Crushing mechanism of crusher and its grinding disc device

Abstract

The present invention provides a grinding disc device for a crusher, which includes a hammer disc and a plurality of hammer heads arranged at intervals on the hammer disc along the rotation direction of the hammer disc. The hammer disc has opposite first end face and second end face and a side face located between the first end face and the second end face; the hammer heads are assembled and connected with the hammer disc, the hammer heads are in covering fit with the first end face of the hammer disc, and the end of the hammer head protrudes outwards from the side face of the hammer disc to form an outwardly convex striking part, and the outwardly convex striking part further extends along the axial direction of the hammer disc to form a covering structure at least partially covering the side face of the hammer disc; so as to protect the side face of the hammer disc and further improve the service life of the hammer disc, and reduce the replacement and maintenance costs. In addition, the present invention also discloses a crushing mechanism of a crusher.

Description

Technical Field

[0001] The present invention relates to the field of material crushing equipment, and particularly to a crushing mechanism of a crusher and its grinding disc device. Background Art

[0002] As is well known, in existing crushers, especially ultrafine crushers, they mainly consist of a crushing device, a classification device, and a power device. Among them, the crushing device includes a crushing rotating grinding disc, hammers evenly distributed along the circumference on the crushing rotating grinding disc, and a gear ring surrounding the outer periphery of the crushing rotating grinding disc. An air inlet channel is left between the crushing rotating grinding disc and the gear ring. The crushing rotating grinding disc is driven by a main shaft in the power device to rotate at a high speed; the classification device includes a shunt cover, a classification impeller, a guide cover, and a dust collection housing. The shunt cover is composed of an outer cylinder and an inner cylinder arranged concentrically. A gap is left between the inner cylinder and the outer cylinder. The outer cylinder is axially fixed at the upper end of the gear ring. The guide cover is fixed at the upper end of the outer cylinder. The dust collection housing is arranged above the guide cover. An air flow channel communicating with the internal space of the dust collection housing is provided at the center of the guide cover. The inner top surface of the guide cover is arc-shaped from the outside to the inside. The fan impeller is arranged vertically and axially extends into the inner cylinder. The upper outer edge of the fan impeller matches the air flow channel on the guide cover. Therefore, during operation, air is drawn from the outlet end of the dust collection housing, and at the same time, the crushing rotating grinding disc is driven by the power device to rotate at a high speed, with a maximum linear velocity of up to 120 meters per second. The hammers on the crushing rotating grinding disc crush the material in a high-speed impact manner, and the high-speed rotation of the hammers also throws the material towards the gear ring, using the high-speed air flow to impact the material, causing the material to collide and rub strongly with each other, thereby achieving the purpose of fine crushing; under the action of the wind, the crushed material passes upward through the shunt cover and then moves along the inner wall of the guide cover towards the classification impeller. The material with a qualified crushing particle size passes through the classification impeller and enters the dust collection housing; while the large-particle material falls and re-enters the hammer head for crushing.

[0003] However, in existing crushers, since the hammers are located at the top surface of the crushing rotating grinding disc, the material thrown by the high-speed rotating hammers towards the gear ring not only collides with the gear ring and the hammers but also collides with the side surface of the crushing rotating grinding disc. As described above, the maximum linear velocity of the crushing rotating grinding disc can reach 120 meters per second, which accelerates the wear of the side surface of the crushing rotating grinding disc and shortens the service life of the crushing rotating grinding disc; also, since the crushing particle size of the material is controlled by the distance between the side surface of the crushing rotating grinding disc and the gear ring, the crushing rotating grinding disc needs to be replaced together with the hammers on the crushing rotating grinding disc after a certain degree of wear, thus increasing the replacement and maintenance costs; in addition, after the crushing rotating grinding disc is worn, it directly affects the power consumption of the grinding disc device and correspondingly reduces the production capacity.

[0004] Therefore, there is an urgent need for a crushing mechanism of a crusher and its grinding disc device to overcome one or more of the above defects. Summary of the Invention

[0005] An object of the present invention is to provide a grinding disc device of a crusher for protecting a hammer disc to further improve the service life of the hammer disc.

[0006] Another object of the present invention is to provide a crushing mechanism of a crusher for protecting a hammer disc to further improve the service life of the hammer disc.

[0007] To achieve the above object, the grinding disc device of the crusher of the present invention includes a hammer disc and a plurality of hammer heads arranged at intervals along the rotation direction of the hammer disc on the hammer disc. The hammer disc has opposite first end face and second end face and a side face located between the first end face and the second end face; the hammer head is assembled and connected with the hammer disc, the hammer head and the first end face of the hammer disc are covered and matched, the end of the hammer head protrudes outward from the side face of the hammer disc to form an outward convex striking part, and the outward convex striking part further extends along the axial direction of the hammer disc to form a covering structure that at least partially covers the side face of the hammer disc.

[0008] Optionally, the outer side face of the outward convex striking part and the outer side face of the covering structure that is opposite to the side face of the hammer disc are flush with each other and are each a rotating surface, and the rotating center line of the rotating surface and the hammer disc coincides.

[0009] Optionally, the inner side face of the covering structure that faces the side face of the hammer disc is a rotating surface or a plane, the rotating center line of the rotating surface and the hammer disc coincides, and the plane is tangent to the side face of the hammer disc; the end of the covering structure extending axially extends beyond the second end face or is flush with the second end face.

[0010] Optionally, the outward convex striking part and the covering structure each extend along the rotation direction of the hammer disc and / or the direction opposite to the rotation direction to further cover the side face of the hammer disc.

[0011] Optionally, the assembly connection between the hammer head and the hammer disc is a replaceable assembly connection and / or the hammer heads are arranged radially around the rotation center line of the hammer disc.

[0012] Optionally, a surfacing structure layer is surfacing-welded on the end face of the hammer disc, the surfacing structure layer completely or partially covers the end face of the hammer disc, and the surfacing structure layer is located between the hammer head and the first end face of the hammer disc.

[0013] Optionally, among all the hammer heads, the covering parts of some hammer heads that are covered and matched with the first end face of the hammer disc are each spliced with a splicing module in a direction close to the rotation center line of the hammer disc, the splicing module is covered and matched with the first end face of the hammer disc, and there is a gap of 1 to 3 hammer heads between adjacent two splicing modules along the rotation direction of the hammer disc.

[0014] Optionally, the splicing module is composed of one or more splicing blocks and / or the hammer head is made of cemented carbide.

[0015] To achieve the above object, the crushing mechanism of the crusher of the present invention includes a gear ring and the aforementioned grinding disc device. The gear ring is coaxially arranged with the hammer disc, and the gear ring also surrounds the grinding disc device.

[0016] Optionally, alloy rods or alloy coating layers are provided in the tooth grooves of the gear ring, and the hardness of the alloy rods or alloy coating layers is greater than the hardness of the gear ring.

[0017] Compared with the prior art, since the end of the hammer head protrudes outward from the side surface of the hammer disc to form an outwardly convex striking part, and the outwardly convex striking part also extends along the axial direction of the hammer disc to form a covering structure that at least partially covers the side surface of the hammer disc, the crushing particle size of the material is controlled by the distance between the outer side surface of the hammer head on the hammer disc and the gear ring, rather than by the distance between the side surface of the hammer disc and the gear ring. At the same time, since the side surface of the hammer disc is covered by the covering structures of a plurality of hammer heads arranged separately on the hammer disc along the rotation direction of the hammer disc, the exposed area of the side surface of the hammer disc relative to the gear ring can be reduced, thus playing a role in protecting the hammer disc, and further improving the service life of the hammer disc. Moreover, since the crushing particle size of the material is controlled by the distance between the outer side surface of the hammer head on the hammer disc and the gear ring, rather than by the distance between the side surface of the hammer disc and the gear ring, even if the side surface of the hammer head wears, it will not affect the crushing particle size of the material. Therefore, the crusher including the grinding disc device of the present invention can still operate efficiently when the outer side surface of the hammer head wears little, and only needs to replace the hammer head when the hammer head wears, thus relatively reducing the replacement and maintenance costs compared with the prior art. BRIEF DESCRIPTION OF THE DRAWINGS

[0018] Figure 1 is a plan view of the crushing mechanism of the first embodiment of the present invention viewed from top to bottom.

[0019] Figure 2 is a plan view of the crushing mechanism of the first embodiment of the present invention viewed from bottom to top.

[0020] Figure 3 is Figure 1 a three-dimensional view of the crushing mechanism shown when only one gear ring block is retained in the gear ring.

[0021] Figure 4 is Figure 3 a three-dimensional view after hiding the gear ring block.

[0022] Figure 5 is Figure 1 a plan view of the gear ring in the crushing mechanism shown.

[0023] Figure 6 isFigure 5 The plan view of a segment of the gear ring shown.

[0024] Figure 7 is a Figure 6 plan view of a deformation of the gear ring segment shown.

[0025] Figure 8 is a Figure 6 plan view of another deformation of the gear ring segment shown.

[0026] Figure 9 is a Figure 6 plan view of yet another deformation of the gear ring segment shown.

[0027] Figure 10 is a cross-sectional view of the grinding disc device after being cut along the B-B line in Figure 1 .

[0028] Figure 11 is the plan view of the hammer disc in the crushing mechanism of the first embodiment of the present invention viewed from top to bottom.

[0029] Figure 12 is a Figure 11 internal view after being cut along the D-D line.

[0030] Figure 13 is the perspective view of the hammer head in the crushing mechanism of the first embodiment of the present invention at an angle.

[0031] Figure 14 is a Figure 13 perspective view of the hammer head shown at another angle.

[0032] Figure 15 is the plan view of the crushing mechanism of the second embodiment of the present invention viewed from top to bottom.

[0033] Figure 16 is the plan view of the crushing mechanism of the third embodiment of the present invention viewed from top to bottom. Detailed implementation manners

[0034] In order to elaborate in detail on the technical content and structural features of the present invention, the following further explanations are provided in conjunction with the implementation manners and accompanied by the drawings.

[0035] Please refer to Figures 1 to 3 , the crushing mechanism 100 of the first embodiment of the present invention includes a grinding disc device 10 and a gear ring 20. The gear ring 20 is coaxially arranged with the hammer disc 11 in the grinding disc device 10 so that the center lines of the gear ring 20 and the hammer disc 11 coincide with each other. See Figure 1 and Figure 2As indicated by the label C therein, this effectively reduces the radial runout of the hammer disc 11 relative to the gear ring 20 during high-speed rotation, thus effectively ensuring the consistency of the crushing particle size of the material. At the same time, the gear ring 20 also surrounds the grinding disc device 10, as shown in Figure 1 and Figure 2 shown. During the high-speed rotation of the hammer disc 11, the hammer head 12 driven by the hammer disc 11 crushes the material in a high-speed impact manner, and the high-speed rotating hammer head 12 also throws the material towards the gear ring 20 in a centrifugal manner. The material thrown towards the gear ring 20 is further crushed by the outward convex striking part 12a, the covering structure 12b and the gear ring 20 described below, finally achieving the purpose of fine crushing. Furthermore, alloy rods 30 with a circular cross-sectional profile are provided in the tooth grooves 21 of the gear ring 20. The alloy rods 30 are welded and fixed to the gear ring 20, and the alloy rods 30 also extend along the axial direction of the gear ring 20. The hardness of the alloy rods 30 is greater than that of the gear ring 20. By introducing the alloy rods 30, on the one hand, the contact surface between the gear ring 20 and the material is retained, and on the other hand, the wear resistance effect of the gear ring 20 is improved, thereby increasing the service life of the gear ring 20. More specifically, as follows:

[0036] In Figure 1 , Figure 2 , Figure 3 and Figure 5 as an example, the gear ring 20 is formed by splicing nine circular arc-shaped gear ring blocks 20a end to end along the circumference of the gear ring 20. This design has the advantages of easy manufacturing and low cost compared with the integral gear ring 20. Of course, according to actual needs, the gear ring 20 can also be formed by splicing other numbers of gear ring blocks 20a end to end along the circumference of the gear ring 20, so it is not limited to Figure 5 shown.

[0037] In Figure 1 , Figure 2 , Figure 5 and Figure 6 as an example, each tooth groove 21 of the gear ring 20 is provided with an alloy rod 30, so that there is an alloy rod 30 in each tooth groove 21. Of course, according to actual needs, alloy rods 30 can also be provided in some tooth grooves 21 of the gear ring 20, while the remaining tooth grooves 21 are not provided with alloy rods 30. The specific arrangement can be: there are one to three empty tooth grooves 21 separated between two adjacent alloy rods 30, so it is not limited to Figure 1 , Figure 2 , Figure 5 and Figure 6 shown. Additionally, in Figure 3 as an example, both axial ends of the alloy rod 30 are flush with the gear ring 20. Of course, according to actual needs, both axial ends of the alloy rod 30 can also be retracted into the gear ring 20, so it is not limited to Figure 3 shown. Specifically, in Figure 6Among them, as an example, the alloy rod 30 protrudes slightly inward along the radial direction of the gear ring 20 beyond the tooth 22; of course, according to actual needs, the alloy rod 30 can also be flush with the tooth 22, so it is not limited Figure 6 as shown. It should be noted that although Figure 6 the tooth 22 shown is a straight tooth extending along the axial direction of the gear ring 20, however, according to actual needs, the tooth 22 can also be an inclined tooth extending obliquely relative to the axial direction of the gear ring 20, so it is not limited Figure 6 as shown.

[0038] Please refer to Figure 7 、 Figure 8 and Figure 9 which are respectively deformations of Figure 6 . Specifically, in Figure 7 , as an example, the cross-sectional profile of the alloy rod 30' provided in the tooth groove 21 of the gear ring 20 is an ellipse; in Figure 8 , as an example, the cross-sectional profile of the alloy rod 30'' provided in the tooth groove 21 of the gear ring 20 is an equilateral triangle; therefore, the cross-sectional profiles of the aforementioned alloy rods 30 (30', 30'') can be designed as circles, ellipses or regular polygons, etc.; and in Figure 9 , as an example, an alloy coating 40 is provided in the tooth groove 21 of the gear ring 20, and the alloy coating 40 is welded to the gear ring 20. The hardness of the alloy coating 40 is greater than that of the gear ring 20, so as to cover the entire surface of the tooth groove 21 of the gear ring 20 with the alloy coating 40, which can also be understood as covering all the teeth 22, thereby protecting the entire gear ring 20 and effectively improving the service life of the gear ring 20. Optionally, the cross-sectional profile of the alloy coating 40 is approximately in the shape of a "V", but not limited thereto. It is supplemented that the cross-sectional profile refers to the profile obtained by intercepting the alloy rod 30 (30', 30'') with a transverse plane perpendicular to the longitudinal direction of the alloy rod 30 (30', 30'').

[0039] In Figure 3 、 Figure 4 、 Figure 10 and Figure 12Among them, as an example, the grinding disc device 10 includes a hammer head 12 and a hammer disc 11. The hammer disc 11 has opposite first end face 111 and second end face 113 and a side face 112 located between the first end face 111 and the second end face 113. A surfacing structure layer 13 is surfacing-welded on the first end face 111, and the surfacing structure layer 13 completely covers the first end face 111 of the hammer disc 11; of course, according to actual needs, the surfacing structure layer 13 can also partially cover the first end face 111 of the hammer disc 11; therefore, during the use of the hammer disc 11, the first end face 111 of the hammer disc 11 is protected by the surfacing structure layer 13; when the surfacing structure layer 13 is worn, at this time, the surfacing structure layer 13 can be surfacing-welded again on the first end face 111 of the hammer disc 11, so there is no need to replace the hammer disc 11, thereby reducing the cost of spare parts by 80%. And there are twelve hammer heads 12, and they are arranged at equal intervals on the hammer disc 11 along the rotation direction of the hammer disc 11 (as shown by the arrow A in Figure 3 and Figure 4 ), of course, according to actual needs, all the hammer heads 12 can also be arranged at unequal intervals on the hammer disc 11, so it is not limited by Figure 3 and Figure 4 shown; at the same time, the hammer head 12 is assembled and connected to the hammer disc 11. As an example, in Figure 10 , Figure 13 and Figure 14 , an installation hole 12c1 is opened on the hammer head 12 along the axial direction of the hammer disc 11 and penetrates through the hammer head 12. By means of a screw passing through the installation hole 12c1 and then assembling and connecting with the hammer disc 11, the hammer head 12 is locked to the hammer disc 11 by the screw, so as to achieve the purpose that the assembly connection between the hammer head 12 and the hammer disc 11 is a replaceable assembly connection. Of course, according to actual needs, there can be other assembly connection methods between the hammer head 12 and the hammer disc 11, so it is not limited to this; furthermore, the hammer head 12 and the first end face 111 of the hammer disc 11 are covered and matched, and the surfacing structure layer 13 is located between the hammer head 12 and the first end face 111 of the hammer disc 11. Such a design increases the contact area of the hammer disc 11 with the hammer head 12 on the one hand, thereby ensuring the assembly connection stability between the hammer disc 11 and the hammer head 12, and reduces the exposed area of the surfacing structure layer 13 on the other hand, correspondingly reducing the wear of the surfacing structure layer 13; in addition, the end of the hammer head 12 protrudes outward from the side face 112 of the hammer disc 11 to form an outward convex striking part 12a, and the outward convex striking part 12a of the hammer head 12 protruding outward from the side face 112 of the hammer disc 11 also extends along the axial direction of the hammer disc 12 (as shown by the arrow beside the hammer disc 11 in Figure 10 ) to form a covering structure 12b that at least partially covers the side face 112 of the hammer disc 11. The covering relationship between the covering structure 12b and the side face 112 of the hammer disc 11 can be seen in Figure 10 shown. Specifically, for the specific structure of the grinding disc device 10, see the following description.

[0040] In Figure 3 , Figure 4, Figure 14 and Figure 15 In Figure 14 and Figure 15 , as an example, the outwardly protruding striking part 12a of the hammer head 12 protruding from the side surface 112 of the hammer disc 11 and the covering structure 12b each protrude from the covering and mating part 12c of the hammer head 12 that covers and mates with the first end surface 111 of the hammer disc 11 along the rotation direction of the hammer disc 11 (as indicated by the arrow A) and the direction opposite to the rotation direction (as indicated by the direction opposite to the arrow A), so that the outwardly protruding striking part 12a and the covering structure 12b protrude from both sides of the covering and mating part 12c, making the hammer head 12 in a "T" shape. In this way, on the one hand, the exposed area of the side surface 112 of the hammer disc 11 can be reduced, and the material usage of the hammer head 12 can be effectively reduced, thereby reducing the manufacturing cost of the hammer head 12. On the other hand, the outer side surface 12a1 of the outwardly protruding striking part 12a and the outer side surface 12b1 of the covering structure 12b can be increased to further improve the crushing efficiency of the material and further cover the side surface 112 of the hammer disc 11. Of course, according to actual needs, the outwardly protruding striking part 12a of the hammer head 12 protruding from the side surface 112 of the hammer disc 11 and the covering structure 12b can be made to protrude from the covering and mating part 12c of the hammer head 12 that covers and mates with the first end surface 111 of the hammer disc 11 along the rotation direction of the hammer disc 11 (as indicated by the arrow A) or the direction opposite to the rotation direction (as indicated by the direction opposite to the arrow A), so that the outwardly protruding striking part 12a and the covering structure 12b protrude from one side of the covering and mating part 12c. Therefore, it is not limited by Figure 1 , Figure 2 , Figure 3 , Figure 4 , Figure 10 , Figure 13 and Figure 14 shown.

[0041] In Figure 10 As an example, the end 12b3 of the covering structure 12b extending axially extends beyond the second end surface 113 of the hammer disc 11. On the one hand, it can more effectively protect the hammer disc 11, and on the other hand, it can increase the crushing contact area with the material. Of course, according to actual needs, the end 12b3 of the covering structure 12b extending axially can also be flush with the second end surface 113 of the hammer disc 11. Therefore, it is not limited by Figure 10 shown.

[0042] In Figure 1 , Figure 3 and Figure 4 As an example, the hammer heads 12 are arranged radially around the rotation center line C of the hammer disc 11, so that each hammer head 12 extends radially along the hammer disc 11, making the assembly of the hammer heads 12 on the hammer disc 11 more reasonable. Of course, according to actual needs, the arrangement of the hammer heads 12 on the hammer disc 11 can also be other forms. Therefore, it is not limited by Figure 1 , Figure 3 and Figure 4 shown. Specifically, inFigure 3 and Figure 4 As an example, among all the hammer heads 12, the covering and mating portions 12c of six hammer heads 12 that cover and mate with the first end face 111 of the hammer disc 11 are each spliced with a splicing module 14 in the direction approaching the rotation center line C of the hammer disc 11. The splicing module 14 covers and mates with the first end face 111 of the hammer disc 11, and the adjacent two splicing modules 14 are separated by 1 hammer head 12 along the rotation direction of the hammer disc 11 (as indicated by the arrow A). That is to say, among the 12 hammer heads 12 shown in Figure 3 and Figure 4 six hammer heads 12 are not spliced with the splicing module 14. The purpose of such a design is to make the hammer heads 12 spliced with the splicing module 14 and the hammer heads 12 not spliced with the splicing module 14 arranged alternately in a long and a short pattern. By matching the hammer heads 12 spliced with the splicing module 14 with the hammer heads 12 not spliced with the splicing module 14, the hammer heads 12 spliced with the splicing module 14 play a crushing role relative to the hammer heads 12 not spliced with the splicing module 14, while the hammer heads 12 not spliced with the splicing module 14 play a shaping role relative to the hammer heads 12 spliced with the splicing module 14, so as to further improve the crushing effect of the material. More specifically, in Figure 3 and Figure 4 as an example, the splicing module 14 is composed of two splicing blocks 141. Of course, the splicing module 14 can also be composed of one or three unequal splicing blocks 141.

[0043] It should be noted that the set number of the splicing blocks 141 is jointly determined by the distance between the rotation center line C of the hammer disc 11 and the hammer head 12 and the length of each splicing block 141. Preferably, the total length of all the splicing blocks 141 when spliced is equal to the distance between the rotation center line C of the hammer disc 11 and the hammer head 12, so as to more effectively control the material falling from the outside to the first end face 111 of the hammer disc 11 to be thrown at high speed to the tooth ring 20. However, since the hammer disc 11 needs to be fixedly installed with the main shaft in the external power device, the total length of all the splicing blocks 141 when spliced can only be as close as possible to the distance between the rotation center line C of the hammer disc 11 and the hammer head 12. In addition, since the hammer head 12 is the part that is easily worn during the operation of the grinding disc device 10, only the hammer head 12 needs to be replaced when it is worn, and there is no need to replace the splicing module 14. Therefore, the cost of the grinding disc device 10 can be further reduced. In addition, according to the combination of the thickness of the feed, 4, 6, 8, 9, 16, 24, etc. hammer heads 12 can be selected on the hammer disc 11 for combined matching. In addition, in Figure 10Among them, as an example, an assembly hole 1411 penetrating axially through the hammer plate 11 is provided on the splicing block 141. By passing a screw through the assembly hole 1411 and then assembling and connecting it with the hammer plate 11, the screw locks the splicing block 141 and the hammer plate 11 together, thus simplifying the detachable assembly connection relationship between the splicing block 141 and the hammer plate 11.

[0044] In Figure 1 , Figure 2 , Figure 3 and Figure 4 Among them, as an example, the outer side surface 12a1 of the outwardly protruding striking portion 12a of the hammer head 12 from the side surface 112 of the hammer plate 11 and the outer side surface 12b1 of the covering structure 12b facing away from the side surface 112 of the hammer plate 11 are flush with each other and are each a rotating surface. This rotating surface coincides with the rotation center line C of the hammer plate 11 and the two, ensuring that the gap sizes at various places between the hammer head 12 and the gear ring 20 are the same, thereby further improving the uniformity of the crushed particle size of the material. In addition, the inner side surface 12b2 of the covering structure 12b facing the side surface 112 of the hammer plate 11 is a plane, and this plane is tangent to the side surface 112 of the hammer plate 11. The state is shown in Figure 2 shown; among them, with the inner side surface 12b2 being a plane, it is convenient for the manufacturing and processing of the hammer head 12 with the covering structure 12b. Of course, according to actual needs, the inner side surface 12b2 of the covering structure 12b facing the side surface 112 of the hammer plate 11 can also be made into a rotating surface. At this time, this rotating surface is made to coincide with the rotation center line C of the hammer plate 11 and the two, so it is not limited to Figure 2 shown.

[0045] Finally, the crushing mechanism 100 of the present invention is made of wear-resistant materials to improve the service life of the crushing mechanism 10 of the present invention from the material aspect; and because the working conditions require that the crushing mechanism 100 of the present invention has a strong pushing ability for the grinding medium (i.e., the material) and also requires that the crushing mechanism 100 of the present invention has good impact resistance, so the considered materials include high-chromium alloy, high-manganese steel, wear-resistant steel, low-carbon alloy steel, tungsten steel, and double-fluid composite materials, etc. And the characteristics of these materials are as follows:

[0046] High-chromium alloy is a wear-resistant material with excellent wear resistance, but its toughness is low and it is prone to brittle fracture.

[0047] High-manganese steel, this type of steel contains 10% to 15% manganese and has a relatively high carbon content, generally 0.90% to 1.50%, and most are above 1.0%. It is often used to make the shovel teeth of excavators, the rolling surface walls and crushing walls of cone crushers, the toggle plates of jaw crushers, the liners of ball mills, railway switches, plate hammers, hammer heads, etc. For example, high-manganese steel ZGMn13 has sufficient impact toughness, but it is not wear-resistant and is prone to deformation.

[0048] In addition to the above materials, there are also NM series such as NM500, NM600, NM700, etc. NM500 is a high-strength wear-resistant steel plate with high wear resistance. Its Brinell hardness value reaches 500 (HBW). It mainly provides protection in occasions or parts that require wear resistance, making the equipment last longer and reducing the maintenance and downtime caused by repairs. Under the same working conditions, NM500 is more wear-resistant than ZGMn13 and has a longer service life.

[0049] The low-carbon alloy steel material has high hardness. It is a high-hardness wear-resistant low-carbon alloy steel plate, which is a plate rolled from a low-carbon iron-based alloy containing alloying elements such as manganese (Mn), silicon (Si), chromium (Cr), molybdenum (Mo), titanium (Ti), and phosphorus (P). Its characteristics lie in the inclusion of alloying elements such as vanadium (V), boron (B), and rare earth (Re), etc. However, the price of the low-carbon alloy steel material is relatively expensive.

[0050] Tungsten steel, also known as cemented carbide, refers to a sintered composite material composed of at least one metal carbide. Tungsten carbide, cobalt carbide, niobium carbide, titanium carbide, and tantalum carbide are common components of tungsten steel.

[0051] The double-fluid composite material adopts different optimized combinations of chromium, molybdenum, copper, nickel, vanadium, titanium, etc. and a rigorous and unique production process, integrating the excellent abrasion resistance, high-temperature oxidation resistance, thermal fatigue resistance (or corrosion resistance) of high-chromium alloy castings with the good toughness and machinability of cast steel, and having excellent wear resistance and overall comprehensive impact resistance that are difficult to achieve by single alloy materials.

[0052] In addition, the price order of each material from low to high is: high-chromium alloy (high manganese steel, wear-resistant steel), wear-resistant surfacing plate, low-carbon alloy steel, and tungsten steel, and the prices of high-chromium alloy, high manganese steel, and wear-resistant steel are the same; combined with the analysis of the processing ease and cost performance of the materials, the material selection for each component of the crushing mechanism 100 of the present invention is as follows: the material of the gear ring 20 is alloy steel, replacing the traditional manganese steel with alloy steel; the materials of the alloy rods 30 (30`, 30``) and the alloy coating 40 are each tungsten steel (also known as cemented carbide); the material of the hammer plate 11 is a wear-resistant plate, replacing the traditional ordinary plate; the material of the hammer head 12 is tungsten steel, replacing the traditional ZGMn13 or alloy steel; such a design can effectively improve the service life of the crushing mechanism 100 of the present invention, which can be increased from the traditional 50 to 60 days to 150 to 180 days, and the life of the grinding disc device 10 is increased by 200%, and the replacement cost is 15 to 30% of the traditional cost.

[0053] Please refer to Figure 15 The structure of the crushing mechanism 100` in the second embodiment of the present invention is basically the same as the structure of the crushing mechanism 100 in the first embodiment. The differences are as follows:

[0054] In the crushing mechanism 100` of the second embodiment, no alloy rods 30 (30`, 30``) are welded in the tooth grooves 21 of the gear ring 20; while in the crushing mechanism 100 of the first embodiment, alloy rods 30 (30`, 30``) are welded in the tooth grooves 21 of the gear ring 20.

[0055] Except for the above differences, the structures of the other parts are the same as those of the crushing mechanism 100 of the first embodiment, so they will not be described in detail here.

[0056] In addition, in Figure 15 the crushing mechanism 100` of the second embodiment shown, further deformation can be made. For example, according to actual needs, the surfacing structure layer 13 on the first end face 111 of the hammer disc 11 can be removed to obtain a crushing mechanism that has fewer alloy rods 30 (30`, 30``) and surfacing structure layer 13 than the crushing mechanism 100 of the first embodiment.

[0057] Please refer to Figure 16 , the structure of the crushing mechanism 100`` of the third embodiment of the present invention is basically the same as that of the crushing mechanism 100 of the first embodiment, and the differences are as follows:

[0058] In the crushing mechanism 100`` of the third embodiment, no surfacing structure layer 13 is surfaced on the first end face 111 of the hammer disc 11; while in the crushing mechanism 100 of the first embodiment, a surfacing structure layer 13 is surfaced on the first end face 111 of the hammer disc 11.

[0059] Except for the above differences, the structures of the other parts are the same as those of the crushing mechanism 100 of the first embodiment, so they will not be described in detail here.

[0060] Compared with the prior art, since the end of the hammer head 12 protrudes outward from the side surface 112 of the hammer disc 11 to form an outward convex striking part 12a, and the outward convex striking part 12a also extends along the axial direction of the hammer disc 11 to form a covering structure 12b that at least partially covers the side surface 112 of the hammer disc 11. In this way, the crushing particle size of the material is controlled by the distance between the outer side surface 12a1 (12b1) of the hammer head 12 on the hammer disc 11 and the gear ring 20, rather than by the distance between the side surface 112 of the hammer disc 11 and the gear ring 20. At the same time, since the side surface 112 of the hammer disc 11 is covered by the covering structures 12b of a plurality of hammer heads 12 arranged at intervals on the hammer disc 11 along the rotation direction of the hammer disc 11, the exposed area of the side surface 112 of the hammer disc 11 relative to the gear ring 20 can be reduced, thereby playing a role in protecting the side surface 112 of the hammer disc 11, and thus further improving the service life of the hammer disc 11. Moreover, since the crushing particle size of the material is controlled by the distance between the outer side surface 12a1 (12b1) of the hammer head 12 on the hammer disc 11 and the gear ring 20, rather than by the distance between the side surface 112 of the hammer disc 11 and the gear ring 20, even if the side surface 12a1 (12b1) of the hammer head 12 wears, it will not affect the crushing particle size of the material. Therefore, the crusher including the grinding disc device 10 of the present invention can still operate efficiently when the outer side surface 12a1 (12b1) of the hammer head 12 wears slightly, and only the hammer head 12 needs to be replaced when the hammer head 12 wears, thus reducing the replacement and maintenance costs.

[0061] It should be noted that, in order to define the boundaries of the outward convex striking part 12a, the covering structure 12b and the mating part 12c on the hammer head 12, please refer to Figure 13 and Figure 14 ; in Figure 13 , the plane P1 enclosed by the center line is used as the dividing line between the outward convex striking part 12a and the covering structure 12b; in Figure 14 , the plane P2 enclosed by the center line is used as the dividing line between the outward convex striking part 12a and the mating part 12c; in order to avoid stress concentration between the outward convex striking part 12a and the mating part 12c, an arc-shaped transition structure 12d is provided between the outward convex striking part 12a and the mating part 12c. In addition, in the crushing mechanism 100 of the present invention in the crusher, the first end face 111 of the hammer disc 11 is arranged upward and the second end face 113 is arranged downward, and the material falls from above to the first end face 111 of the hammer disc 11; in addition, in Figure 11 , as an example, the circumferential outer contour of the hammer disc 11 is circular. Of course, according to actual needs, the circumferential outer contour of the hammer disc 11 can also be a regular polygon, so it is not limited to Figure 12 shown.

[0062] The above-disclosed are only the preferred examples of the present invention, and the scope of the rights of the present invention cannot be limited thereby. Therefore, all equivalent changes made according to the claims of the present invention fall within the scope covered by the present invention.

Claims

1. A grinding disc device of a crusher, comprising a hammer disc and a plurality of hammer heads arranged at intervals on the hammer disc along the rotation direction of the hammer disc. The hammer disc has opposite first end faces and second end faces and a side surface located between the first end face and the second end face. The hammer heads are assembled and connected to the hammer disc, and the hammer heads are in covering cooperation with the first end face of the hammer disc. Characterized in that, The end of the hammer head protrudes outward from the side surface of the hammer disc to form an outward convex striking part, and the outward convex striking part also axially extends along the hammer disc to form a covering structure that at least partially covers the side surface of the hammer disc; the outward convex striking part and the covering structure each extend along the rotation direction of the hammer disc and / or the direction opposite to the rotation direction to further cover the side surface of the hammer disc.

2. The grinding disc device according to claim 1, Characterized in that, The outer side surface of the outward convex striking part and the outer side surface of the covering structure facing away from the side surface of the hammer disc are flush with each other and are each a rotating surface, and the rotating center lines of the rotating surface and the hammer disc coincide with each other.

3. The grinding disc device according to claim 1, Characterized in that, The inner side surface of the covering structure facing the side surface of the hammer disc is a rotating surface or a plane. The rotating center lines of the rotating surface and the hammer disc coincide with each other, and the plane is tangent to the side surface of the hammer disc; the axially extending end of the covering structure extends beyond the second end face or is flush with the second end face.

4. The grinding disc device according to claim 1, Characterized in that, The assembly connection between the hammer head and the hammer disc is a replaceable assembly connection and / or the hammer heads are arranged radially around the rotation center line of the hammer disc.

5. The grinding disc device according to claim 1, Characterized in that, A surfacing structure layer is surfacing-welded on the first end face of the hammer disc. The surfacing structure layer completely or partially covers the first end face of the hammer disc, and the surfacing structure layer is located between the hammer head and the first end face of the hammer disc.

6. The grinding disc device according to claim 1, Characterized in that, Among all the hammer heads, the covering parts of some hammer heads that are in covering cooperation with the first end face of the hammer disc are each spliced with a splicing module towards the direction close to the rotation center line of the hammer disc. The splicing module is in covering cooperation with the first end face of the hammer disc, and there are 1 to 3 hammer heads spaced along the rotation direction of the hammer disc between two adjacent splicing modules.

7. The grinding disc device according to claim 6, Characterized in that, The splicing module is composed of one or more splicing blocks and / or the hammer head is made of cemented carbide.

8. A crushing mechanism of a crusher, including a gear ring, Characterized in that, The crushing mechanism further includes the grinding disc device according to any one of claims 1 to 7. The gear ring is coaxially arranged with the hammer disc, and the gear ring also surrounds the grinding disc device.

9. The crushing mechanism according to claim 8, Characterized in that, An alloy rod or an alloy covering layer is provided in the tooth groove of the gear ring, and the hardness of the alloy rod or the alloy covering layer is greater than the hardness of the gear ring.

Images