A scalable multi-station belt conveyor

Abstract

The application discloses a telescopic multi-station belt conveyor and relates to the technical field of conveyors. The telescopic multi-station belt conveyor comprises a first conveying line, a telescopic conveying line and a distribution unit. The telescopic conveying line is composed of a walking mechanism and a second conveying line. The distribution unit is provided with an inner shaft, an outer cylinder and a matched plough inside a storage bin. Power of a single driving mechanism is distributed through a planetary gear set to form an up-down differential reverse shearing flow field. Meanwhile, the plough is radially telescopic through an eccentric track and elastic members. Air flow assisting and pre-crushing buffer structures are matched to optimize operation performance. The application can realize multi-station continuous feeding and self-adaptive arch breaking operation, solves the problems of poor station adaptability of traditional equipment, blind area of arch breaking and easy blockage of materials, and is suitable for conveying of bulk materials such as coal, quartz sand and iron ore. Operation efficiency and stability are significantly improved.

Description

Technical Field

[0001] This invention relates to the field of conveyor technology, specifically a retractable multi-station belt conveyor. Background Technology

[0002] In the field of bulk material transportation in mining and industrial production, coal, quartz sand, and iron ore are commonly used materials. These materials generally have the characteristics of large particle size variation, uneven moisture content, and strong compaction properties.

[0003] During continuous conveying, storage, distribution and unloading processes, it is easy for material to be squeezed, arched, bridged and blocked inside the silo. The smoothness and uniformity of material flow directly determine the overall efficiency and production stability of the multi-station distribution operation of the conveyor. For example, the "multi-station belt conveyor head telescopic device" with publication number CN203997802U, although it realizes the functions of multi-station unloading and conveyor line telescopic, its silo part only undertakes the simple functions of material storage and guiding, which can easily cause serious accumulation of material inside the silo. Summary of the Invention

[0004] The purpose of this invention is to provide a retractable multi-station belt conveyor to solve the problems mentioned in the prior art.

[0005] To achieve the above objectives, the present invention provides the following technical solution: a retractable multi-station belt conveyor, comprising a first conveyor line, a retractable conveyor line, and a distribution unit; The telescopic conveyor line includes a traveling mechanism and a second conveyor line, the second conveyor line being connected to the traveling mechanism; The distribution unit includes a hopper, a drive mechanism, and a plow blade. The hopper is provided with an inlet and an outlet and is mounted on a traveling mechanism. The drive mechanism is installed on the hopper, and an inner shaft is connected to the output end of the drive mechanism. An outer cylinder is sleeved on the inner shaft near the hopper inlet. The outer cylinder is rotatably mounted on the hopper. The inner shaft and the outer cylinder are connected by a planetary gear set for transmission. Both the inner shaft and the outer cylinder are provided with a number of mounting cylinders, and each mounting cylinder is equipped with an arch-breaking shaft, and the plow blade is mounted on the arch-breaking shaft.

[0006] The planetary gear set is a single-stage planetary gear system, in which the sun gear is connected to the output end of the drive mechanism, the planet carrier is installed on the hopper, and the gear ring is installed on the inner wall of the outer cylinder. At this time, the sun gear serves as the power input end, the planet carrier serves as the fixed end, and the gear ring serves as the power output end.

[0007] The hopper is equipped with tracks at positions corresponding to the inner shaft and outer cylinder. A sealing ring is rotatably installed on the inner side of the track, and the track is eccentrically positioned relative to the inner shaft. One end of the arch-breaking shaft forms a sliding seal connection with the mounting cylinder, and the other end of the arch-breaking shaft passes through the sealing ring and is provided with rollers, which roll in the track. An elastic element connects the arch-breaking shaft and the mounting cylinder.

[0008] The arch-breaking shaft and the sealing ring are connected by a sliding seal through a sealing ring and a sealing gasket.

[0009] The inner shaft and the arch-breaking shaft on the inner shaft are both equipped with air supply channels. The two air supply channels are connected by a telescopic hose. The arch-breaking shaft on the inner shaft is equipped with several air jet holes facing the outlet of the hopper. The inlet of the air supply channel is connected to the air supply system, and the outlet of the air supply channel is connected to the air jet holes.

[0010] The air supply system includes an air pump and a rotary joint. The rotary joint is sleeved on the inner shaft and installed on the hopper. The inlet of the rotary joint is connected to the air pump, and the outlet of the rotary joint is connected to the air supply channel inside the inner shaft. The rotary joint is sleeved on the inner shaft and fixed to the hopper, forming a dynamic air seal between the fixed end of the air pump and the rotating end of the inner shaft, allowing the pressurized airflow to be continuously and stably delivered without leakage while the inner shaft is rotating continuously. The air pump is located on the hopper. The arch-breaking shaft on the outer cylinder is not supplied with air.

[0011] The plow blade has a trapezoidal cross-section, with the upper base being shorter than the lower base. The upper base is positioned adjacent to the mounting cylinder, while the lower base is positioned away from the mounting cylinder. The plow blade is made by spiral twisting.

[0012] When the plow blade rotates in opposite directions, both directions maintain a stable cutting rake angle, and during the cutting process, it generates a synergistic effect of axial pushing and loosening on the material. It is suitable for breaking up arches of materials with high hardness and easy arching, such as coal, quartz sand, and iron ore.

[0013] The plow blade is equipped with several arch-breaking blades.

[0014] The arch-breaking piece has serrated blades on both sides.

[0015] A material passage gap is formed between adjacent arch-breaking plates. The arch-breaking plates protrude outward from the surface of the plow blade. Both sides of the arch-breaking plates are provided with serrated blades, and the tips of the serrated blades on both sides are respectively facing the two rotation directions of the plow blade.

[0016] A buffer assembly is provided at the inlet of the hopper, and the buffer assembly is located above the outer cylinder; The buffer assembly includes a buffer ring, a flow divider, and a vibrator. The buffer ring is slidably mounted on the hopper. An elastic structure connects the buffer ring and the hopper. A detection element is provided on the hopper at the position corresponding to the buffer ring. Multiple flow dividers are provided, and all flow dividers are mounted on the buffer ring; The vibrator is installed on the hopper and is electrically connected to the control system. The output end of the vibrator is connected to the buffer ring.

[0017] The elastic structure includes an elastic cylinder and a buffer spring. The elastic cylinder is a telescopic structure, with its two ends connected to a buffer ring and a hopper, respectively. The buffer spring is located inside the elastic cylinder and is connected to both ends of the elastic cylinder.

[0018] The detection elements include a pressure sensor and a displacement sensor. The pressure sensor is used to detect the pressure on the buffer ring, and the displacement sensor is used to detect the displacement of the buffer ring. The pressure sensor and the displacement sensor feed the pressure data and displacement data back to the control system. The control system determines the magnitude of the material resistance based on the pressure data and displacement data, and then adjusts whether the vibrator works or the vibration frequency of the vibrator according to the magnitude of the resistance.

[0019] The flow divider plate is equipped with a flow divider blade on the side near the hopper inlet.

[0020] A flow divider blade is provided on the side of the flow divider plate near the hopper inlet. The flow divider blade extends along the length of the flow divider plate, and the cross-section of the flow divider blade is triangular. The blade edge of the flow divider blade faces upward toward the hopper inlet.

[0021] The walking mechanism includes a walking track, a walking frame, and a power unit. The walking frame is equipped with a number of walking wheels, which are in contact with the walking track. The power unit drives the walking frame to walk on the walking track. The second conveyor line is connected to the traveling frame, and the hopper is installed on the traveling frame.

[0022] The power unit includes a power motor, a reducer, a power wheel, and several power columns; Both the power motor and the reducer are mounted on the walking frame, and the output end of the power motor is connected to the drive wheel through the reducer; Several power columns are arranged on the walkway, and the power wheel meshes with several power columns.

[0023] Compared with the prior art, the beneficial effects of the present invention are: 1. A telescopic second conveyor line enables multi-station conveying, significantly reducing operation time. Driven by a traveling mechanism, the second conveyor line extends laterally, allowing for full-load material reception during operation without stopping. It can cover multiple unloading stations, replacing the traditional single-station dedicated conveyor configuration. This effectively solves the problems of traditional conveyors requiring downtime for material reception, long operation times, high investment costs for multi-station equipment, and low equipment utilization, significantly reducing operation time and lowering equipment procurement and deployment costs.

[0024] 2. Differential arch breaking prevents material accumulation. A single drive mechanism combined with a single-stage planetary gear set achieves power diversion, driving the inner shaft to rotate at high speed in the forward direction and the outer cylinder to rotate at low speed in the reverse direction. This creates a differential reverse flow field within the hopper, with low-speed loosening at the top and high-speed shearing at the bottom. Multi-dimensional material crushing can be achieved without two independent drive systems, solving the problems of material swirl, blind spots in arch breaking, and incomplete agglomerate crushing inherent in traditional unidirectional arch breaking methods. This ensures uniform material particle size and maintains a stable material flow balance.

[0025] 3. A buffer assembly with a flow divider is installed at the hopper inlet, combined with pressure and displacement dual-sensor detection and an adaptive vibration adjustment structure. The flow divider pre-crushes large materials, while the elastic structure buffers the impact of materials, and vibration is activated as needed to prevent blockage. This solves the problems of concentrated material impact, easy bridging and blockage at the inlet, and overload and jamming caused by large particles, protecting the transmission structure and reducing equipment energy consumption and wear. Attached Figure Description

[0026] Figure 1 This is a schematic diagram of the overall structure of the present invention (the hopper and the inner shaft are concentrically arranged); Figure 2 This is a schematic diagram of the structure of the second conveyor line in this invention; Figure 3 This is a schematic diagram of the walking frame in this invention; Figure 4 This is a schematic diagram of the structure of the silo in this invention; Figure 5 This is a schematic diagram of the buffer ring structure in this invention; Figure 6 This is a schematic diagram of the drive mechanism in this invention; Figure 7 This is a schematic diagram of the mounting cylinder in this invention; Figure 8 This is a schematic diagram of the planetary gear set in this invention; Figure 9 This is a schematic diagram of the track structure in this invention; Figure 10 This is a schematic diagram of the plow blade in this invention (the track and the inner shaft are eccentrically set); Figure 11 This is a schematic diagram of the sealing ring structure in this invention; Figure 12 This is a schematic diagram of the air supply channel in this invention; Figure 13 This is a schematic diagram of the arch-breaking piece in this invention.

[0027] In the diagram: 1. First conveyor line; 2. Telescopic conveyor line; 21. Traveling mechanism; 211. Traveling path; 212. Traveling frame; 213. Power unit; 2131. Power motor; 2132. Reducer; 2133. Power wheel; 2134. Power column; 22. Second conveyor line; 3. Distribution unit; 31. Hopper; 311. Track; 312. Sealing ring; 32. Drive mechanism; 33. Plow blade; 34. Inner shaft; 341. Mounting cylinder; 342. Air supply channel; 35. Outer cylinder; 36. Planetary gear set; 37. Arch breaking shaft; 38. Buffer assembly; 381. Buffer ring; 382. Diverter plate. Detailed Implementation

[0028] The technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] like Figures 1-8 As shown in the figure, Embodiment 1 of the present invention provides a retractable multi-station belt conveyor.

[0030] The specific content of Embodiment 1 is as follows: A retractable multi-station belt conveyor includes a first conveyor line 1, a retractable conveyor line 2, and a distribution unit 3; the retractable conveyor line 2 includes a traveling mechanism 21 and a second conveyor line 22, which is connected to the traveling mechanism 21; the distribution unit 3 includes a hopper 31, a drive mechanism 32, and a plow 33, the hopper 31 is provided with an inlet and an outlet, and the hopper 31 is mounted on the traveling mechanism 21; the drive mechanism 32 is mounted on the hopper 31, and an inner shaft 34 is connected to the output end of the drive mechanism 32. An outer cylinder 35 is sleeved on the inner shaft 34 near the inlet of the hopper 31, and the outer cylinder 35 is rotatably mounted on the hopper 31. The inner shaft 34 and the outer cylinder 35 are connected by a planetary gear set 36; a plurality of mounting cylinders 341 are provided on both the inner shaft 34 and the outer cylinder 35, and each mounting cylinder 341 is equipped with an arch-breaking shaft 37, and the plow 33 is mounted on the arch-breaking shaft 37.

[0031] The materials transported in this embodiment are coal, quartz sand, iron ore, etc.

[0032] In this embodiment, both the first conveyor line 1 and the second conveyor line 22 are belt conveyor lines driven by electric rollers. The belts in the two conveyor lines are omitted in the attached drawings.

[0033] In this embodiment, the drive mechanism 32 is a drive motor, which has a built-in encoder and pressure sensor.

[0034] In this embodiment, the walking mechanism 21 can be a conventional electric rail-guided trolley.

[0035] In this embodiment, both the inner shaft 34 and the outer cylinder 35 are concentrically arranged with the hopper 31.

[0036] In this embodiment, the planetary gear set 36 is a single-stage planetary gear system, wherein the sun gear is connected to the output end of the drive mechanism 32, the planet carrier is mounted on the hopper 31 by a bracket, and the gear ring is mounted on the inner wall of the outer cylinder 35. At this time, the sun gear serves as the power input end, the planet carrier serves as the fixed end, and the gear ring serves as the power output end.

[0037] In this embodiment, the arch-breaking shaft 37 and the mounting cylinder 341 are fixedly connected, and the end of the arch-breaking shaft 37 away from the mounting cylinder 341 is at a certain distance from the inside of the hopper 31.

[0038] The working steps of Example 1 are as follows: During operation, the traveling mechanism 21 drives the second conveyor line 22 to move towards the first conveyor line 1 until the second conveyor line 22 moves to the leftmost end of the first conveyor line 1. As the second conveyor line 22 moves to the left, the first conveyor line 1 continuously transports materials to the second conveyor line 22. As the second conveyor line 22 moves to the left, the materials are sequentially laid on the bearing surface of the second conveyor line 22, allowing the second conveyor line 22 to complete full-load material reception while moving, without having to stop and wait for material reception, thus greatly shortening the operation time.

[0039] When the second conveyor line 22 moves to the leftmost end of the first conveyor line 1, the first conveyor line 1 stops conveying materials. Then, the traveling mechanism 21 drives the second conveyor line 22 and the hopper 31 to move to the right in sequence to multiple unloading stations. The lateral movement of the traveling mechanism 21 enables one set of conveying equipment to cover multiple unloading stations, saving the equipment investment of configuring a fixed conveyor line for each station separately. When the hopper 31 reaches the unloading station, the traveling mechanism 21 stops traveling, and the second conveyor line 22 starts working. The second conveyor line 22 drives the material to be transported towards the inlet of the hopper 31, and the material enters the hopper 31 through the inlet.

[0040] When the material enters the silo 31, the second conveyor line 22 feeds the displacement data back to the control system. The control system controls the drive mechanism 32 to start synchronously. The output end of the drive mechanism 32 directly drives the inner shaft 34 to rotate in the forward direction at the first speed. The inner shaft 34 drives the arch-breaking shaft 37 and the plow blade 33 to rotate synchronously at high speed through the mounting cylinder 341. The plow blade 33 performs high-frequency cutting on the falling material in the lower area of ​​the silo 31. The inner shaft 34 simultaneously drives the sun gear in the planetary gear set 36 to rotate. The sun gear drives the planetary gears to rotate around the planetary carrier fixed to the hopper 31. The planetary gears drive the outer gear ring to rotate. Since the planetary carrier is fixed and the gear ring has more teeth than the sun gear, the gear ring outputs at a speed lower than the sun gear and in the opposite direction to the sun gear. The gear ring drives the outer cylinder 35 to rotate synchronously in the opposite direction at a low speed, so that the outer cylinder 35 rotates in the opposite direction at a second speed lower than the inner shaft 34. The outer cylinder 35 drives the arch-breaking shaft 37 and the plow blade 33 to rotate in the opposite direction in the upper region of the hopper 31 through the mounting cylinder 341. Thus, through a single drive mechanism 32, the power is split through the planetary gear set 36, and both high-speed forward and low-speed reverse rotations are output simultaneously. A differential reverse shear flow field with low-speed reverse rotation in the upper part and high-speed forward rotation in the lower part can be constructed in the hopper 31 without two independent drive systems.

[0041] The material entering the hopper 31 is first loosened and pre-crushed by the upper low-speed reverse plow blade 33. The upper plow blade 33 cuts into the arched compaction zone with high torque without causing material to fly or swirl. After the clumps are initially broken up, they fall to the lower area and are then refined by the high-frequency cutting of the lower high-speed forward plow blade 33. Under the action of the speed gradient of the two sets of plow blades 33, the material is repeatedly torn and sheared, and the arched clumps are fully broken into loose material with uniform particle size. This fundamentally avoids the material swirl and arch-breaking blind zone that is easily formed by unidirectional stirring. At the same time, the circumferential disturbance of the upper plow blade 33 and the shearing action of the lower plow blade 33 work together to keep the material in a flow balance of "upstream loosening and downstream fast discharge". The crushed material gathers towards the outlet of the hopper 31 under the action of gravity and the downward pushing action of the lower plow blade 33, and is continuously discharged from the outlet of the hopper 31 to the unloading station.

[0042] During the aforementioned arch-breaking process, the encoder and pressure sensor built into the drive mechanism 32 collect the rotational speed, angular displacement, and pressure signals of the inner shaft 34 in real time. When the hardness of the material arch increases, causing the load on the inner shaft 34 to increase, the rotational speed to decrease, or the pressure to increase, the control system increases the output torque of the drive mechanism 32 accordingly, so that the differential ratio output by the planetary gear set 36 is maintained within the preset range, ensuring the stability of the arch-breaking shear force. When a decrease in load is detected, the control system automatically reduces the rotational speed of the drive mechanism 32 to operate in energy-saving mode, realizing adaptive arch-breaking for materials with different hardness such as coal, quartz sand, and iron ore.

[0043] After the material distribution at the current unloading station is completed, the second conveyor line 22 stops conveying, the drive mechanism 32 stops after a delay, and the traveling mechanism 21 drives the second conveyor line 22 and the hopper 31 to continue moving to the right to the next unloading station, repeating the above feeding and arch breaking actions. Through the traveling mechanism 21, the second conveyor line 22 passes through multiple unloading stations in sequence, realizing continuous material conveying and distribution at multiple stations.

[0044] like Figures 9-12As shown, Embodiment 2 of the present invention is a further optimized design based on Embodiment 1. The difference is that the setting of the arch-breaking shaft 37 is changed so that the arch-breaking shaft 37 drives the plow blade 33 to move radially, thereby improving the arch-breaking effect.

[0045] The specific details of Embodiment 2 are as follows: The hopper 31 is provided with a track 311 at the positions corresponding to the inner shaft 34 and the outer cylinder 35. A sealing ring 312 is rotatably provided on the inner side of the track 311. The track 311 and the inner shaft 34 are eccentrically arranged. One end of the arch-breaking shaft 37 forms a sliding seal connection with the mounting cylinder 341. The other end of the arch-breaking shaft 37 passes through the sealing ring 312 and is provided with a roller. The roller rolls in the track 311. An elastic element is connected between the arch-breaking shaft 37 and the mounting cylinder 341.

[0046] In this embodiment, the arch-breaking shaft 37 and the sealing ring 312 are connected by a sealing ring and a sealing gasket to achieve a sliding sealing connection, and the sealing ring 312 rotates to seal the track 311.

[0047] In this embodiment, the elastic element is a spring.

[0048] The working steps of Example 2 are as follows: As the inner shaft 34 and outer cylinder 35 drive the arch-breaking shaft 37 to revolve, the rollers at the outer end of each arch-breaking shaft 37 roll synchronously along the track 311 with the arch-breaking shaft 37. Since the track 311 and the inner shaft 34 are eccentrically set, the distance from the roller to the central axis of the inner shaft 34 changes periodically with the revolution angle as the roller rolls along the track 311 for one revolution.

[0049] When the roller moves to the side of the track 311 away from the center of the inner shaft 34, the elastic element releases elastic potential energy to push the arch-breaking shaft 37 to extend outward radially along the mounting cylinder 341. The roller moves outward with the arch-breaking shaft 37 and always presses against the inner wall of the track 311. The plow blade 33 extends outward synchronously, and the breaking radius increases. When the roller moves to the side of the track 311 near the center of the inner shaft 34, the inner wall of the track 311 presses the roller inward, and the roller drives the arch-breaking shaft 37 to overcome the preload of the elastic element and retract inward along the mounting cylinder 341. The elastic element is compressed, and the plow blade 33 retracts inward simultaneously, reducing the breaking radius. Thus, each arch-breaking shaft 37, while revolving with the inner shaft 34 or the outer cylinder 35, performs radial reciprocating extension and retraction motion under the synergistic effect of the eccentric track 311 and the elastic element. The plow blade 33 forms a composite motion trajectory of "revolution + radial extension and retraction". Its cutting radius changes periodically with the revolution angle. The crushing coverage extends from the near-axis area to the vicinity of the inner wall of the hopper 31, eliminating the arch-breaking blind zone of the fixed radius plow blade 33 in the radial direction. The entire cross-section inside the hopper 31 is within the effective cutting range.

[0050] Because the arch-breaking shaft 37 on the inner shaft 34 and the arch-breaking shaft 37 on the outer cylinder 35 rotate in opposite directions and have different rotation speeds, and the initial phases of each arch-breaking shaft 37 on the track 311 are different, the radial extension and retraction rhythms of each plow blade 33 are staggered. At different radial positions and different circumferential angles in the hopper 31, variable radius cutting is carried out simultaneously. The material cannot form a swirl by moving synchronously with a certain plow blade 33. While the arched clumps are differentially sheared by the upper low-speed reverse plow blade 33 and the lower high-speed forward plow blade 33, they are further subjected to the squeezing impact when the plow blades extend radially and the scraping and tearing when they retract radially. They are crushed simultaneously from both circumferential and radial dimensions, and the crushing efficiency and crushing particle size uniformity are significantly improved.

[0051] like Figure 12 As shown, in Embodiment 3 of the present invention, the design is further optimized based on Embodiment 2, and a jet-assisted arch-breaking device is provided, which significantly improves the arch-breaking effect at the bottom of the silo 31 and avoids material blockage at the bottom of the silo 31.

[0052] The specific content of Embodiment 3 is as follows: The inner shaft 34 and the arch-breaking shaft 37 on the inner shaft 34 are both provided with air supply channels 342. The two air supply channels 342 are connected by a telescopic hose. The telescopic hose passes through the mounting cylinder 341. The arch-breaking shaft 37 on the inner shaft 34 is provided with several air jet holes facing the outlet of the hopper 31. The inlet of the air supply channel 342 is connected to the air supply system, and the outlet of the air supply channel 342 is connected to the air jet holes.

[0053] The air supply system in this embodiment includes an air pump and a rotary joint. The rotary joint is sleeved on the inner shaft 34 and installed on the hopper 31. The inlet of the rotary joint is connected to the air pump, and the outlet of the rotary joint is connected to the air supply channel 342 inside the inner shaft 34 through a pipe. The rotary joint is sleeved on the inner shaft 34 and fixed to the hopper 31, forming a dynamic air seal between the fixed end of the air pump and the rotating end of the inner shaft 34, so that the pressurized airflow is continuously and stably delivered without leakage while the inner shaft 34 is rotating continuously. The air pump is installed on the hopper 31. The arch-breaking shaft 37 on the outer cylinder 35 is not supplied with air.

[0054] The working steps of Example 3 are as follows: Simultaneously with the synchronous start of the drive mechanism 32, the air pump starts. The pressurized airflow output by the air pump enters the air supply channel 342 inside the inner shaft 34 through the rotary joint. The pressurized airflow flows axially along the air supply channel 342 inside the inner shaft 34, enters the air supply channel 342 inside the arch-breaking shaft 37 through the telescopic hose, and finally sprays downward from the jet hole on the arch-breaking shaft 37, forming a continuous downward airflow field below the plow blade 33. The downward airflow exerts a direct downward thrust on the bulk material after it has been crushed by the plow blade 33, overcoming the frictional resistance between the bulk particles and between the bulk material and the inner wall of the hopper 31, accelerating the flow of the bulk material to the outlet of the hopper 31, and preventing the crushed bulk material from suspending and accumulating below the plow blade 33 or in the lower part of the hopper 31 and being recompacted. This significantly improves the arch-breaking effect at the bottom of the hopper 31 and prevents the material from clogging at the bottom of the hopper 31.

[0055] During the injection process, the downward airflow simultaneously sweeps the surfaces of the plow blade 33 and the arch-breaking shaft 37, preventing fine particles such as coal, quartz sand, and iron ore from adhering to the blades of the plow blade 33 and the outer wall of the arch-breaking shaft 37, thus maintaining the cutting sharpness of the plow blade 33 and the movement flexibility of the arch-breaking shaft 37. At the same time, the downward airflow creates a top-down airflow disturbance within the hopper 31, driving the loose material in the mechanical arch-breaking blind zone towards the outlet. This, combined with the differential reverse shearing and radial reciprocating extension and retraction of the plow blade 33, forms a synergistic effect of "mechanical arch breaking + airflow assistance," further improving the material falling speed and the continuity of discharge.

[0056] During the radial reciprocating extension and retraction of the arch-breaking shaft 37 along the eccentric track 311, the telescopic hose adaptively extends and retracts synchronously with the extension and retraction of the arch-breaking shaft 37. The length of the telescopic hose is reserved with a bending margin greater than the maximum extension and retraction stroke of the arch-breaking shaft 37, so that the air supply channel 342 of the inner shaft 34 and the air supply channel 342 of the arch-breaking shaft 37 remain continuously connected throughout the entire extension and retraction stroke, and the pressurized air supply is continuously supplied without interruption. Since the air circuit is independently connected by the telescopic hose, the gas does not pass through the fitting gap between the mounting cylinder 341 and the arch-breaking shaft 37. Only a dustproof seal is required between the mounting cylinder 341 and the arch-breaking shaft 37, which avoids the interference of the axial thrust generated by the air pressure acting on the end of the arch-breaking shaft 37 on the radial reciprocating extension and retraction motion, and also eliminates the problem of increased sliding friction caused by the air pressure opening the seal ring. The extension and retraction motion of the arch-breaking shaft 37 is only driven by the eccentric track 311 and the elastic element, and the extension and retraction rhythm is stable and reliable.

[0057] like Figures 6-12 As shown, Embodiment 4 of the present invention is a further optimized design based on Embodiment 1. The difference lies in that the cross-sectional shape and overall configuration of the plow blade 33 are changed so that the two directions of the plow blade 33 maintain a stable cutting rake angle when rotating in opposite directions, and generate a synergistic effect of axial pushing and loosening on the material during the cutting process. It is suitable for breaking the arch of materials with high hardness and easy arching, such as coal, quartz sand, and iron ore.

[0058] The specific details of Embodiment 4 are as follows: the cross-section of the plow blade 33 is trapezoidal, the length of the upper base of the trapezoid is less than the length of the lower base, the upper base of the trapezoid is located near the mounting cylinder 341, and the lower base of the trapezoid is located away from the mounting cylinder 341; the plow blade 33 is made by spiral twisting.

[0059] The working steps of Example 4 are as follows: When the drive mechanism 32 drives the inner shaft 34 to rotate at high speed in the forward direction and the outer cylinder 35 to rotate at low speed in the reverse direction, the plow blade 33 on the inner shaft 34 cuts the material with one side of the trapezoid facing it, and the plow blade 33 on the outer cylinder 35 cuts the material with the other side of the trapezoid facing it. Since the two sides of the trapezoid are symmetrically arranged, there is a suitable cutting rake angle in both forward and reverse rotation, avoiding the problem of deterioration of the cutting angle and decrease in cutting efficiency when the single-sided plow blade 33 rotates in the reverse direction. The upper base of the trapezoidal section is close to the mounting cylinder 341 and the lower base faces outward, so that the cutting width of the plow blade 33 gradually increases from the root to the end. When rotating, the cutting coverage of the end with a higher linear velocity is wider, and the cutting width of the root with a lower linear velocity is narrowed to reduce rotational resistance. The cutting load is distributed more evenly along the radial direction.

[0060] like Figure 13 As shown, Embodiment 5 of the present invention is a further optimized design based on Embodiment 4. The difference is that several arch-breaking blades are added to the plow blade 33 so that the plow blade 33 forms multi-blade intermittent crushing on the basis of continuous cutting of the trapezoidal body, thereby further improving the crushing efficiency of dense arched clumps.

[0061] The specific content of Embodiment 5 is as follows: a plurality of arch-breaking blades are provided on the plow blade 33; both sides of the arch-breaking blades are provided with serrated blades.

[0062] In this embodiment, a material passage gap is formed between adjacent arch-breaking plates. The arch-breaking plates protrude outward from the surface of the plow blade 33. Both sides of the arch-breaking plates are provided with serrated blades, and the tips of the serrated blades on both sides are respectively facing the two rotation directions of the plow blade 33.

[0063] The working steps of Example 5 are as follows: As the plow blade 33 revolves with the arch-breaking shaft 37, each arch-breaking blade sequentially cuts into the arched clump. The serrated edges on both sides of the arch-breaking blade are adapted to the forward rotation of the inner shaft 34 and the reverse rotation of the outer cylinder 35, respectively, generating multi-point compression and tearing action on the clump. Under the alternating action of the continuous shearing surface and the multi-point serrated edges, the clump is quickly decomposed into smaller particles. The material passage gap between adjacent arch-breaking blades allows the crushed material to pass through in time, avoiding the material from spinning synchronously with the plow blade 33. At the same time, it reduces the overall pushing area of ​​the plow blade 33, reducing the rotational resistance and the load on the drive mechanism 32. Since the inner shaft 34 and the outer cylinder 35 rotate in opposite directions and have different speeds, the arch-breaking blades on the upper and lower layers of plow blades 33 form an interlaced multi-point cutting grid in the hopper 31. The clump is impacted by at least one arch-breaking blade at any position, completely eliminating the cutting blind zone.

[0064] like Figures 5-6 As shown, in Embodiment Six of the present invention, the design is further optimized based on Embodiment One. The difference is that a buffer component 38 is added at the inlet position of the hopper 31 to buffer and divert the material entering the hopper 31 from the second conveyor line 22, so as to avoid the material from concentrating and impacting the upper area of ​​the outer cylinder 35, and at the same time prevent the material from bridging and blocking at the inlet.

[0065] The specific content of Embodiment Six is ​​as follows: A buffer assembly 38 is provided at the inlet position of the hopper 31, and the buffer assembly 38 is located above the outer cylinder 35; the buffer assembly 38 includes a buffer ring 381, a flow divider 382 and a vibrator. The buffer ring 381 is slidably installed on the hopper 31, and an elastic structure connects the buffer ring 381 and the hopper 31. A detection element is provided on the hopper 31 at the position corresponding to the buffer ring 381; multiple flow dividers 382 are provided, and multiple flow dividers 382 are installed on the buffer ring 381; the vibrator is installed on the hopper 31, and the vibrator is electrically connected to the control system. The output end of the vibrator is connected to the buffer ring 381.

[0066] The elastic structure in this embodiment (not shown in the figure) includes an elastic cylinder and a buffer spring. The elastic cylinder is a telescopic structure. Both ends of the elastic cylinder are connected to the buffer ring 381 and the hopper 31, respectively. The buffer spring is set inside the elastic cylinder and connected to both ends of the elastic cylinder.

[0067] In this embodiment, the detection elements include a pressure sensor and a displacement sensor. The pressure sensor is used to detect the pressure on the buffer ring 381, and the displacement sensor is used to detect the displacement of the buffer ring 381. The pressure sensor and the displacement sensor feed back the pressure data and displacement data to the control system. The control system determines the magnitude of the material resistance based on the pressure data and displacement data, and then adjusts whether the vibrator works or the vibration frequency of the vibrator based on the magnitude of the resistance.

[0068] The working steps of Example 6 are as follows: After the second conveyor line 22 conveys the material to the inlet of the silo 31, the material first falls onto the buffer ring 381 and the diverter plate 382. Multiple diverter plates 382 guide the material to different radial positions of the cross section of the silo 31 in the circumferential direction, avoiding the material from falling into the area directly above the outer cylinder 35 and causing a single-point impact on the outer cylinder 35 and the plow blade 33 on it. When the material falls and impacts the buffer ring 381, the elastic cylinder and the buffer spring work together to absorb the impact energy. The buffer ring 381 floats slightly up and down along the inner wall of the silo 31, converting the rigid impact into elastic buffering, protecting the outer cylinder 35 and the planetary gear set 36 from the impact load of the material.

[0069] During the buffering process described above, the pressure sensor collects the pressure data of the buffer ring 381 in real time, and the displacement sensor collects the displacement data of the buffer ring 381 in real time. The two sets of data are synchronously fed back to the control system, and the control system combines the pressure data and displacement data to determine the magnitude of the material resistance at the inlet. When the material falls through normally, the pressure data shows intermittent pulse fluctuations and the displacement data rebounds rapidly within a small range. The control system judges this as a normal feeding state, and the vibrator does not work or maintains low-frequency micro-vibration to save energy. As material gradually accumulates on the buffer ring 381 and the diverter plate 382, ​​the pressure data continues to rise and the displacement data continues to increase without rebounding. The control system judges that the material resistance is increasing and there is a tendency for bridging and blockage. It then starts the vibrator or increases the vibration frequency of the vibrator. The vibrator drives the buffer ring 381 to generate high-frequency micro-amplitude vibration, causing the accumulated material to loosen and fall off. After the accumulated material is shaken off and the pressure and displacement data return to the normal range, the control system automatically reduces the vibration frequency or shuts down the vibrator, restoring the energy-saving operation state.

[0070] Therefore, by cross-judging the dual parameters of pressure and displacement, it is possible to distinguish between instantaneous impact and continuous accumulation of materials, avoiding false start-ups caused by instantaneous large particle impacts when detecting a single parameter. The vibrator only works as needed when materials are actually accumulating, reducing energy consumption and vibrator wear while ensuring that the inlet is not blocked. After buffering and diverting, the material is evenly distributed in the upper area of ​​the hopper 31, and then loosened and pre-crushed by the low-speed reverse plow blade 33 on the outer cylinder 35. The material load distribution is more uniform and the arch breaking process is more stable.

[0071] like Figure 6 As shown, Embodiment Seven of the present invention is a further optimized design based on Embodiment Six. The difference is that a flow-dividing blade is provided on the side of the flow-dividing plate 382 near the inlet of the hopper 31, so that the flow-dividing plate 382 can pre-crush large clumps while dispersing the material, thereby reducing the cutting load of the subsequent plow blade 33; and vibrates synchronously with the buffer ring 381 when the vibrator is working, thereby enhancing the pre-crushing effect on large clumps.

[0072] The specific content of Embodiment 7 is as follows: A flow divider blade is provided on the side of the flow divider plate 382 near the inlet of the hopper 31.

[0073] In this embodiment, a flow divider blade is provided on the side of the flow divider plate 382 near the inlet of the hopper 31. The flow divider blade extends along the length of the flow divider plate 382, ​​and the cross-section of the flow divider blade is triangular. The blade edge of the flow divider blade faces upward toward the inlet of the hopper 31.

[0074] The working steps of Example 7 are as follows: When the material falls from the inlet of the hopper 31, large clumps first come into contact with the diversion blade at the top of the diversion plate 382. The cutting edge of the diversion blade splits the clumps, and the clumps are cut into several smaller fragments under their own gravity. The fragments then slide down along both sides of the diversion plate 382 and disperse to various parts of the hopper 31. The particle size of the material after pre-crushing by the diversion blade is significantly reduced, and it is easier to be sheared and refined by the plow blade 33 after entering the cutting zone. This reduces the impact load of the plow blade 33 when it encounters oversized clumps and the risk of instantaneous overload of the drive mechanism 32. At the same time, it reduces the probability of large pieces of material getting stuck between adjacent plow blades 33, causing equipment jamming. The diversion blade and the diversion plate 382 are an integral structure, requiring no additional drive. The pre-crushing is completed by utilizing the gravitational potential energy of the falling material, resulting in low energy consumption and a reliable structure.

[0075] like Figures 2-3 As shown, Embodiment 8 of the present invention is a further optimized design based on Embodiment 1. The difference is that it provides another specific implementation of the walking mechanism 21. The walking mechanism 21 adopts a combination structure of walking track 211, walking frame 212 and power unit 213. The power unit 213 adopts a pin and rack transmission method with power wheel 2133 meshing with power column 2134 to provide a non-slip, high-precision lateral walking trajectory for telescopic conveyor line 2 and distribution unit 3. It is suitable for multi-station precise positioning and unloading operation scenarios.

[0076] The specific details of Embodiment 8 are as follows: The walking mechanism 21 includes a walking track 211, a walking frame 212, and a power unit 213. The walking frame 212 is equipped with several walking wheels, which are in contact with the walking track 211. The power unit 213 drives the walking frame 212 to walk on the walking track 211. The second conveyor line 22 is connected to the walking frame 212, and the hopper 31 is installed on the walking frame 212. The power unit 213 includes a power motor 2131, a reducer 2132, a power wheel 2133, and several power columns 2134. The power motor 2131 and the reducer 2132 are both installed on the walking frame 212. The output end of the power motor 2131 is connected to the power wheel 2133 through the reducer 2132. Several power columns 2134 are arranged on the walking track 211, and the power wheel 2133 meshes with several power columns 2134.

[0077] The working steps of Example 8 are as follows: When it is necessary to move the receiving or unloading material, the rotational motion output by the power motor 2131 is reduced and increased in torque by the reducer 2132 and then transmitted to the power wheel 2133. When the power wheel 2133 rotates, it meshes with the power column 2134 on the side of the walkway 211 in sequence. Since the power column 2134 is fixed on the walkway 211, the meshing reaction force pushes the walking frame 212 to move along the walkway 211. The walking frame 212 drives the second conveyor line 22 and the hopper 31 to move laterally synchronously. The walkway 211 provides a fixed walking trajectory and rigid support for the walking frame 212. The walking wheel always travels along the walkway 211, avoiding the deviation and serpentine problems that are easy to occur when traveling without tracks, and ensuring that the feeding end of the second conveyor line 22 is always aligned with the discharging end of the first conveyor line 1.

[0078] It will be apparent to those skilled in the art that the present invention is not limited to the details of the exemplary embodiments described above, and that the invention can be implemented in other specific forms without departing from its spirit or essential characteristics. Therefore, the embodiments should be considered in all respects as exemplary and non-limiting, and the scope of the invention is defined by the appended claims rather than the foregoing description. Thus, all variations falling within the meaning and scope of equivalents of the claims are intended to be included within the present invention. No reference numerals in the claims should be construed as limiting the scope of the claims.

Claims

1. A retractable multi-station belt conveyor, characterized in that: It includes a first conveyor line (1), a telescopic conveyor line (2), and a distribution unit (3); The telescopic conveyor line (2) includes a walking mechanism (21) and a second conveyor line (22), the second conveyor line (22) being connected to the walking mechanism (21); The distribution unit (3) includes a hopper (31), a drive mechanism (32), and a plow (33). The hopper (31) is provided with an inlet and an outlet, and the hopper (31) is mounted on a walking mechanism (21). The drive mechanism (32) is installed on the hopper (31). An inner shaft (34) is connected to the output end of the drive mechanism (32). An outer cylinder (35) is sleeved on the inner shaft (34) near the inlet of the hopper (31). The outer cylinder (35) is rotatably mounted on the hopper (31). The inner shaft (34) and the outer cylinder (35) are connected by a planetary gear set (36). The inner shaft (34) and the outer cylinder (35) are each provided with a number of mounting cylinders (341), and each mounting cylinder (341) is equipped with an arch-breaking shaft (37), and the plow blade (33) is installed on the arch-breaking shaft (37); A buffer assembly (38) is provided at the inlet of the hopper (31), and the buffer assembly (38) is located above the outer cylinder (35); The buffer assembly (38) includes a buffer ring (381), a flow divider (382) and a vibrator. The buffer ring (381) is slidably mounted on the hopper (31). An elastic structure connects the buffer ring (381) and the hopper (31). A detection element is provided on the hopper (31) at the position corresponding to the buffer ring (381). Multiple flow dividers (382) are provided, and all multiple flow dividers (382) are installed on the buffer ring (381); The vibrator is installed on the hopper (31), the vibrator is electrically connected to the control system, and the output end of the vibrator is connected to the buffer ring (381). The flow divider (382) has a flow divider blade on the side near the inlet of the hopper (31).

2. The extendable multi-station belt conveyor according to claim 1, characterized in that: The hopper (31) is provided with rails (311) at the positions corresponding to the inner shaft (34) and the outer cylinder (35). A sealing ring (312) is rotatably provided on the inner side of the rails (311). The rails (311) and the inner shaft (34) are eccentrically arranged. One end of the arch-breaking shaft (37) forms a sliding seal connection with the mounting cylinder (341), and the other end of the arch-breaking shaft (37) passes through the sealing ring (312) and is provided with rollers, which roll in the track (311); An elastic element is connected between the arch-breaking shaft (37) and the mounting cylinder (341).

3. The retractable multi-station belt conveyor according to claim 2, characterized in that: The inner shaft (34) and the arch-breaking shaft (37) on the inner shaft (34) are both provided with air supply channels (342). The two air supply channels (342) are connected by a telescopic hose. The arch-breaking shaft (37) on the inner shaft (34) is provided with several air jet holes facing the outlet of the hopper (31). The inlet of the air supply channel (342) is connected to the air supply system, and the outlet of the air supply channel (342) is connected to the air jet holes.

4. A retractable multi-station belt conveyor according to any one of claims 1-3, characterized in that: The cross-section of the plow blade (33) is trapezoidal, the length of the upper base of the trapezoid is less than the length of the lower base, the upper base of the trapezoid is located near the mounting cylinder (341), and the lower base of the trapezoid is located away from the mounting cylinder (341). The plow blade (33) is made by spiral twisting.

5. A retractable multi-station belt conveyor according to claim 4, characterized in that: The plow blade (33) is equipped with several arch-breaking blades.

6. A retractable multi-station belt conveyor according to claim 5, characterized in that: The arch-breaking piece has serrated blades on both sides.

7. A retractable multi-station belt conveyor according to claim 1, characterized in that: The walking mechanism (21) includes a walking track (211), a walking frame (212) and a power unit (213). The walking frame (212) is provided with a plurality of walking wheels, and the plurality of walking wheels are in contact with the walking track (211). The power unit (213) drives the walking frame (212) to walk on the walking track (211). The second conveyor line (22) is connected to the walking frame (212), and the hopper (31) is installed on the walking frame (212).

8. A retractable multi-station belt conveyor according to claim 7, characterized in that: The power unit (213) includes a power motor (2131), a reducer (2132), a power wheel (2133), and several power columns (2134). The power motor (2131) and the reducer (2132) are both mounted on the walking frame (212), and the output end of the power motor (2131) is connected to the drive wheel (2133) through the reducer (2132); Several of the power columns (2134) are arranged on the walkway (211), and the power wheel (2133) meshes with the several power columns (2134).

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