a parallel groove (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 clear from FIG. 8, in the case of using the mechanical crushing device of the present invention, the crushed product having a smaller average particle diameter than the comparative example 1 can be obtained in the invention sample 1. In addition, in Inventive Example 1, no increase in power of the mechanical pulverizer and no increase in pulverization temperature due to tilting of the grooves for pulverization were observed.

(Example 2 and Comparative Example 2) Using the same mechanical crushing apparatus as in Example 1 as Example 2 and the same mechanical crushing apparatus as in Comparative Example 1 as Comparative Example 2, the throughput of raw material toner ( Supply speed) is fixed at 10 kg / h, and rotor 1
The raw material toner was crushed in the same manner as in Example 1 except that the rotation speed of No. 6 was changed from 10,000 rpm to 13,000 rpm 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 crushed product having the same average particle diameter, the content of particles having a particle size of 5 μm or less in the crushed product of the mechanical crushing device of Inventive Example 2 as compared with the crushed product of the crushing 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.

(Examples 3, 4 and Comparative Example 3) Using the mechanical pulverizer 30 shown in FIG. 2, the average particle size is 200.
The mono-component toner of μm was used as the raw material powder, and the powder was 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
Degree. 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 rotation speed of the rotor 16 is 10,000 rpm, 11,000 rpm, 12.0 rpm.
Instead of 00 rpm, the suction blower was operated with an air flow rate of 4 m ³ / min, and the processing amount (supply speed) of the raw material toner was 10 kg / min.
As h, crushing treatment was performed. 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 Example 3 of the present invention, as 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 is more remarkable when the mechanical crushing apparatus of Inventive Example 4 is used for crushing. In addition, in Examples 3 and 4 of the present invention as well, the power of the mechanical crushing device was increased by inclining the crushing groove,
No increase in grinding temperature was observed.

(Embodiment 5) Using a mechanical pulverizer 30 having the structure shown in FIG. 2, pulverization was carried out under the following conditions using a single-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 240 mm.
The distance between the rotor 16 and the liner 18 was 2 mm. A suction blower was connected to the product discharge port 22 of the mechanical crusher 30 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 suction blower was operated at an air flow rate of 4 m ³ / min, and the rotational speed of the rotor 16 was adjusted so that the pulverized product had a particle size of 12 μm at a throughput of the raw material toner (supply rate of 20 kg / h).

(Comparative Example 4) As Comparative Example 4, a test was also conducted under the same operating conditions with the rotor 16 having the groove inclination angle of the outer peripheral surface of 0 degree, that is, the 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 rotation 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 inclination angle is 0 degree, the rotor speed is 11,000 rpm.
When the tilt angle is 5 degrees, the rotor speed is 10,500rp
When the tilt angle was 10 degrees and 20 degrees, the rotor speed was adjusted to 10,000 rpm, and when the tilt angle was 45 degrees, the rotor speed was adjusted to 9,800 rpm. FIG. 11 shows the result 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. FIG. 12 shows the result of plotting the relationship between the volume ratio of so-called over-milled particles of 8 μm or less contained in the crushed product and the inclination angle of the rotor groove.

As is apparent from FIGS. 11 and 12, when the crushing is performed by the mechanical crushing device of the present invention example 5, the outer peripheral surface of the rotor 16 is smaller than that when crushing 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 a mechanical crusher 30 having a structure shown in FIG. 2, a test was conducted using a single-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 32 are formed in a direction parallel to the rotation axis direction of the rotor 16, the groove pitch is 4 mm, the groove depth is 2 mm, and the angle α in FIG. 5C is 45 degrees. , 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 2
A groove having a diameter of 40 mm, which is inclined by 10 degrees in the 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, and has a cross section perpendicular to the direction in which the groove is cut. The shape is such that the angle δ in FIG. 5D is 45 degrees and the angle γ is 15 degrees.
34d is 1.4mm, groove pitch is 4mm, groove depth is 2
mm. The gap 28 between the liner 18 and the rotor 16 was 2 mm.

With this device 30, the number of rotations of the rotor is 10,000.
rpm, suction blower air volume 4 m ³ / min, feed rate 1
The raw material powder was pulverized at a target average particle diameter of 12 μm at 0 kg / h. However, the crushed material 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 obtained pulverized product had an average particle size of 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. 5 (b) is 60 ° and the angle β is 15 °. 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 perpendicular to the direction in which the groove is cut is as shown in FIG. 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.

Although the mechanical crushing apparatus of the present invention has been described in detail above, the present invention is not limited to the above-mentioned embodiment,
Of course, various improvements and modifications may be made without departing from the spirit of the present invention.

[0057]

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 contain 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 a gentle crushing condition, 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. Further, according to the present invention, since the volume of the crushing chamber can be increased, the processing amount can be increased. 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.

5A 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, taken along the line VV in FIG. 1. FIG. , (B) and (c) are partial cross-sectional views showing an example of the cross-sectional shape of the groove of the liner shown in (a) orthogonal to the groove direction, and (d) and (e) are respectively (a) FIG. 4A is a partial cross-sectional view showing an example of a cross-sectional shape of the groove of the rotor shown in FIG. 7B, which is orthogonal to the groove direction, and FIG. 6F is a schematic view 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.

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 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.

FIG. 13 is a schematic cross-sectional view of a conventional rotary mechanical crushing device.

14 (a), (b), (c) and (d) are partial cross-sectional views showing different structures of a rotor and a casing in the conventional crushing device shown in FIG. 13, respectively.

15 (a) and 15 (b) are partial cross-sectional views showing still another structure of the rotor and the casing in the conventional crushing device shown in FIG. 13, respectively.

[Explanation of symbols]

 10, 30 Mechanical crushing device 11 Casing 12 Rotating shaft 14 Rotor unit 16 Rotor 18 Liner 20 Raw material supply port 22 Product discharge port 24a, 24b Bearings 26a, 26b Side plate 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 portion of inclined groove 32S, 34S Main vortex α, β, γ, δ Cross sectional inclination angle of inclined groove a Direction of air flow (direction parallel to rotation axis) ) B Rotating direction of rotor c Moving direction of crushed particles (object to be crushed)

Front Page Continuation (72) Inventor Hideo Okabe 3-5-36 Miyahara, Yodogawa-ku, Osaka-shi, Osaka Shin-Osaka No. 2 Mori Building Nisshin Engineering Co., Ltd. Osaka Sales Office

Claims (8)

[Claims] 1. A rotor supported by a rotary shaft and having a plurality of grooves formed on an outer peripheral surface thereof, and an outer peripheral surface of the rotor which is fitted to the outer peripheral surface of the rotor so as to have a desired clearance. A mechanical crushing device comprising: a liner having a plurality of grooves formed on a surface thereof and crushing an object to be crushed in the gap, wherein the groove of at least one of the rotor and the liner is parallel to the rotation axis. The mechanical crushing device is characterized in that it is inclined in a direction that hinders the flow of the object to be crushed with respect to various directions. 2. The liner according to claim 1, further comprising a groove formed on an inner peripheral surface of the liner, the groove being inclined with respect to a direction parallel to the rotation axis in a direction opposite to a direction in which the flow of the material to be ground is impeded. Mechanical grinding device. 3. The rotor further has a groove on its outer peripheral surface, which is inclined in a direction opposite to the direction in which the flow of the material to be ground is impeded with respect to the direction parallel to the rotation axis.
The mechanical crushing device according to. 4. An inclination angle of one of the groove of the rotor and the groove of the liner with respect to a direction parallel to the rotation axis is 5 degrees or more and less than 90 degrees.
The mechanical crushing device according to. 5. The groove of the rotor has both a direction that impedes the flow of the material to be ground with respect to a direction parallel to the rotation axis and a groove that is inclined in the opposite direction, and the inclination angle is 5 The mechanical crushing device according to claim 1, wherein the mechanical crushing device has an angle of not less than 45 degrees and not more than 45 degrees. 6. The cross-sectional shape of the groove in a direction perpendicular to the direction of the groove of the rotor is such that the surface on the front side with respect to the rotation direction of the rotor is in a direction opposite to the rotation direction of the rotor with respect to the radial direction of the rotor. Inclined at an angle within the range of 30 degrees to 30 degrees in the rotation direction of the rotor, and the rear surface with respect to the rotation direction of the rotor is in a direction opposite to the rotation direction of the rotor with respect to the radial direction of the rotor. The mechanical crushing device according to any one of claims 1 to 5, which is inclined at an angle within the range of 30 to 70 degrees. 7. The liner groove has a groove inclined in a direction parallel to the rotational axis of the rotor in a direction of impeding the flow of the material to be ground, and a groove inclined in the opposite direction thereof. The mechanical crushing device according to any one of claims 1 to 6, wherein the inclination angle is 5 to 45 degrees. 8. The cross-sectional shape of the groove in a direction perpendicular to the direction of the groove of the liner is such that the surface on the front side with respect to the rotation direction of the rotor is from 30 degrees in the rotation direction of the rotor with respect to the center direction of the rotor. The rear surface with respect to the rotation direction of the rotor is inclined at an angle within the range of up to 70 degrees, and the rear surface with respect to the center direction of the rotor is from 30 degrees in the direction opposite to the rotation direction of the rotor to 30 in the rotation direction of the rotor. The mechanical crushing device according to any one of claims 1 to 7, which is inclined at an angle within a range of up to degrees.