Scraper structure for onboard swing type scraper conveyor

Abstract

The invention belongs to the technical field of middle single-chain swing type scraper conveyors, and particularly relates to a scraper structure for a machine-mounted swing type scraper conveyor, the scraper structure comprises a slotting scraper base, a sliding frame and a roller assembly, the end part of the slotting scraper base is provided with a sliding frame mounting structure, the sliding frame is arranged in the sliding frame mounting structure in a sliding manner, and the roller assembly is arranged in the slotting scraper base. A spring is arranged between the sliding frame and the sliding frame mounting structure; the roller assembly is arranged on the sliding frame; the sliding frame installation structure comprises a sliding groove end cover and a lower sliding groove formed in the slotting scraper blade base, the sliding groove end cover is detachably arranged on the slotting scraper blade base, and an upper sliding groove corresponding to the lower sliding groove is formed in the sliding groove end cover. According to the scraper chain, the scraper used by a traditional scraper chain is modified, the sliding frame, the rolling wheel assembly, the spring and the like are additionally arranged at the end of the scraper, the rolling wheel makes contact with the conveying groove during swinging operation, impact force passes through the C-shaped supporting sliding frame assembly and the spring, vibration impact is effectively absorbed, and the cushioning effect is achieved. And the normal coal conveying effect is not influenced during straight operation.

Description

Technical Field

[0001] The invention belongs to the technical field of intermediate single-chain swing-type scraper conveyors, and more specifically, relates to a scraper structure for an airborne swing-type scraper conveyor. Background Art

[0002] In the existing fully-mechanized tunneling equipment widely used in coal mine roadway excavation, such as roadheader-anchoring machines, boom-type roadheaders, continuous miners, etc., the transportation parts that undertake the transportation of coal materials in such tunneling equipment all adopt short-distance swing-type scraper conveying technology. Restricted by the space limitation in the coal mine underground and the requirements for the layout of the overall machine structure size, the chain drive system of the existing scraper conveyor adopts the chain drive system provided by the invention patent with the publication number of CN101709643A. The two wings of its scraper adopt a trapezoidal straight design to meet the requirements of the rotatability and compactness of the scraper chain. However, in actual use, there are still deficiencies.

[0003] With the rapid development of domestic mining technology, mining equipment is developing towards high-efficiency loading and transportation, and the corresponding mining capacity is continuously improved. In order to adapt to the needs of the overall machine to move and turn in the roadway and the adjustment of the discharge position of the shuttle car transportation equipment behind the unit, the short-distance swing-type scraper conveying mechanism adopts a segmented structure and the conveyor tail can swing left and right around the transportation trough. When the conveyor tail swings for operation, the running track of the scraper chain will change. When the scraper enters the swing bending section, the side wing of the scraper contacts the spring plate to generate sliding friction, and the local resistance suddenly increases, causing bumps and jams. The scraper will deflect, causing system shock and damaging the running stability of the chain drive system. The stress at the hinge of the scraper chain increases, thereby increasing the possibility of faults such as chain breakage and chain jamming.

[0004] With the traditional straight design of the two wings of the scraper, the two wings of the scraper directly contact, collide and rub with the spring plate in the swing bending section, and serious wear phenomena occur on both the wing tip of the scraper and the spring plate. When replacing relevant components, the machine must be stopped, seriously affecting the reliability and production efficiency of the use of the overall machine equipment.

[0005] Therefore, it is necessary to improve the existing technology. Summary of the Invention

[0006] In order to overcome the deficiencies existing in the prior art, a scraper structure for an airborne swing-type scraper conveyor is provided, which improves the running stability of the chain drive system, reduces the wear of the wing tip of the scraper and the spring plate, and is convenient for replacement and maintenance.

[0007] In order to solve the above technical problems, the technical solution adopted by the invention is as follows: A scraper structure for an airborne swing-type scraper conveyor, comprising a grooved scraper base, a carriage, and a roller assembly. A carriage mounting structure is provided at the end of the grooved scraper base. The carriage is slidably disposed in the carriage mounting structure, and a spring for driving the carriage to move away from the grooved scraper base is provided between the carriage and the carriage mounting structure. The roller assembly is disposed on the carriage; The carriage mounting structure includes a chute end cover and a lower chute provided on the grooved scraper base. The chute end cover is detachably disposed on the grooved scraper base. An upper chute corresponding to the lower chute is provided on the chute end cover. The carriage is located between the upper chute and the lower chute and is slidably limited and stroke-limited by the upper chute and the lower chute.

[0008] Preferably, a first step and a second step with decreasing height are provided at the end of the grooved scraper base. The lower chute is provided on the upper end surface of the second step. A recessed groove is provided on the side surface of the first step along the direction of the lower chute. The spring is located in the recessed groove.

[0009] Preferably, a threaded hole is provided on the upper end surface of the first step. The chute end cover is provided with a counterbore seat corresponding to the threaded hole. The counterbore seat and the threaded hole are connected by a fastening screw; Side baffles are provided on both sides of the chute end cover.

[0010] Preferably, the carriage is a C-shaped support carriage. A spring fixing seat is fixedly connected to the rear end of the C-shaped support carriage. The spring is provided on the spring fixing seat.

[0011] Preferably, the roller assembly includes a fixed shaft, a roller, and a bearing. The fixed shaft is provided on the carriage. The roller is provided on the fixed shaft through two bearings. Axial limits of the two bearings away from each other are provided by circlips on the fixed shaft. A dust-proof ring is provided between the bearing and the circlip.

[0012] Preferably, slag discharge holes are provided on the side wall of the lower chute along the sliding direction of the carriage.

[0013] The beneficial effects of the present invention compared with the prior art are as follows: 1. By transforming the scraper used in the traditional scraper chain, adding a carriage, a roller assembly, a spring, etc. at the end of the scraper, when swinging, contact occurs between the roller and the conveying trough, and the impact force passes through the C-shaped support carriage assembly and the spring, effectively absorbing vibration and impact, playing a shock-absorbing role. When operating straight, it does not affect the normal coal transportation. Greatly reduces the accident rate of chain breakage of the scraper chain in the chain drive conveying system equipped with this scraper during swinging operation.

[0014] 2. In the present invention, through the combined action of the C-shaped support carriage and the rollers, when the cylindrical surface of the roller contacts the conveying groove, the rotation of the roller converts the sliding friction between the scraper and the conveying groove into rolling friction, effectively reducing the friction and enabling the load to be evenly distributed along the contact surface.

[0015] 3. The chute end cover, carriage, rollers, etc. of the present invention can all be quickly disassembled and assembled. When the rollers are severely worn and need to be replaced, compared with the traditional scraper, there is no need to disconnect the entire scraper chain to replace parts, nor to disassemble the spring plates on both sides of the chain drive conveying system. Just unscrew the screws from the upper end, open the chute end cover, and the damaged parts can be vertically taken out, greatly saving the downtime and ultimately increasing the service life of the scraper chain. BRIEF DESCRIPTION OF THE DRAWINGS

[0016] The following will further elaborate on the specific embodiments of the present invention through the drawings.

[0017] Figure 1 It is a schematic structural diagram of a set of scraper structures of the present invention.

[0018] Figure 2 It is an exploded view of the scraper structure of the present invention.

[0019] Figure 3 It is a partial cross-sectional view of the scraper structure of the present invention; Figure 4 It is a schematic structural diagram of the grooved scraper base; Figure 5 a, Figure 5 b are respectively the side sectional view and the bottom view of the chute end cover of the present invention; Figure 6 It is a partial cross-sectional view of the roller structure of the present invention; Figure 7 It is a schematic working diagram of the present invention when used in the conveying system of an airborne mining equipment; Figure 8 It is a simulation schematic diagram of the present invention; Figure 9 It is a diagram of the angle change of the scraper at different chain speeds during the full-circle operation with the tail swing of 30°; Figure 10 It is a diagram of the angle change of the scraper during the full-circle operation at the same chain speed with different tail swing angles; Figure 11 It is a diagram of the tension change at the hinge of the scraper during the full-circle operation with the tail swing of 30° and the chain speed of 0.9 m / s; Figure 12 It is a diagram of the tension change at the hinge of the scraper during the full-circle operation with the tail swing of 30° and the chain speed of 2.1 m / s; Figure 13 It is a comparison diagram of the swing angle change of the scraper during the cyclic operation with the tail swing of 45° and the chain speed of 1.7 m / s; Figure 14It is a comparison chart of the tension change at the hinge joint of the scraper running in a cycle with a chain speed of 1.7 m / s and a tail swing angle of 45°.

[0020] In the figure: 1 - Slotted scraper base, 2 - Outer knuckle joint, 3 - Inner knuckle joint, 4 - Chain link, 5 - Pin shaft, 6 - Spring plate Ⅰ, 7 - Spring plate Ⅱ, 8 - Bottom plate of the middle conveying trough, 9 - Spring plate pressing plate, 10 - Bottom plate of the tail conveying trough, 11 - Compensation plate, 12 - Motor reducer, 13 - End cover of the chute, 14 - Screw, 15 - Spring fixing seat, 16 - Spring, 17 - Slide carriage, 18 - Fixed shaft, 19 - Snap ring, 20 - Dust-proof ring, 21 - Bearing, 22 - Roller, 23 - Discharge hole, 24 - Lower chute, 25 - Threaded hole, 26 - Upper chute, 27 - Countersunk head seat for the end cover, 28 - First step, 29 - Second step, 30 - Relief groove. Detailed implementation manners

[0021] Next, the technical solutions in the embodiments of the present invention will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present invention. Obviously, the described embodiments are only a part of the embodiments of the present invention, rather than all the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present invention.

[0022] Embodiment: This embodiment provides a scraper structure for an airborne swing-type scraper conveyor, which is applied to the scraper chain of short-distance swing conveying equipment such as a roadheader-anchor rig, a continuous miner, and a roadheader. While overcoming the technical disadvantages of the existing equipment chain drive conveying system during swing operation, the reliability and service life of the scraper chain drive conveying system used on the equipment are improved. This embodiment will be described in detail by taking the chain drive conveying system applied to a roadheader-anchor rig as an example.

[0023] As Figure 1 shown, the scraper structure of the present invention is applied to the scraper chain of the conveying system of an airborne mining equipment. The scraper chain includes a scraper structure, an outer knuckle joint 2, an inner knuckle joint 3, a chain link 4, and a pin shaft 5. The scraper structure is connected to two outer knuckle joints 2 through a plurality of pin shafts 5. The outer knuckle joint 2 and the inner knuckle joint 3 form a cross chain link, and then are connected to the chain link 4 through a plurality of pin shafts 5. Finally, a set of scraper chains formed is a unit, and the complete conveying system is composed of a plurality of units connected end to end.

[0024] As Figures 2 to 7As shown in the figure, the scraper structure for an airborne swing scraper conveyor includes a grooved scraper base 1, a carriage 17, and a roller assembly. A carriage mounting structure is provided at the end of the grooved scraper base 1. The carriage 17 is slidably disposed in the carriage mounting structure. A spring 16 is provided between the carriage 17 and the carriage mounting structure to drive the carriage 17 to move away from the grooved scraper base 1. Specifically, the carriage mounting structure includes a chute end cover 13 and a lower chute 24 provided on the grooved scraper base 1. The end of the grooved scraper base 1 is provided with a first step 28 and a second step 29 with decreasing height. The lower chute 24 is provided on the upper end surface of the second step 29. The carriage 17 is a C-shaped support carriage. The lower end of the carriage 17 is placed in the lower chute 24 and is slidably engaged with the lower chute 24.

[0025] The chute end cover 13 is provided on the grooved scraper base 1. An upper chute 26 corresponding to the lower chute 24 is provided on the chute end cover 13. The carriage 17 is located between the upper chute 26 and the lower chute 24. The upper end of the carriage 17 is located in the upper chute 26. The maximum movement stroke of the carriage 17 is limited by the length of the upper chute 26 or the lower chute 24.

[0026] The roller assembly is provided on the carriage 17. When the roller assembly contacts the spring plate I 6 and the spring plate II 7, the pressure is transmitted to the spring 16 through the carriage 17. The spring 16 is compressed, and the carriage 17 and the roller assembly move inward along the chute.

[0027] A slag discharge hole 23 is provided on the side wall of the lower chute 24 along the sliding direction of the carriage 17. There is a possibility that slag may fall into the chute when the carriage 17 moves. When the spring 16 resets, the carriage 17 will also reset and push the slag to the end. The slag discharge hole 23 can achieve the overflow of slag materials during scraper transportation, avoiding the accumulation of coal slag materials and affecting the normal movement of the carriage.

[0028] To facilitate the disassembly, assembly, and positioning of the chute end cover 13, a threaded hole 25 is provided on the upper end surface of the first step 28. The chute end cover 13 is provided with an end cover countersunk seat 27 corresponding to the threaded hole 25. The end cover countersunk seat 27 and the threaded hole 25 are connected by a fastening screw 14. The screw head of the fastening screw 14 is completely sunk into the end cover countersunk seat 27 of the chute end cover 13, so that the upper surface of the chute end cover 13 is flush with the upper surface of the scraper structure.

[0029] The bends of the carriage 17 are all 90-degree right angles, and the upper and lower edges are circular, with dimensions matching the corresponding upper chute and lower chute. Side baffles are provided on both sides of the chute end cover 13 to enclose the first step 28 within the side baffles.

[0030] A relief groove 30 is provided along the chute direction on the side of the first step 28. A spring fixing seat 15 is fixedly connected to the rear end of the C-shaped support carriage. The spring fixing seat 15 is in the shape of a stepped cylindrical boss, with screw holes on the side and bottom. The height of the inner diameter boss is shorter than the spring compression stroke. The spring is inserted into the inner diameter boss and fixed against detachment by screws. The spring fixing seat can be welded to the middle position of the C-shaped support carriage or connected to the C-shaped support carriage by screws. The spring 16 is located in the relief groove 30 and, in cooperation with the chute end cover 13, can protect the spring 16.

[0031] The roller assembly includes a fixed shaft 18, rollers 22 and bearings 21. Through holes are provided at the upper and lower ends of the carriage 17. The fixed shaft 18 is inserted into the through holes of the carriage 17. The length of the fixed shaft is the same as the distance between the upper and lower end faces of the C-shaped support carriage to ensure the normal sliding of the carriage. The rollers 22 are arranged on the fixed shaft 18 through two bearings 21 and are axially limited with the two bearings 21. On the side where the two bearings 21 are away from each other, they are axially limited with the fixed shaft 18 through a circlip 19. A dust-proof ring 20 is provided between the bearing 21 and the circlip 19.

[0032] The rollers 22 are cylindrical, with the upper and lower edges processed into arcs. When the cylindrical surface contacts the conveying groove, the contact area increases, enabling the load to be evenly distributed along the contact surface. The rollers convert the sliding friction between the scraper and the conveying groove into rolling friction, reducing friction and greatly minimizing the running resistance.

[0033] A complete set of the above components is installed on both wings of the scraper structure to achieve the same effect when swinging left and right.

[0034] Simulation experiment: Simulation test working condition table The corresponding relationship between the above boundary condition settings and the working condition numbers is illustrated by taking working condition 3 as an example: The initial swing angle of the scraper tail is 45°. The tensioning displacement function is defined as: step(time, 0, 0, 0.5, 144), that is, when the tail swings, the compensation and tensioning displacement of the driving sprocket along the conveying direction is 144 mm. The speed function is defined as step(time, 0.5, 0, 2.5, 7.8), that is, the rotational speed of the driving sprocket is 7.8 rad / s, and the corresponding chain speed of the scraper chain is 0.9 m / s. The simulation setting duration is 23 s, and the total number of steps is 400 steps. Similarly, there is a corresponding relationship between the definitions of the remaining functions and the working condition numbers.

[0035] Set the scraper to run in a cycle for at least two complete cycles to obtain enough stable data for analysis. At this time, the simulation duration is only related to the chain speed. Combining the time used in the acceleration section of the conveyor and the chain speed and the length of the conveying trough, the required simulation durations are obtained as follows: the simulation setting duration at a chain speed of 0.9 m / s is 23 s, the simulation setting duration at a chain speed of 1.3 m / s is 17.5 s, the simulation setting duration at a chain speed of 1.7 m / s is 15 s, and the simulation setting duration at a chain speed of 2.1 m / s is 13 s.

[0036] 1. Analysis of scraper yaw during multi-condition operation: Figure 9 And Figure 10 They are respectively the data analysis of the angle change of the target scraper during the interaction between the target scraper and the swinging conveying trough within a stable cycle of the whole week of operation of the two types of scrapers. Among them, each numbered scraper chain of the research object runs a complete week in the chain path, and the simulation test acquisition step size is the same.

[0037] Figure 9 It is a comparison diagram of the rotation of the scraper when the two scraper models run in a full week at different chain speeds under the same tail swing angle. The corresponding working conditions are working conditions 11, 23 and working conditions 2, 14. At a chain speed of 2.1 m / s, the No. 6 scraper starts to move at 0 s, enters the swinging bending section at 1.9 s, and the total trend of the scraper angle gradually deflects to 30°. By 3.1 s, it enters the straight section and maintains the coordinate orientation. Then, after passing through the chain return journey, it enters the swinging bending section again and deflects to 60°. Finally, it returns to the upper chain path through the redirecting roller and the coordinate returns to zero. The change law principle of the 0.9 m / s chain speed is the same as this.

[0038] Comparing the two types of scrapers from the perspective of the rotation angle, taking the change law of the 2.1 m / s chain speed as an example, the angle deflection of the scraper chain in the swinging bending section is due to the friction and scraping between the side wing of the scraper and the spring plate and the trough side. After getting stuck, the scraper will continue to run at the original speed, causing the scraper to deflect and swing violently. At 2.5 s, the relative angle change of the No. 6 scraper exceeds 15.2°, and the yaw angle fluctuates significantly; at a similar position, the yaw angle change of the No. 6 optimized new scraper is only 1.8°, effectively suppressing the sudden change of the angle. Comparing the two types of scrapers from the perspective of the chain speed, when the chain speed rises from 0.9 m / s to 2.1 m / s, the prototype scraper is more sensitive to the influence brought by the change of the chain speed. The average rotation change of the No. 24 scraper in the swinging bending section at a chain speed of 0.9 m / s is 8.7°. When the chain speed rises to 2.1 m / s, the value rises to 12.0°, and the value change is about 1.4 times; after adopting the new scraper, the increase of the chain speed instead makes the scraper operation more stable. The rollers on both wings of the new scraper play a role in reducing resistance and stabilizing, alleviating the scraping and jamming compared with the prototype scraper, and the optimization effect is significant.

[0039] Figure 10For the same running chain speed, taking the chain speed of 2.1 m / s as an example, it is a comparison diagram of the rotation of two scraper models when running full circle at different swing angles. The simulation swing angles of 45° and 30° correspond to working conditions 12, 24 and working conditions 11, 23 respectively.

[0040] Analyzing the two scrapers from the perspective of variable swing angle, at a chain speed of 2.1 m / s, the prototype scraper causes the scraper to swing evenly due to scraping. The swing amplitude of the 30° swing in working condition 10 is more uniform and stable than that of the 45° swing in working condition 12. The peak value of the scraper angle in working condition 10 is the largest, with a difference exceeding 18.3°. The reason is that as the swing angle increases, the required tension ∆S of the scraper chain responds more strongly, and the rotation arc increases, resulting in the side wing of the scraper being closely attached to and scraping against the spring plate of the conveying trough. The existence of scraping intensifies the impact on the scraper and the spring plate of the trough side, which is then reflected in the deflection of the scraper. The new type of scrapers No. 6 and No. 24 under both swing angles can suppress the scraping of the scraper, converting the sliding friction of the side wing of the scraper into rolling friction, significantly reducing the deflection of the scraper. Overall comparison shows that as the swing angle increases, the new type of scraper is slightly affected, and the deflection swing amplitude of the prototype scraper shows a positive correlation with the change of the swing angle.

[0041] 2. Analysis of the change in scraper tension during multi-condition operation: Figure 11 and Figure 12 They are respectively the analysis of the change law of the tension at the hinge of the scraper and the corresponding scraper operation morphological characteristics when the target scraper interacts with the swinging conveying trough during one cycle of the full-circle operation of the two scrapers. The target scraper is selected as the scraper on the upper chain path near the head end to observe the operation state of the scraper during the simulation process and extract data.

[0042] From Figure 11 it can be analyzed that the working condition is the comparison of the change trend of the tension at the hinge during the operation cycle of the two scrapers and the morphology of the scraper chain at special positions with a chain speed of 0.9 m / s and a tail swing angle of 30°. As shown in Figure 11 (a), it can be seen from the overall trend that at low chain speeds, due to the small scraping impact of the scraper chain, the change trends of the tensions of the two scrapers are almost the same, and the overall tension value of the new type of scraper is slightly lower than that of the prototype scraper chain. Combining Figure 11 (b) shows that: at 3.04 s and 3.56 s, the sudden change values of the tension are 1949.04 N and 5847.17 N respectively, and the corresponding scraper morphologies show a "V-shaped chain" and a "parallelogram chain"; at 3.56 s, for the new type of scraper compared with the prototype scraper, its two-wing rollers play a key role. The rollers are in full contact with the spring plate of the chain path and smoothly transition, and the internal spring makes the tension change more evenly. When the prototype scraper contacts the spring plate, the resistance at the wing tip increases instantaneously, the tension at the hinge of the scraper increases, and the scraper morphology shows an inclined state.

[0043] Analysis Figure 12(a)Tension variation at the hinge of the scraper during full - circle operation with a chain speed of 2.1 m / s and a tail swing angle of 30°, comparison Figure 11 (a)It can be seen that when the chain speed increases to the rated chain speed of 2.1 m / s, the tension of the prototype scraper chain varies from the range of 2000 N - 4000 N to 4000 N - 9000 N, while the tension of the new - type scraper only increases to 3000 N - 5000 N; combined with Figure 12 (b)The data of the scraper deflection angle when the target scraper enters the swing area of the upper chain path can be intuitively observed Figure 12 (c)As shown: at 2.14 s, the prototype scraper shows a "V - shaped chain", at 2.33 s, it shows an "S - shaped twisting chain", at 2.51 s, it shows a "parallelogram - shaped chain", and at 2.67 s, it shows an "inverted V - shaped chain"; comparison Figure 12 (d)For the running state of the new - type scraper chain, during the running process of the scraper, the new - type scraper chain moves evenly to the tail of the machine. The rollers on both wings of the scraper are in full contact with the spring plate of the curved chain path, and the shape of the scraper shows an ideal "fan - shaped" structure; as Figure 12 (a)shown, the tension fluctuation at the hinge of the 6th new - type scraper in the upper chain path is 3000 N - 5000 N, while at the hinge of the 6th prototype scraper, there are peak values at numbers 3, 4, and 6, and the maximum peak value reaches 14950.24 N. This peak value causes excessive impact on the scraper and the chain links, affecting the safe operation of the scraper chain.

[0044] 3. Discussion on the dynamic characteristic law of the circulating - motion scraper: Figure 13 and Figure 14 are the comparison diagrams of the scraper angle change and the tension change at the scraper hinge when the target scraper and the swing conveyor trough interact during two stable cycles of the two - type scraper circulation operation. Among them, each numbered scraper chain of the research object runs completely in the chain path for two weeks, and the simulation test acquisition step size is the same. The most suitable chain - speed range value is 1.7 m / s, and the working conditions related to a chain speed of 1.7 m / s are selected as an example for analysis.

[0045] Figure 13 and Figure 14 both correspond to working conditions 9 and 21, with a tail swing angle of 45° (limit swing angle), a chain speed of 1.7 m / s, the target scraper numbered 6, and the simulation corresponding duration of 15 s. During the first cycle, the 6th scraper experiences 2.5 seconds for the conveying chain to accelerate to the predetermined chain speed, then passes through the swing section of the upper chain path, the running direction of the scraper rotates 45 degrees, passes through the driving sprocket and enters the return journey of the lower chain path, rotates 45 degrees again through the swing - bending section of the lower chain path, and completes the first cycle through the redirecting roller; in the second cycle, there is only no acceleration section and it circulates again in the same way.

[0046] Comparison of the deflection - angle change of the 6th scraper at the same position between the prototype scraper chain and the new - type scraper chain is as Figure 13Analysis shows that when the scraper enters the swing section, the change in the deflection angle of the new scraper is almost positively correlated with the running time; the dynamic characteristics of the same type of scraper in periodic cyclic operation have a periodic change pattern; within the same cycle, the deflection laws of the same type of scraper on the upper and lower chain channels are the same. The prototype scraper shows an oscillating deflection law in the swing section. In contrast, the new scraper has a significant inhibitory effect. Combined with the comparison of the tension changes at the hinge of the No. 6 scraper at the same position of the prototype scraper chain and the new scraper chain as Figure 14 Analysis shows that due to the decrease in the tension of the scraper in the return section of the lower chain channel, the scraping force between the scraper and the spring plate is more likely to cause abnormal deflection of the scraper. Therefore, when the scraper runs to the swing section of the lower chain channel, the deflection amount of the scraper is greater than that in the swing section of the upper chain channel; as the scraper runs to the driving sprocket end, the tension at the hinge of the scraper increases accordingly; due to the scraping of the scraper in the swing section, there are multiple sudden change peaks in the tension change. Under multi-cycle comparison, the tension at the hinge during the operation of the new scraper chain is generally less than that of the prototype scraper chain. The two-wing rollers reduce the tension at the hinge to about 3000 N, which not only solves the scraping problem but also greatly reduces the possibility of chain breakage and improves the operation stability.

[0047] 4. Conclusion: (1) During the full-cycle operation, when the prototype scraper runs to the swing bending section, as the chain speed increases, the phenomenon of the scraper flank sticking to the conveyor trough spring plate becomes more severe, and the deflection fluctuation becomes more significant; there is a positive correlation between the deflection amplitude and the swing angle change of the prototype scraper; the two-wing rollers of the new scraper are in full contact with the chain channel spring plate, converting the sliding friction of the scraper flank into rolling friction, effectively reducing the deflection amount of the scraper.

[0048] (2) During the tail swing operation, the entire scraper chain in the swing bending section runs along an arc. The trajectory of the prototype scraper chain shows an "S-shaped twisting chain" distribution, and the scrapers show an "inner and outer eight-shaped" and "parallelogram-shaped" distribution. The new scraper shows an ideal "fan-shaped" distribution; the flank of the scraper is closely attached to the spring plate and is greatly affected by the swing angle. There are many sudden change values in the tension at the hinge of the prototype scraper, while the tension change at the hinge of the new scraper fluctuates relatively stably.

[0049] (3) The new scraper is installed with a slidable roller rotating mechanism on both wings. The rollers and the slidable brackets are both detachable for easy maintenance; the sliding friction between the two wings of the scraper and the trough side is converted into rolling friction. When colliding with the spring plate, the internal spring of the mechanism effectively buffers the shock, and the combined action reduces the impact and resistance during the operation.

[0050] Only the preferred embodiments of the present invention have been described in detail above. However, the present invention is not limited to the above embodiments. Within the scope of knowledge possessed by those of ordinary skill in the art, various changes can be made without departing from the purpose of the present invention, and all such changes should be included within the protection scope of the present invention.

Claims

1. A scraper structure for an airborne swing-type scraper conveyor, characterized in that: It includes a grooved scraper base (1), a carriage (17) and a roller assembly. A carriage mounting structure is provided at the end of the grooved scraper base (1). The carriage (17) is slidably arranged in the carriage mounting structure. A spring (16) for driving the carriage (17) to move away from the grooved scraper base (1) is provided between the carriage (17) and the carriage mounting structure. The roller assembly is arranged on the carriage (17). The carriage mounting structure includes a chute end cover (13) and a lower chute (24) provided on the grooved scraper base (1). The chute end cover (13) is detachably arranged on the grooved scraper base (1). An upper chute (26) corresponding to the lower chute (24) is provided on the chute end cover (13). The carriage (17) is located between the upper chute (26) and the lower chute (24) and is slidably limited and stroke-limited by the upper chute (26) and the lower chute (24).

2. The scraper structure for an airborne swing-type scraper conveyor according to claim 1, characterized in that: A first step (28) and a second step (29) with a decreasing height are provided at the end of the grooved scraper base (1). The lower chute (24) is arranged on the upper end surface of the second step (29). A relief groove (30) is arranged on the side surface of the first step (28) along the direction of the lower chute (24). The spring (16) is located in the relief groove (30).

3. The scraper structure for an airborne swing-type scraper conveyor according to claim 2, characterized in that: A threaded hole (25) is provided on the upper end surface of the first step (28). The chute end cover (13) is provided with an end cover counterbore seat (27) corresponding to the threaded hole (25). The end cover counterbore seat (27) and the threaded hole (25) are connected by a fastening screw (14). Side baffles are provided on both sides of the chute end cover (13).

4. The scraper structure for an airborne swing-type scraper conveyor according to claim 1, characterized in that: The carriage (17) is a C-shaped support carriage. A spring fixing seat (15) is fixedly connected to the rear end of the C-shaped support carriage. The spring (16) is arranged on the spring fixing seat (15).

5. The scraper structure for an airborne swing-type scraper conveyor according to claim 1, characterized in that: The roller assembly includes a fixed shaft (18), a roller (22) and a bearing (21). The fixed shaft (18) is arranged on the carriage (17). The roller (22) is arranged on the fixed shaft (18) through two bearings (21). One side of the two bearings (21) away from each other is axially limited to the fixed shaft (18) by a circlip (19). A dust-proof ring (20) is arranged between the bearing (21) and the circlip (19).

6. The scraper structure for an airborne swing-type scraper conveyor according to claim 1, characterized in that: A slag discharge hole (23) is arranged on the side wall of the lower chute (24) along the sliding direction of the carriage (17).

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