Plate hammer for impact crusher and impact crusher

Abstract

The utility model discloses a plate hammer for an impact crusher and the impact crusher. The longitudinal axis extends in the z direction and is parallel to the extending direction of the positioning groove in the installation position, the vertical axis extends in the y direction and points to the radial top face of the plate hammer in the installation position, and the transverse axis extends in the x direction and points to the impact side face of the plate hammer. At least one end, along the vertical axis, of the plate hammer is a working head, and in the extending direction of the transverse axis, the rear impact side face and the front impact side face are sequentially arranged at intervals and are arranged on the two sides of the working head respectively. Wherein the front impact side surface is provided with a convex part at a position close to the radial top surface, and the surface of the convex part protrudes out of the front impact side surface.

Description

TECHNICAL FIELD

[0001] The present application relates to the field of crushers, in particular to a plate hammer for an impact crusher and an impact crusher. BACKGROUND

[0002] Impact crushers are used for crushing mineral materials. During crushing, the material enters the plate hammer working area and is thrown against the back lining plate.

[0003] The plate hammer is a wearing part and must be replaced regularly. The working head of the currently applied plate hammer is prone to breakage and has insufficient wear resistance, and is replaced frequently. To this end, the strength and hardness of the material can be considered to be improved, but the hardness improvement will correspondingly reduce the toughness of the material, the plate hammer is more prone to breakage, and the breakage accident will also damage other components such as the rotor of the crusher. Alternatively, the overall size can be increased to prolong the wear time, but this will greatly increase the material cost, and the weight will be significantly increased, which is not safe and convenient for hoisting and use. CONTENT OF THE INVENTION

[0004] The present application relates to the field of crushers, in particular to a plate hammer for an impact crusher and an impact crusher.

[0005] The present application provides a plate hammer for an impact crusher, the plate hammer has a longitudinal axis extending in the z direction and parallel to the extension direction of the positioning groove in the installed position, a vertical axis extending in the y direction and pointing to the radial top surface of the plate hammer in the installed position, and a transverse axis extending in the x direction and pointing to the impact side surface of the plate hammer in the installed position.

[0006] The plate hammer has a working head at at least one end along the vertical axis, and the rear impact side surface and the front impact side surface are sequentially and separately arranged on both sides of the working head in the extension direction along the transverse axis.

[0007] The front impact side surface is provided with a convex portion near the radial top surface, and the surface of the convex portion protrudes from the front impact side surface.

[0008] In one embodiment, in the x direction, the protrusion size X1 of the convex portion relative to the front impact side surface is greater than 0 and less than or equal to 150 mm; preferably, the protrusion size X1 of the vertex of the convex portion relative to the front impact side surface is 20-80 mm.

[0009] In one embodiment, the convex part is a column extending along the longitudinal axis, and the longitudinal dimension of the column is substantially consistent with the longitudinal dimension of the front impact side in the direction along the longitudinal axis; or the convex parts are arranged at intervals along the longitudinal axis on the front impact side; or the number of the convex parts is two or more, and the convex parts are arranged in sequence along the vertical axis; or the projection shape of the convex part on the x-y plane is semicircular, triangular, square or trapezoidal.

[0010] In one embodiment, the plate hammer is provided with a fitting head matching the positioning groove at the other end along the vertical axis; the rear limiting side and the front limiting side are arranged in sequence at intervals along the transverse axis and are respectively arranged on both sides of the fitting head; the interval between the rear impact side and the front impact side is X2, the interval between the rear limiting side and the front limiting side is X3, X2>X3, and the difference between X2 and X3 is in the range of 10-100 mm; preferably, the difference between X2 and X3 is in the range of 20-50 mm.

[0011] In one embodiment, the interval X2 between the rear impact side and the front impact side is in the range of 120-125 mm; the interval X3 between the rear limiting side and the front limiting side is in the range of 90-110 mm.

[0012] In one embodiment, the front impact side and the rear impact side are respectively on both sides of the y-z plane;

[0013] And the front impact side is offset from the y-z plane along the transverse axis by a distance L1, and the rear impact side is offset from the y-z plane along the transverse axis by a distance L2, L1>L2, and the difference between L1 and L2 is in the range of 0-100 mm.

[0014] In one embodiment, the difference between L1 and L2 is in the range of 20-50 mm.

[0015] In one embodiment, the front impact side is offset from the y-z plane along the transverse axis by a distance L1 of 70-75 mm, and the rear impact side is offset from the y-z plane along the transverse axis by a distance L2 of 45-50 mm.

[0016] In one embodiment, the reinforcing block is embedded in the position close to the radial top surface of the plate hammer; the intersection line is formed between the convex surface and the front impact side surface; the first surface and the second surface are sequentially arranged on both sides of the reinforcing block in the extension direction along the vertical axis; and the lateral dimension of the reinforcing block gradually increases in the direction along the vertical axis and pointing to the radial top surface, the distance between the side edge of the first surface close to the intersection line and the intersection line is B1, the distance between the second surface and the radial top surface is B2, B1>B2, and the difference between B1 and B2 ranges from 0 to 80 mm.

[0017] In one embodiment, the difference between B1 and B2 ranges from 10 to 40 mm.

[0018] In one embodiment, the distance B1 between the side edge of the first surface close to the intersection line and the intersection line is 18-23 mm, and the distance B2 between the second surface and the radial top surface is 13-15 mm.

[0019] In one embodiment, the lateral dimension A1 of the first surface of the reinforcing block is 80-100 mm.

[0020] In one embodiment, the rear limiting side surface is provided with a support shoulder at one end along the vertical axis.

[0021] The rear limiting side surface is connected with the support shoulder, and the dimension Y1 of the rear limiting side surface 122 along the vertical axis is 50-150 mm; the rear limiting side surface is provided with a feeding head, and the feeding head is located in the middle of the rear limiting side surface along the longitudinal axis.

[0022] In one embodiment, the working head has two, which are respectively arranged at both ends of the plate hammer along the vertical axis, and the two working heads are rotationally symmetrically configured about the longitudinal axis.

[0023] Another aspect of the present application also provides an impact crusher comprising the plate hammer for the impact crusher.

[0024] Compared with the prior art, the present application has at least the following effects:

[0025] In this embodiment, the front impact side has a protrusion near the radial top surface. The surface of the protrusion protrudes beyond the front impact side. This is because the part of the front impact side near the radial top surface has the highest frequency of contact with the material and directly bears the impact of the material. Therefore, designing a protrusion protruding beyond the front impact side in this local area can enhance impact resistance and reduce the risk of breakage. It has been verified that the breakage frequency can be reduced by more than 80%. At the same time, the designed protrusion allows for an increase in the thickness of the working head near the radial top surface. The larger thickness can improve the resistance to impact breakage and extend the wear life. Grinding it flat requires a longer time, thereby reducing the replacement frequency. The locally added protrusion does not significantly increase material costs or workpiece weight. In addition, the protrusion increases the overall strength of the hammer plate. The added protrusion can also provide a larger space for the ceramic reinforcing block, allowing for the installation of a larger ceramic reinforcing block, directly increasing the volume of the impact working area.

[0026] The preferred embodiments of this application will be described in more detail below with reference to the accompanying drawings, so as to facilitate an understanding of the features and advantages of this application. Attached Figure Description

[0027] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings of the embodiments of this application will be briefly described below. The drawings are merely illustrative of some embodiments of this application and are not intended to limit all embodiments of this application to them.

[0028] Figure 1 A perspective view of a hammer plate structure for an impact crusher provided in an embodiment of this application;

[0029] Figure 2 for Figure 1 End view;

[0030] Figure 3 This is a schematic diagram of a hammer mounted on a rotating shaft according to an embodiment of this application;

[0031] Figure 4 This is a structural view of the end of a hammer provided in another embodiment of this application;

[0032] Figure 5 for Figure 1 A three-dimensional view of the hammer from another perspective;

[0033] Figure 6 for Figure 5 Rear view of the hammer;

[0034] Figure 7 A perspective view of a hammer plate structure for an impact crusher provided in another embodiment of this application;

[0035] Figure 8A perspective view of a plate hammer for an impact crusher is provided for another embodiment of the present application;

[0036] Figure 9 A perspective view of a plate hammer for an impact crusher is provided for another embodiment of the present application;

[0037] In the figure,

[0038] 10, rotating shaft; 11, positioning groove; 12, front positioning component; 13, rear positioning component;

[0039] 100, plate hammer;

[0040] 110, working head; 111, front impact side; 112, rear impact side; 113, convex part; 114, radial top surface; b, boundary line;

[0041] 120, assembling head; 121, front limiting side; 122, rear limiting side; 123, supporting shoulder; 124, groove; 125, fixing pin; a, feeding head;

[0042] 130, notch; 140, through hole;

[0043] 200, reinforcing block; 210, first surface; 220, second surface. DETAILED DESCRIPTION

[0044] In order to make the purpose, technical scheme and advantages of the technical scheme of the present application more clear, the technical scheme of the embodiments of the present application will be described clearly and completely in the following with reference to the drawings of the embodiments of the present application. The same reference signs in the drawings represent the same components. It should be noted that the described embodiments are part of the embodiments of the present application, rather than all the embodiments. Based on the described embodiments of the present application, all other embodiments obtained by those skilled in the art without creative labor fall within the scope of protection of the present application.

[0045] Unless otherwise defined, technical terms or scientific terms used herein shall have the same meaning as commonly understood by one of ordinary skill in the art to which this application belongs. The terms "first", "second", and the like, as used in the specification and claims herein, do not imply any order, quantity, or importance, but are used to identify various elements. Also, the terms "a" and "an" do not denote a limitation of quantity, and are used to describe at least one of something. The terms "comprises", "comprising", "includes", "including", or the like, mean including at least the elements listed thereafter and equivalents thereof, but not excluding other elements. The terms "connected", "coupled", or the like, mean to be directly or indirectly connected or coupled, and can include wired or wireless connections or couplings.

[0046] Reference Figures 1-3 A plate hammer for an impact crusher, the plate hammer 100 has a longitudinal axis extending in the z direction and extending parallel to the extension direction of the positioning groove 11 in the installed position, a vertical axis extending in the y direction and pointing to the radial top surface 114 of the plate hammer 100 in the installed position, and a transverse axis extending in the x direction and pointing to the impact side surface of the plate hammer 100;

[0047] The plate hammer 100 has a working head 110 at at least one end along the vertical axis, and the rear impact side surface 112 and the front impact side surface 111 are arranged in sequence and are respectively arranged on both sides of the working head 110 in the extension direction along the transverse axis;

[0048] The front impact side surface 111 is provided with a convex portion 113 near the radial top surface 114, and the surface of the convex portion 113 protrudes from the front impact side surface 111.

[0049] Specifically, the rotating shaft 10 of the crusher can rotate around the rotation axis F; four plate hammers 100 are arranged on the rotating shaft 10 in a circumferential direction, and the plate hammers 100 extend parallel to the rotation axis F of the rotating shaft 10.

[0050] The plate hammer 100 generally includes a middle section and end portions at both ends of the middle section. In the following description of the plate hammer 100, the coordinate system is referred to Figure 2 The origin of the coordinate system is located at the center of the middle section of the plate hammer 100, i.e., the origin is at half the length (z axis), height (y axis), and width (thickness) (x axis) of the middle section of the plate hammer 100; the coordinate system is related to the corresponding plate hammer 100, and not to the rotating shaft 10. Since the plate hammer 100 can be slightly tilted in the installed position, the coordinate system is also referred to Figure 3The coordinate system of the middle plate hammer 100 can also be slightly inclined around the longitudinal axis (z-axis) of the plate hammer 100 body. In Figure 3 In the middle, the x direction of the coordinate system points to the direction perpendicular to the front side; the y direction is the radial direction and points to the direction away from the rotation axis F; the z axis is parallel to the front side and the rotation axis F. The positioning groove 11 is a recess extending along the longitudinal direction of the rotating shaft 10, i.e. parallel to the rotation axis F.

[0051] In the present embodiment, the front impact side 111 is provided with a protrusion 113 at the local part close to the radial top surface 114, and the surface of the protrusion 113 protrudes from the front impact side 111. This is because the part of the front impact side 111 close to the radial top surface 114 is contacted most frequently by the material and directly bears the impact of the material. Therefore, the design of the protrusion 113 protruding from the front impact side 111 at this local part can enhance the impact resistance and reduce the risk of breakage. It has been verified that the breakage frequency is reduced by more than 80%. At the same time, the design of the protrusion 113 increases the thickness D of the working head 110 at the part close to the radial top surface 114. The larger thickness size can improve the ability to resist impact breakage, prolong the wear life, and take a longer time to wear it flat, thereby reducing the replacement frequency. The locally added protrusion 113 will not significantly increase the material cost and the weight of the workpiece. At the same time, the added protrusion 113 can also provide more space for the setting of the ceramic reinforcing block and can set a larger ceramic reinforcing block, directly increasing the volume of the impact working area and increasing the overall strength of the plate hammer.

[0052] In the present application, when the material block hits the surface of the protrusion 113, the surface of the protrusion 113 will change the trajectory direction of the material block because of the included angle between the surface of the protrusion 113 and the vertical front impact side 111, so that the material block will splash to the adjacent part and be broken again by the front impact side 111. The material block can contact different parts of the working head 110 multiple times, which can improve the crushing efficiency per unit time. Moreover, since the protrusion 113 is arranged at the local part of the front impact side 111 close to the radial top surface 114, most of the material blocks first contact the protrusion 113, and most of the material blocks contacting the front impact side 111 are splashed onto its surface after being collided by the protrusion 113. Therefore, the impact force borne by the front impact side 111 is significantly reduced, and the probability of breakage and wear is reduced.

[0053] Reference Figure 2In some embodiments, the protrusion 113 has a protruding dimension X1 relative to the front impact side 111 in the x direction, which is greater than 0 and less than or equal to 150 mm. It has been tested that when the dimension is within this range, the anti-impact breaking property can be effectively improved, and when the dimension is too large, more material cost is required. Preferably, the protruding dimension X1 of the vertex of the protrusion 113 relative to the front impact side 111 is 20-80 mm. When the protruding dimension X1 is too large (greater than 80 mm), it may hinder the contact between the material and the main part of the front impact side 111, which is not conducive to improving the work efficiency, and the increase in the anti-impact breaking property is not obvious.

[0054] Reference Figure 1 and Figure 2 In some embodiments, the protrusion 113 is a column extending along the longitudinal axis (z direction), and in the direction along the longitudinal axis (z direction), the longitudinal dimension of the column is consistent with the longitudinal dimension of the front impact side 111. Alternatively, in other embodiments, the protrusions 113 are arranged on the surface of the front impact side 111 at intervals along the longitudinal axis (z direction).

[0055] Specifically, in the present embodiment, the protrusion 113 can be a whole column extending in the z direction, which has a large area and a high probability of contacting the material, which is conducive to exerting the advantages of the present application. Alternatively, the protrusions 113 can be arranged at intervals on the front impact side 111, which is equivalent to strengthening the local position of the front impact side 111 of the working head 110 in the form of points, which has higher flexibility and stronger applicability to the scene.

[0056] Furthermore, the multiple point-like arrangements can increase the contact frequency of the protrusions 113 and the material. When a material block hits the surface of one of the protrusions 113, since the upper, lower, left and right side surfaces of the point-like protrusion 113 form an angle with the vertical front impact side 111, the circumferential surface of the protrusion 113 will change the trajectory direction of the material block, so that it splashes to the adjacent position on the side. When the multiple protrusions 113 are arranged at intervals, the material block whose direction has been changed has a high probability of hitting the surface of the adjacent protrusion 113 on the left or right side and being broken by impact. A single material block can have a high probability of sequentially contacting multiple protrusions 113, which can improve the breaking efficiency per unit time. The front impact side 111 is below the protrusions 113, and most of the contacted material blocks splash onto its surface after being hit by multiple protrusions 113 above, so that the impact force borne by the front impact side 111 is lower, and the probability of breaking and wearing is significantly reduced.

[0057] Reference Figure 5 , 7In some embodiments, the projection shape of the convex part 113 in the x-y plane is semicircular, triangular, square or trapezoidal. Specifically, the convex part 113 can adopt various forms, all of which have the effect of enhancing the impact resistance, reducing the risk of breakage, and improving the wear resistance. In particular, when it is semicircular, the surface has no sharp corners, and when the convex part 113 is in contact with the material, the arc surface will not produce local stress concentration, the stress on each part of the convex part 113 surface is uniform, which is conducive to maintaining the stability of the cross-sectional shape, and the shape will not change even after a long time of work. When the projection shape of the convex part 113 is triangular or trapezoidal, the sharp corners on the surface will produce local stress, which may cause breakage at the corners.

[0058] Of course, in addition to the above forms, the projection shape of the convex part 113 can adopt various forms, which are not limited in the present application.

[0059] Reference Figure 9 In some embodiments, the number of convex parts 113 is two or more, and they are arranged in sequence along the vertical axis.

[0060] Specifically, when the number of convex parts 113 is two or more, more areas on the front impact side 111 are arranged with convex parts 113, and the arrangement of multiple convex parts 113 can increase the contact frequency between the convex part 113 and the material. When a material block hits the surface of one of the convex parts 113, the surface of the convex part 113 will change the trajectory direction of the material block due to the included angle between the surface of the convex part 113 and the vertical front impact side 111, so that the material block is splashed to the adjacent part. The material block that has been changed in direction has a high probability of hitting the surface of the adjacent convex part 113 and being broken by impact. The single material block can be in contact with multiple convex parts 113 in sequence, which can improve the breaking efficiency per unit time. The front impact side 111 is far away from the radial top surface 114, and there are fewer materials falling directly onto its surface or falling onto its surface after being hit by the convex part once. Therefore, the material blocks that contact the front impact side 111 are mostly splashed onto its surface after being hit by multiple convex parts 113, so the impact force borne by the front impact side 111 is lower, and the probability of breakage and wear is significantly reduced.

[0061] Reference Figure 2 In some embodiments, the plate hammer 100 has a fitting head 120 at the other end along the vertical axis to match the positioning slot 11. In the extension direction along the transverse axis (x direction), the rear limiting side 122 and the front limiting side 121 are arranged in sequence and spaced apart, and are respectively arranged on both sides of the fitting head 120. The distance between the rear impact side and the front impact side is X2, the distance between the rear limiting side and the front limiting side is X3, X2>X3, and the difference between X2 and X3 is in the range of 10-100 mm.

[0062] Specifically, the distance X2 between the rear impact side 112 and the front impact side 111 can be 120-125 mm; the distance X3 between the rear limiting side 122 and the front limiting side 121 can be 90-110 mm. With the design of the present embodiment, X2>X3, the difference ranges from 10 to 100 mm, the working head 110 part has a larger thickness ratio, the wear needs a longer time, and a larger wear-resistant reinforcing block can be built in; the thickness of the assembly head 120 can meet the assembly and fixing strength requirement, and the thickness of the assembly head 120 is smaller than the thickness of the working head 110, which avoids excessive use of materials and increases the cost. As a preferred, the difference between X2 and X3 ranges from 20 to 50 mm, the size of the working head will not be too large, and the material cost will not be increased too much.

[0063] Reference Figure 2 In some embodiments, the front impact side 111 and the rear impact side 112 are respectively on both sides of the y-z plane;

[0064] And the front impact side is offset from the y-z plane by a distance L1 along the transverse axis direction, and the rear impact side is offset from the y-z plane by a distance L2 along the transverse axis direction, L1>L2, and the difference between L1 and L2 ranges from 0 to 100 mm.

[0065] Specifically, the distance L1 between the front impact side 111 and the y-z plane along the transverse axis direction can be 70-75 mm, and the distance L2 between the rear impact side 112 and the y-z plane along the transverse axis direction can be 45-50 mm. The front impact side 111 is directly in contact with the high-frequency material and bears stronger impact force, so a larger offset distance L1 can improve the impact resistance and be beneficial to improve the working efficiency and prolong the service life; the rear impact side 112 is not directly in contact with the material surface, and the impact is small, so the offset distance L2 is relatively small. However, compared with the traditional plate hammer (the offset distance is less than 30 mm), the offset distance and the offset thickness size are also increased to some extent, and the thickening is beneficial to improve the wear resistance. As a preferred, the difference between L1 and L2 ranges from 20 to 50 mm, the difference between the offset sizes of the two will not be too large, which can avoid the inclination of the working head installation on the left and right of the lever, and reduce the difficulty of hoisting and configuring.

[0066] Reference Figure 4In some embodiments, the plate hammer 100 is embedded with a reinforcing block 200 near the radial top surface 114; an intersection line b is formed between the convex portion 113 surface and the front impact side 111, the first surface 210 and the second surface 220 are sequentially arranged on both sides of the reinforcing block 200 in the extension direction of the vertical axis; and in the direction of the vertical axis (y direction) and pointing to the radial top surface 114, the lateral dimension of the reinforcing block 200 gradually increases, the distance between the side edge of the first surface close to the intersection line and the intersection line is B1, and the distance between the second surface and the radial top surface 114 is B2, B1>B2, and the difference between B1 and B2 is in the range of 0-80mm.

[0067] Specifically, the material of the plate hammer 100 is metal such as iron, and the reinforcing block 200 is made of high-hardness material such as ceramic, etc. In this embodiment, the reinforcing block 200 is covered in the iron block by hot melting, that is, the reinforcing block 200 is placed in the molten iron and hot melted together and then cooled and formed. In actual production, when the distance B2 is less than 13mm, the fusion performance of the iron layer and the reinforcing block 200 is poor and the interface is easy to crack, which may be due to the fact that if the covering thickness of the surface iron material is small during hot melting, the two materials may not be fused together at the molecular level or even cracked at the interface. Therefore, the distance B2 needs to be greater than or equal to 13mm, and the actual optional range is 13mm-15mm. Moreover, under the same production conditions, the distance B1 needs to be set to be greater than or equal to 18mm to reduce the cracking of the interface between the iron layer and the reinforcing block 200, which may be because there is a sharp corner at the intersection line b of the convex portion 113 and the front impact side 111, and the local stress is concentrated at this part. The difficulty of fusing iron and reinforcing block 200 at this part is greater, and a thicker covering thickness is required. Therefore, the distance B1 is greater than the distance B2. When the thickness of the distance B1 is greater than 23mm, the material cost increases and the performance improvement is not obvious. That is, the value of B1 in this application is 18mm-23mm. Based on this limitation, the lateral dimension of the first surface 210 is limited, and due to the setting of the convex portion 113 in this application, the second surface 220 can extend into the convex portion 113 in the lateral direction, so the lateral dimension is larger. That is, in the direction of the vertical axis and pointing to the radial top surface 114, the lateral dimension of the reinforcing block 200 gradually increases, so that the reinforcing block 200 has a trapezoidal cross section. The hardness of the reinforcing block 200 such as ceramic is extremely high (HV1600), and the increase in size is more conducive to increasing the wear resistance.

[0068] As a preferred, the difference between B1 and B2 is in the range of 10-40mm, which is not too large to cause the area range where the reinforcing block 200 is arranged to be squeezed and reduced, so as to ensure that there is a large enough area to arrange the reinforcing block, thereby increasing the wear life and impact strength.

[0069] As another preferred, the distance between the first surface 210 and the radial top surface 114 is less than the distance between the intersection line b and the radial top surface 114. With such an arrangement, the reinforcing block 200 is wrapped in the head region where the convex portion 113 is located, the head region has a large cross-sectional area, which is conducive to placing a larger volume of reinforcing block 200, thereby enhancing the wear resistance and overall performance.

[0070] Reference Figure 4 In some embodiments, the lateral dimension A1 of the first surface 210 of the reinforcing block 200 is 80mm-100mm. The reinforcing block 200 is in the head region of the working head 110 close to the radial top surface 114, the head region has a convex portion 113 and a large cross-sectional area, which is conducive to placing a large volume of reinforcing block 200, so the lateral dimension A1 of the first surface 210 of the reinforcing block 200 is designed to be 80mm-100mm; at the same time, since the lateral dimension A2 of the second surface 220 is greater than A1, the size is larger, so the overall size of the reinforcing block 200 is significantly increased, thereby being very conducive to increasing the wear resistance.

[0071] In some embodiments, the material of the hammer 100 is selected to be martensitic alloy steel, and the component ratio is Si: 0.3%-1.0%, Mo: 0.4%-0.7%, Ni: 0.7%-1.0%, Mn: 0.4%-1.0%, C: 0.42%-0.59%, Cr:

[0072] 3.0%-3.9%. The traditional plate hammer has insufficient structural strength and is prone to breakage. If a material with greater hardness and greater wear resistance is selected, the probability of breakage under the same stress conditions will be greater, so the overall performance cannot be improved by improving the material, and the C content can only be set to less than 0.4% and the Cr content can only be set to less than 3.0%. The material selected in the present application has the following component contents: Si: 0.3%-1.0%, Mo: 0.4%-0.7%, Ni: 0.7%-1.0%, Mn: 0.4%-1.0%, C: 0.42%-0.59%, and Cr: 3.0%-3.9%. No cracks occur, and the hardness can reach HRC58, the wear resistance is improved by 10-15%, and the overall performance is significantly improved. This may be because the added convex portion 113 increases the local strength, and the reinforcing block 200 embedded in the end position corresponding to the convex portion 113 has a significant increase in volume, which enhances the strength and crack resistance of the plate hammer 100 in terms of structural design. Under this premise, the special design of the component weight composition: Si: 0.3%-1.0%, Mo: 0.4%-0.7%, Ni: 0.7%-1.0%, Mn: 0.4%-1.0%, C: 0.42%-0.59%, and Cr: 3.0%-3.9% is fused, and the plate hammer 100 made of the material has improved hardness and is not prone to cracking. The C content in the alloy can even be increased to 0.59%, and the plate hammer 100 is also not prone to breaking. However, when the C content in the alloy is greater than 0.59% and the Cr is greater than 3.9%, the hardness and overall performance are not significantly improved, and some cracks may appear under harsh working conditions. Therefore, when the material containing Si: 0.3%-1.0%, Mo: 0.4%-0.7%, Ni: 0.7%-1.0%, Mn: 0.4%-1.0%, C: 0.42%-0.59%, and Cr: 3.0%-3.9% is selected as the material of the plate hammer 100, the performance is significantly improved, the hardness can reach HRC58, the wear resistance is improved by 10-15%, and the overall performance is good.

[0073] More preferably, Si: 0.3%-1.0%, Mo: 0.4%-0.7%, Ni: 0.7%-1.0%, Mn: 0.4%-1.0%, C: 0.42%-0.50%, and Cr: 3.0%-3.4%. Compared with traditional products, the hardness and wear resistance of this component material are significantly improved, the toughness performance is better, the overall mechanical properties are more excellent, and it is suitable for use in most working conditions.

[0074] Reference Figure 5 and Figure 6 In some embodiments, the rear limiting side surface 122 is provided with a support shoulder 123 at one end along the vertical axis;

[0075] The rear limiting side surface 122 is connected with the supporting shoulder 123, and the size Y1 of the rear limiting side surface 122 along the vertical axis (y direction) is 50-150 mm, and the rear limiting side surface 122 is provided with a feeding riser a, which is located at the middle of the rear limiting side surface 122 along the longitudinal axis direction (z direction). The plate hammer 100 is usually formed by casting, and specifically, when casting, the molten iron at about 1400 DEG C is first poured into the mold through the casting gate; when there are defects such as pores due to incomplete filling, the second step of supplementing pouring through the feeding riser a with a large radial size is needed to fill the pores, and when the second step is implemented, the overall temperature in the mold has decreased, and the flowability of the feeding iron liquid has decreased. If the feeding riser a is arranged at one end of the plate hammer 100 along the longitudinal axis, the feeding iron liquid is difficult to flow to the defect position at the other end, such as the other end of the longitudinal axis. In the present application, in order to facilitate the arrangement of the feeding riser a with a large radial size, the size Y1 of the rear limiting side surface 122 along the vertical axis is designed to be 50-150 mm, and the feeding riser a is arranged at the middle of the rear limiting side surface 122 along the longitudinal axis direction. At this time, the feeding riser a is located at the middle of the plate hammer 100 along the longitudinal axis, and the distance from the feeding riser a to both ends of the plate hammer 100 along the longitudinal axis is consistent. Therefore, the feeding iron liquid entering through the feeding riser a at the middle will not be too far away from the defect position, and even if the temperature of the feeding iron liquid is relatively low, it can still smoothly and quickly reach any position in the mold, ensuring the feeding effect and avoiding the occurrence of defect pores that cannot be fed. On the other hand, since the rear limiting side surface 122 is connected with the supporting shoulder 123 and there is a clear angle between them, when the rear limiting side surface 122 is milled by using a high-hardness milling cutter, if the size of the rear limiting side surface 122 along the vertical axis is too small, the milling cutter will frequently contact the angle position where the rear limiting side surface 122 is connected with the supporting shoulder 123 during milling, and at this time, the milling cutter will be partially suspended and stress concentration will occur. Therefore, in the present application, the size Y1 of the rear limiting side surface 122 along the vertical axis is expanded to 50-150 mm, so that when the rear limiting side surface 122 is milled by the milling cutter, the milling cutter will not frequently contact the angle position where the rear limiting side surface 122 is connected with the supporting shoulder 123, and the stress concentration phenomenon is reduced.

[0076] In some other embodiments, the working head 110 has two, which are respectively arranged at both ends of the plate hammer 100 along the vertical axis, and the two working heads 110 are rotationally symmetrically configured about the longitudinal axis.

[0077] In this embodiment, compared with a single working head 110, two working heads 110 arranged rotationally symmetrically can be used in turn. When one working head 110 reaches the wear limit, it can be subsequently flipped around its own longitudinal axis, and the other working head 110 of the plate hammer 100 located in the positioning groove 11 in the rotor, which has not yet been worn, is thereby moved to the outside, so that the plate hammer 100 can be used until the wear limit of both working heads 110 is reached. Each working head 110 can have the structural features mentioned above, and the two working heads 110 are arranged rotationally symmetrically with respect to each other.

[0078] It should be noted that the support shoulder 123 is supported on the rear positioning member 13, which is welded to the rotor.

[0079] The front positioning member 12 and the rear positioning member 13 on both sides of the plate hammer 100 guide and position the plate hammer 100 in the longitudinal direction (z-axis) and the circumferential direction at the same time. Further, the plate hammer 100 is prevented from moving in the longitudinal direction (z-axis) of the rotor by at least one recess 124 adjacent to the support shoulder 123, which is used to accommodate a detachably inserted fixing pin 125 that passes through a hole in the rear positioning member 13 of the plate hammer 100 and is embedded in the recess 124.

[0080] Preferably, the recess 124 and the fixing pin 125 are provided with two, so that when the plate hammer 100 breaks, the two fixing pins 125 can simultaneously fix the plate hammer 100, thereby avoiding the broken part flying out and causing a safety accident.

[0081] The end of the plate hammer 100 is provided with a notch 130 on the end side adjacent to the support shoulder 123, and a through hole 140 is arranged in the notch 130. The through hole 140 and the notch 130 are used to accommodate a hoisting tool for hoisting the plate hammer 100 into or out of the positioning groove 11.

[0082] The exemplary embodiments of the present application are described in detail above with reference to the preferred embodiments, however, those skilled in the art can understand that various modifications and improvements can be made to the above specific embodiments without departing from the concept of the present application, and various technical features and structures proposed in the present application can be combined without exceeding the scope of the present application, and the scope of protection of the present application is determined by the appended claims.

Claims

1. A plate hammer for an impact crusher, characterized in that, the plate hammer has a longitudinal axis extending along the z direction and parallel to the extension direction of the positioning groove in the installed position, a vertical axis extending along the y direction and pointing to the radial top surface of the plate hammer in the installed position, and a transverse axis extending along the x direction and pointing to the impact side surface of the plate hammer; the plate hammer is provided with a working head at at least one end along the vertical axis, and a rear impact side surface and a front impact side surface are arranged in sequence and respectively on both sides of the working head in the extension direction along the transverse axis; wherein the front impact side surface is provided with a protrusion near the radial top surface, and the surface of the protrusion protrudes from the front impact side surface.

2. A board hammer for an impact crusher according to claim 1, characterized in that In the x direction, the protrusion has a protrusion size X1 relative to the front impact side surface greater than 0 and less than or equal to 150 mm.

3. A board hammer for an impact crusher as claimed in claim 1, characterized in that, The protrusion is a column extending along the longitudinal axis, and in the direction along the longitudinal axis, the longitudinal size of the column is substantially the same as the longitudinal size of the front impact side surface; or the protrusions are arranged in sequence on the front impact side surface; or the number of protrusions is two or more and arranged in sequence along the vertical axis; or the projection shape of the protrusion on the x-y plane is semicircular, triangular, square or trapezoidal.

4. A board hammer for an impact crusher as defined in claim 1, characterized in that The plate hammer is provided with a fitting head matching the positioning groove at the other end along the vertical axis, and a rear limiting side surface and a front limiting side surface are arranged in sequence and respectively on both sides of the fitting head in the extension direction along the transverse axis; the distance between the rear impact side surface and the front impact side surface is X2, the distance between the rear limiting side surface and the front limiting side surface is X3, X2>X3, and the difference between X2 and X3 is in the range of 10-100 mm.

5. A board hammer for an impact crusher as claimed in claim 4, characterised in that, The distance X2 between the rear impact side surface and the front impact side surface is 120-125 mm, and the distance X3 between the rear limiting side surface and the front limiting side surface is 90-110 mm.

6. A board hammer for an impact crusher as defined in claim 1, characterized in that The front impact side surface and the rear impact side surface are respectively on both sides of the y-z plane; and the front impact side surface is offset relative to the y-z plane along the transverse axis by a distance L1, and the rear impact side surface is offset relative to the y-z plane along the transverse axis by a distance L2, L1>L2, and the difference between L1 and L2 is in the range of 0-100 mm.

7. A board hammer for an impact crusher as claimed in claim 6, characterised in that, The difference between L1 and L2 is in the range of 20-50 mm.

8. A board hammer for an impact crusher as defined in claim 6, characterized in that The front impact side surface is offset relative to the y-z plane along the transverse axis by a distance L1 of 70-75 mm, and the rear impact side surface is offset relative to the y-z plane along the transverse axis by a distance L2 of 45-50 mm.

9. A board hammer for an impact crusher as defined in claim 1, characterized in that The reinforcing block is embedded in the part close to the radial top surface of the plate hammer; the intersection line is formed between the convex surface and the front impact side surface, the first surface and the second surface are sequentially and spacedly arranged on the two sides of the reinforcing block in the extension direction along the vertical axis; and the lateral dimension of the reinforcing block gradually increases in the direction along the vertical axis and pointing to the radial top surface, the spacing between the side edge of the first surface close to the intersection line and the intersection line is B1, the spacing between the second surface and the radial top surface is B2, B1>B2, and the difference between B1 and B2 ranges from 0 to 80 mm.

10. A board hammer for an impact crusher as claimed in claim 9, characterised in that, The difference between B1 and B2 ranges from 10 to 40 mm.

11. A board hammer for an impact crusher as claimed in claim 9, characterized in that The spacing B1 between the side edge of the first surface close to the intersection line and the intersection line is 18-23 mm, and the spacing B2 between the second surface and the radial top surface is 13-15 mm.

12. A board hammer for an impact crusher as defined in claim 9, characterized in that The lateral dimension A1 of the first surface of the reinforcing block is 80-100 mm.

13. A board hammer for an impact crusher as defined in claim 4, characterized in that The rear limiting side surface is provided with a support shoulder at one end along the vertical axis. The rear limiting side surface is connected with the support shoulder, and the dimension Y1 of the rear limiting side surface along the vertical axis is 50-150 mm, and the rear limiting side surface is provided with a feeding head, and the feeding head is located in the middle of the rear limiting side surface along the longitudinal axis.

14. A board hammer for an impact crusher as defined in claim 1, characterized in that The working head has two, which are respectively arranged at the two ends of the plate hammer along the vertical axis, and the two working heads are rotationally symmetrically constructed about the longitudinal axis.

15. An impact crusher, characterized in that The plate hammer for the impact crusher according to any one of claims 1-14 is included. The plate hammer for the impact crusher according to any one of claims 1-14 is included.

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