LT3563B - A crushing apparatus for frangible or friable material - Google Patents

Abstract

The device is designed for crushing fragile and frangible materials in rotary motion. The device comprises the following elements: a bin 13 for crushing material and a chamber 15. The chamber base includes a central discharge vent 27. The gape 27 is mounted in the discharge vent 27. A rotational crushing cap 17 is mounted in the centre of the chamber 27 so there is an opening between the gape 38 and the cap, and the opening provides a ring gap for crushing. The crushing cap can rotate and swing around the centre 3. The swinging movement is triggered by special equipment through the spindle 43.The device is constructed in order to pull out the material from the bin through the vent 41 by the rotating cap 17.

Description

The device is intended for crushing fragile and friable materials and belongs to the rotary device type.

Shredders for crushing fragile and friable materials have a rotating shredding mechanism (gyroscope). A typical rotary shredder consists of a conical rotating member rotating about a central axis of the conical chamber. An annular gap is formed between the chamber and the rotating member. The pivoting member is pivoted about the vertical axis of the camera but does not pivot about its native pivot axis [US 2901189; TPI B02C 2/04 (August 25, 59); FR 1411834; TPI B02C 2/04 (24. 12. 65)]. These shredders were inefficient.

To overcome this disadvantage, crushing equipment having a geometric intersection of the inner and outer cones above the inner cone [SU 425642; TPI B02C 2/04 (07.01.83)]. This means that the rotation is practically horizontal, resulting in a relatively small gap on one side between the rotating cone and the chamber wall and a large gap on the opposite side. This results in very different material shredding. If the particle size required is of a certain size, up to 40% of them are repeatedly crushed. This causes the shredder to last longer, which means that it crumbles faster.

A device has been developed in which, in an eccentric mechanism, a central bushing has a spherical surface interacting with the same surface in a crushing cone [SU 986488; TPI B02C 2/04 (07.01.83)]. Although the design of this unit was simpler than previous counterparts and allowed to reduce operating costs, wear and power costs remained high.

The closest technical solution to the present invention is the Device described in [SU 1061837; TPI B02C 2/04 {23.

12. 83)]. The machine has a fixedly mounted outer cone, a shaft consisting of a lower vertical and an upper oblique portion whose geometric axes intersect, a crushing cone mounted on the upper part of the shaft, forming a crushing chamber between these cones. In the longitudinal section, the cone surfaces form evenly extending lines both upwards and downwards from the horizontal plane of minimum eccentricity, and, below the minimum eccentricity, the constituent cones are hyperbole.

This cone design reduces the slip of the crushing material on the grinding surface, resulting in less cone wear and increased machine performance.

However, the inner cone-turning elements of the lower part of the violin are complex and precise construction, which is very expensive to replace, not only because of the cost of the elements themselves, but also due to the downtime of the violin and the need for highly qualified technicians.

The object of the present invention is to create a crusher of the kind used up to the present type. This type of shredder must have a more efficient shredding process and lower maintenance and repair costs for the shredder.

rotary motion

Such a device for crushing fragile and friable materials has the following parts:

- a hopper with a camera for loading materials. The base of the hopper has a discharge opening which forms the outline of a mouth having a enveloping or peripheral wall;

in the center of the discharge opening, the mouth of the mouth is rotatable and oscillating, e is a rotation c;

rotary head with a built-in distance from the head to the annular slot. That the head remains at the center point of the opening at all times;

- rotating and providing mechanism.

fluctuating with movement with 10 The material in the hopper is crushed by moving the head relative to the mouth of the mouth. When the opposite sides of the head interact with the envelope, a defined gap is maintained throughout the head swing cycle.

As used herein, the pivot axis refers to the axis with respect to which the pivoting head is symmetrical, and the pivot angle is the angle between the pivot axis of the hopper and the center axis.

It is best to have a shaft in the center of the shredder chamber which rotates about a central axis and whose axial end is internally connected to the head at a fixed angle to allow relative rotation of the head and the shaft.

The fixed angle is best set with a pivot pin inserted between the shaft and the head. In addition, the pin coincides with the axis of rotation of the head, allowing for relative rotation of the head relative to the shaft.

The invention will be explained in the following preferred embodiments. The following variants are shown in the drawings:

1. - schematic side view of the shredder; the principle of rotation of the shredder is shown;

4 2. FIG. - top view; area of vomit; shown on shredder end- 3. FIG. - shredder first or when cutting; 4. FIG. - the second of the shredder variant cut .ir

5. - disassembled shaft view: pivot pin, head and shredder for first version cam i.s.

For the sake of illustration, the head rotation angle is increased in the drawings (FIG. 1 in particular), but in fact the rotation angle is much steeper than the one shown in the drawings. It is apparent from the description of the invention that this angle can also be obtuse.

Both variants have a swivel-type mechanism for breaking and breaking materials. Figure 1 shows the concept of creating a rotary shredder 11. The shredder 11 comprises a hopper 13, a shredder head 17 and a drive 'and support blocks disposed on opposite sides of the head. In addition, the drive and support units have a cam 19 mounted at the base of the hopper 13 and a shaft 21 located above the grinding head 17, as well as a pivot pin 23 mounted between the shaft 21 and the grinding head 17.

The hopper 13 has an inner conical chamber 15 (Fig. 2) having a round hole 25 at the top, through which the material entering the chamber 15 is crushed between the crushing head and the hopper walls 37 and 39. The hopper 13 has a discharge opening 27 shredded material. The discharge opening 27 forms the contour of the mouth 38 with the enveloping conical wall 39. The chamber 15 is generally symmetrical with respect to the axis AC and may be made with a conical cone wall 24 having a conicity opposite to the mouth wall 39. Thus, the wall 24 narrows inwardly with respect to the opening 25 toward the hopper discharge opening. . The purpose is to connect to the mouth. The enclosure wall 39 generally widens outwardly from the chamber 15 toward the base of the hopper 13. Thus, the joining points of the walls 24 and 39 may form a circular contour 29 inside the hopper, although it is not necessary for any particular shape or contour of the hopper to form a compression gap.

The cam 19 is fixedly mounted in the center of the hopper discharge opening 27 and generally has a semi-spherical surface 31 facing the interior of the chamber 15. .The semi-spherical surface 31 forms a bearing or space for mounting the head 17 and defining the contour of the universal swivel joint. The contour allows the head to rotate or oscillate on the cam surface about a point of rotation B that coincides with the center axis AC of the chamber 15.

The grinding head 17 is generally in the form of a cut cone. Its tops 33 are made flat and circular with a diameter slightly smaller than the circumferential compression contour 29. The lower surface 35 of the cone of the grinding head 17 is parallel to the surface 33 and is also flat and circular with a diameter larger than the compression contour 29. 35 an intervening conical grinding surface 37. The center 35 of the surface 17 of the head 17 has a recess which acts in interaction with the surface 31 of the cam 18 to act as a bearing surface and a bearing. As a rule, the interaction of this recess with the hemispherical cam surface may rotate about point B. The cam 19 and the head 17 must be of very precise configuration so that the head fits within the discharge area 27 and the chopping surface 3 ' ^{7 is positioned at} a certain distance from wall 39 and mouth. 38, thereby forming an annular compression gap 41 between the wall 39 and the head crushing surface 37. Consequently, the diameter of the head 17 below the surface 35 will be less than the maximum diameter of the discharge port 27, thereby axially sliding the hopper relative to the head and cam. sliding the cam with the cam in the same direction relative to the hopper will adjust the size of the gap between the chopping surface 37 and the wall 39. The top surface 33 of the head has a circular recess 49 whose axis is perpendicular to the surface 33 and coincides with the axis of rotation of the head. One end of the pin 23 connecting the head 17 and the shaft 21 is inserted into the recess 49.

The shaft 21 is mounted to a roller 43 on the upper part of the hopper which rotates the shaft about the central axis AC of the chamber 15. The surface of the shaft axial end 47 is inclined relative to the right portion of the shaft.

In the first embodiment of the invention, the shaft axial end 47 has a circular recess 51 on the surface of the shaft 17. The central axis of the recess 51 is perpendicular to the end surface and offset at a certain distance from the shaft central axis.

AC. The recess 51 is for mounting the second end of the pin 23; thus connecting the shaft to the head.

The pivot pin 23 has a regular cylindrical shape, so that both of its working ends, which can pivot both spindle and head, are mounted in recesses 49 and 51 to position the head 17 at a certain angle with respect to the axis AC while allowing relative movement between head and spindle. would be the rotation of the head relative to the central axis AC of the chopping chamber 15. Consequently, the central axes of the recesses 49 and 51 and the pin 23 coincide with the axis of rotation GB of the head 17.

The axial length of the pin 23 may be greater than the total depths of the recesses 49 and 51 so as to provide a certain distance between the lower surfaces 47 and the upper surface 33 and to interact only with the working surfaces of the shaft and head. The rear surface 47 and the upper surface 33 are sealed (not shown in the drawing) to prevent dusting of chipping material into the plug and recess area. In other embodiments of the invention, not shown in the drawing, the distance between surfaces 47 and 33 can be formed in other ways, for example by opposing the inner and outer rings of a tapered cylindrical bearing.

During the operation of the crusher, the hydromotor (not shown in the drawings) directly rotates the rotor 43, which rotates the shaft 21 about the central axis AC of the chamber. As the shaft rotates, the shredder head 17 will need to rotate about the rotation point B of the cam 19 at a defined angle relative to the center axis AC of the shredding chamber 15, although in general the shredder head Bunker and shaft may rotate about the axis BG. Because the point B is low relative to the housing and the crushing head due to the specific position and configuration of the compression point 29, the conicity of the mouth wall 39 and the head 37 results in a size H gap 41 throughout the rotation of shaft 43 at the inner periphery very little change occurs and vice versa - the periphery or the circumference of the top surface 33 of the head in close proximity to the bunker narrowing 29 generally changes significantly the size of the gap through the rotation of the same shaft 43. If the shaft rotates about the AC axis, the chopping head is completely unloaded and may rotate relative to the hopper and shaft. However, if the fragile or frangible material loaded into the chamber 15 through the orifice 25 is distributed in the annular slot 41, it will resist rotation of the head relative to the hopper. This means that the spindle 21 will rotate continuously about the axis AC, and the rotating head will rotate sufficiently about point B. The rotating head will rotate about the axis of rotation itself. Its GB axis rotation will be approximately equal to the center axis AC rotation, but there may be slight deviations due to the effect of the friction material between the shear wall and the head shear surface. Therefore, when the head rotates, its outer point-s. H may move in a circular arc either counterclockwise or clockwise relative to a point on the adjacent circular wall 39. '

Thus, upon entering the compression gap 41, the material will stop the rotation of the head 17 and cause the relative rotation of the shaft 21 and the head. Consequently, the head will rotate about the GB axis and oscillate around the cam point B. This oscillation will eventually result in a point on the surface of the head that will alternate in the vertical plane of the arc passing through point B. Consequently, the material within the compression slot 41 will always be affected by the oscillatory or vertical oscillation movement of the crushing head or any combination thereof. This type of crushing action effectively distributes the crushing forces in the compression slot, reducing the impact on the material and continuously compressing it in the convergence of the opposite bands.

Although not shown in the drawings, it is due to this oscillation, rather than rotation of the head, that the various parts of the surface of the crushing head alternate between maximum and minimum compression cracks in the compression area. However, the interacting portions of the crushing head surface are obliquely disposed on opposite sides of the head so that, when inclined to one side (see Fig. 1), its surface points F and H provide a minimum compression region gap. At the same time, the opposite points F and I will form a maximum compression gap. However, regardless of the position of the chopping head, there will be maximum cracks on one side and minimal cracks on the other. Although Figs. this aspect of the invention is not illustrated with sufficient clarity, since the crushing head is enlarged, but is well illustrated in the description of the other embodiments. It should be noted that if one part of the compression region, either at the top or at the bottom of the head, changes the size of the gap from a minimum to a maximum, a completely different situation occurs on the other side of the head. whereas on the opposite side, the pulp is crushed until the crack is completely reduced. For example, if there is a maximum compression crack at the top of the head and a minimum crush at the bottom of the head, the material will fall into the V-shaped recess. But as the size of the compression slit changes, the shape gradually begins to change until finally a minimum slit appears at the top of the head and a maximum slit at the bottom. This means that the material in the maximum slit will gradually be crushed and the minimum slit pressed less and more through the discharge opening. In this way, after repeated oscillations, the material passes through the compression gap. This means that in this case, the shredding process is more efficient, since more material is shredded, but with lower throughput.

This variant is advantageous in that there is little difference between the maximum and minimum particle size of the crushing material by maintaining consistent fluctuations of the upper and lower surfaces of the crushing head at any point of maximum or minimum compression and is dependent on the gap in compression region 41. This allows the particle size of the crushed material to be accurately determined and completely eliminated from re-crushing, or re-crushing very little material. The slit size is very easy to adjust axially by raising or lowering the cam 19 in the hopper or vice versa by raising the hopper relative to the cam. In this way, the size of the compression gap can be adjusted to compensate for wear on the surface 37 or the semi-spherical surface 31 of the crushing head.

Figure 3 illustrates the first version of the shredder, which is closely related to the conceptual interpretation of the shredder. Therefore, the relevant blocks ... and elements are denoted by the same numerals as interpreted by the conceptual design of the shredder.

The first embodiment of the invention is slightly different from the conceptual one.

The hopper 13 has a segmental construction, the inner portion 13a of which is mounted in the outer frame 13b and is adjustable. The frame 13a has a base 13a and an upper portion 13d which protrudes above the opening 25 to form a strong bearing support for mounting the shaft 21. A simple safety mechanism (not shown in the drawing) is used to prevent non-crumbling material caught between the head 17 and the mouth 38.

Figure 4 shows a second version of the shredder, which is significantly different from the first, but based on the conceptual variant already described. Therefore, in this example, the respective blocks are denoted by the same numerals as in the conceptual embodiment of the invention.

The second variant differs from the first in that the upper part 13d of the frame is extended over the crusher opening 25 to form a double support for mounting the shaft 21. Thus, in this embodiment, a shaft 21 of a different design can be used, so that the spinner 43 can be substantially extended to form the outer bearing neck 3563 B hatch 53 in the inner frame portion 13d, the diametrically extended outer portion 55, and the inner neck 57 in the diametrically extended frame portion 59. the rotor 43 is tapered symmetrically from the main axial end 47. The axial end 47 is provided with a transverse 61, the plenum surface of which, as in the previous embodiment, is inclined obliquely with respect to the center axis of the chamber and the outer surface of the shaft 33. There is no round recess on the outer surface 63 of the transverse 61, the transverse being formed with the pivot pin 23 so that the central pin increases to the outside by resizing it to the required center axis of the shaft. As in the previous embodiment, the pivot pin 23 is mounted so that it can be pivoted in the recess 49 made in the flat surface 33 of the grinding head. Thus, as in the previous embodiment, the shaft pivots to give the head both rotatable and oscillatory motion.

In one embodiment of the present invention, the pin 23 may be formed with the head 17 and mounted so as to pivot in the recess 31 on the outer flat surface 63 of the shaft.

In one of the modifications of the previous embodiments, the surface of the grinding head 17 may be of any shape other than a cut cone. Consequently, in order to reduce the gap between the crushing surfaces of the head 37 and the hopper 39 from the constriction point 9 to the crusher outlet 39

Still another aspect of the present invention with respect to vn 17 may be as shown in the drawings.

openings 27, enveloping rmos and should be.

iante the position of point B above or below

Alternatively, a bearing bearing is provided between the upper head surface 33 and the lower shaft surface 47.

The advantages of this design compared to the ones used so far are:

1. Because such shredders are simple in design and have fewer components, the production is very cheap. For example, known shredders have at least 30 main parts, whereas in a typical embodiment of the present invention there will be only eight.

2. Knives of known construction have 14 or more moving parts, and in the typical embodiment of the present invention there are only three.

3. New construction shredders require much less spare parts, less maintenance and repairs.

4. Shredders of this design are suitable for simple hydraulic drive, whereas existing shredders require the use of electric motors and gearboxes.

5. The simplicity of the shredder parts does not cause lubrication problems, while the existing shredders are quite difficult to lubricate.

6. A significant reduction in the shredder's yield time will result in much less time for maintenance.

7. Because of the higher quality of the machinery, the shredder consumes far less energy than other shredders of the type in question, which have only 65% efficiency.

8. The shredder efficiency of this design can actually reach 100%, with only a small amount of material being needed for re-shredding, while other shredders require up to 60% re-shredding.

9. Shredder material of this design can be shredded to a size smaller than 1/16 inch, eliminating the need for re-shredding, while known shredders make it difficult to shred to 3/16 inch (40% and more of the shredded material must be re-shredded).

10. Compared to existing shredder designs, the working mechanism of the new shredder has a smaller centrifugal balance (depending on the shaft design, it may not exist at all). Consequently, abrasion, energy consumption and balance are minimized, making it possible to produce large-size shredders that were not possible before.

± 1. Due to the simplicity of construction and the small number of parts, these shredders can be made small, suitable for individual transport and used for small jobs. Existing transportable shredders are very expensive and bulky and require special heavy duty transport.

You only need.% Ki ritu ¹ small. n emphasize that the invention embrace.

.io description variant. New i

- can be used not only when. i, but also in other industries: Ksmo does not limit the component here, nor is it limited to the manufacture of fine ore, since smui Χίο lis.

Claims (13)

DEFINITION OF INVENTION 1. A device for crushing fragile and friable material consisting of a hopper having a chamber for loading material and a central discharge opening, which, in addition, forms the outline of a mouth with a circumference, a rotary shred head located at a certain distance from the mouth. walls to form an annular compression gap between it and the outer surface of the head, chopping heads supported around the pivot point to rotate! both oscillating and oscillating devices, characterized in that the material in the hopper is crushed as the head moves relative to the wall, and in that the head is mounted such that its opposite sides interact with the wall, thereby maintaining a compression gap throughout the head oscillation cycle . 2. A device according to claim 1, characterized in that said devices comprise a pivot shaft which is mounted in the center of the chamber and pivoting about a central axis, the axial end of which is inside the chamber and coupled to the front axial end of the head. relative to the axis and rotating the shaft, relative movement occurs between it and the head. 3. A device according to claim 2, characterized in that the fixed angle is fixed by a pin which is inserted between the head and the shaft and whose central axis coincides with the axis of rotation of the head and thus allows for relative movement between the head and the shaft. 4. Device according to claim 3, characterized in that the position of the pin angle is fixed by the axial end of the same pin which is connected to the axial end of the displaced shaft and is inclined obliquely with respect to the central axis of the shaft. be engaged with the axial end of the head in such a position that it coincides with the axis of rotation of the head and that the axis of the pin coincides with the axis of rotation of the head. 5. A device as claimed in claim 4, characterized in that the pin is cylindrical in shape with its axial ends forming outwardly projecting support portions which are inserted into recesses in the respective projections of the shaft and the head for fixing the head and the pin at a predetermined angle. 6. A device according to claim 5, characterized in that the length of the pin for the required distance between the respective axial ends of the head and the shaft can be greater than the sum of the recess depths. 7. A device according to claim 6, characterized in that a seal is provided between the respective axial ends of the head and the shaft, impervious to the particles of material in the hopper. 8. Device according to one of claims 1 to 7, characterized in that, with respect to the hopper, the crushing head is supported by a universal pivoting joint allowing the head to rotate and rotate about a pivot point, furthermore, having a pair of mutually selectable components .. in the center of the floor outlet, and the other at the axial end of the trough. 9. A device according to claim 8, wherein one component has a cam having a fixed base and the other component having a recess in the center of the rear axial end, the cam having a hemispherical face facing the chamber and the recess having an additional hemispherical working surface. , into which the cam forms a support surface or socket in which the head can rotate and oscillate freely. 10. A device according to claims 8 and 9, characterized in that one of its components is axially adjustable relative to the hopper, which allows to adjust the annular compression gap. Device according to one of Claims 1 to 10, characterized in that the chopping head has the shape of a regular cut cone. the anterior and posterior axial ends form an outline of parallel circular surfaces, with a circular conical surface between them, the anterior conical surface being slightly smaller in diameter than the posterior surface, resulting in an annular compression gap when the conical surface interacts with the mouth. must be smooth. 12. A device as claimed in any of claims 1-11, wherein the chamber has a loading aperture and an enveloping surface which engages in and toward the discharge opening, and the mouth of the mouth extends outwardly from the chamber towards the hopper and discharge, a round narrowing contour is formed at the junction of the opening. Device according to any one of claims 1 to 12, characterized in that it comprises a shaft which is driven by a mechanical or electric drive.