Belt vibration patting sweeper and patting amplitude generation method thereof

Abstract

The present application relates to the field of belt material accumulation cleaning, in particular to a belt vibration beating sweeper and a beating amplitude generation method thereof. The belt vibration beating sweeper comprises a mounting hanger, a hoisting connecting rod, a vibration supporting plate and a vibration source. The mounting hanger is arranged above the return belt, the hoisting connecting rod is rotatably connected with the mounting hanger and the vibration supporting plate at two ends respectively, the length of the hoisting connecting rod is greater than the distance from the mounting hanger to the belt and the hoisting connecting rod is arranged obliquely, and the end connected with the vibration supporting plate is close to the downstream of the belt movement. The vibration source drives the vibration supporting plate to make the hoisting connecting rod reciprocate, and the vibration supporting plate is suspended above the belt, and the hoisting connecting rod is connected with the vibration supporting plate in a floating manner. This structure avoids strong restriction of the vibration force, prevents the increase of the local stress of the belt and the extrusion damage. Meanwhile, the vibration supporting plate is in contact with the belt surface, compared with the linear contact of the existing beating roller, the force area is large, the beating force is uniform, the bending stress is small, the damage to the brittle area of the belt can be avoided, and greater beating force can be applied without damaging the belt, so that the materials can be effectively shaken off.

Description

Technical Field

[0001] This invention relates to the field of belt conveyor cleaning, and in particular to a belt vibration beater cleaner and a method for generating the beater amplitude. Background Technology

[0002] Inclined belt conveyors, herringbone belt conveyors, and other belt conveyors are special belt conveyors capable of transporting bulk materials at large inclination angles (even vertical). They break through the limitation of ordinary belt conveyors, whose inclination angle generally does not exceed 18°-20°, and are widely used in industries such as mining, ports, metallurgy, chemical, cement, power, and municipal engineering.

[0003] Large-angle belts (such as corrugated sidewall belts) typically consist of three parts: a base belt (the main load-bearing component, similar to a regular belt), corrugated sidewalls (preventing material slippage, with a height of several hundred millimeters), and transverse partitions (preventing material slippage, in T-, C-, or rectangular shapes). This structure significantly increases the belt's lateral and longitudinal bending stiffness, preventing deformation during large-angle or even vertical operation. In other words, it exhibits higher rigidity in its overall structure. However, because the sidewalls and transverse partitions need to connect with other components, local stresses are more concentrated at these connection points. For example, the root of the sidewall, where the belt connects to the base belt, is subjected to combined bending, tensile, and shear stresses, making it prone to delamination and cracking; the connection between the partition and the sidewall is subjected to triaxial stress, making it a high-risk area for fatigue fracture. Therefore, these localized areas are more brittle and more susceptible to damage and failure. Especially in low-temperature environments, the increased brittleness of these connection points due to low temperatures further exacerbates the likelihood of failure.

[0004] Meanwhile, due to the structural design of steeply inclined belts and their large inclination angle during operation, materials are more likely to be tightly compacted and adhere to the structure. Therefore, compared to existing ordinary straight conveyor belts, steeply inclined belts are more prone to material accumulation, especially at the root of the sidewalls and in the partition area of ​​the return section. In existing technologies, to solve the problem of material residue on belt conveyors, corresponding beating devices are usually configured to perform high-frequency vibration beating on the return section of the conveyor belt (the vibration mentioned in this invention can be either regular and rhythmic vibration or irregular vibration, the main purpose of which is to beat the belt through reciprocating motion) to promote the removal of materials adhering to the conveyor belt. This is exemplified by the solution disclosed in the utility model patent application CN202022700804.6, "Belt Conveyor Unloading Vibrating Device". Current beating and cleaning mechanisms use a vibrating motor to drive steel rollers, beating and vibrating the conveyor belt through line contact. However, for belts with large inclination angles, their rigidity exceeds that of ordinary conveyor belts. This makes it difficult for existing contact patting methods using steel rollers to effectively vibrate and shake the conveyor belt, thus significantly reducing the cleaning effect.

[0005] Meanwhile, in the return section of a steep-angle belt, some material may roll onto the belt during the return stroke. Consequently, driven by the belt, this material will be compressed between the belt and the slapping rollers. Furthermore, the existing slapping mechanism design has relatively strict positional constraints on the slapping rollers to ensure continuous contact between them and the back of the belt. This further increases localized stress and bending on the belt during the compression process, making it more susceptible to damage in areas of stress concentration at the connection points of components in steep-angle belts. In particular, existing belt cleaning structures are inadequate for conveying low-temperature materials (such as snow, ice, and mixtures thereof). Summary of the Invention

[0006] To address the aforementioned technical problems, the technical solution adopted by this invention is as follows:

[0007] According to one aspect of the present invention, a belt vibrating beater cleaner is provided, comprising: a mounting bracket, a lifting rod, a vibrating support plate, and a vibration source;

[0008] The mounting bracket is connected to the mounting bracket of the belt conveyor so that the mounting bracket is erected above the return belt;

[0009] The two ends of the lifting link are rotatably connected to the mounting bracket and the vibrating support plate, respectively; the length of the lifting link is greater than the distance between the mounting bracket and the return belt; the lifting link is inclined relative to the return belt, and the end of the lifting link connected to the vibrating support plate is closer to the downstream of the return belt's direction of movement.

[0010] The vibration source includes at least one vibration motor and a vibration transmission support;

[0011] The vibration motor is fixed to the inside of the vibration support plate via a vibration transmission bracket.

[0012] The vibration transmission support includes a motor mounting base and multiple vibration transmission stiffeners;

[0013] The upper end of the vibration transmission stiffener is fixedly connected to the motor mounting base, and the lower end of the vibration transmission stiffener is fixedly connected to the bottom surface and / or side wall surface of the vibration support plate; multiple vibration transmission stiffeners are staggered with each other; the vibration transmission stiffener is a trapezoidal plate structure with a smaller top and a larger bottom.

[0014] Furthermore, the lifting linkage is configured with four links;

[0015] The vibration support plate is provided with first connecting lugs at the four corners, and the mounting bracket is provided with second connecting lugs at the corresponding four corners.

[0016] The lower end of each lifting link is rotatably connected to a first connecting lug, and the upper end is rotatably connected to a corresponding second connecting lug;

[0017] The rotation center line connecting the two first connecting lugs on the front side of the vibrating plate, the rotation center line connecting the two second connecting lugs on the front side of the mounting bracket, and the two lifting rods connecting them together form a parallelogram mechanism.

[0018] The rotation center line connecting the two first connecting lugs on the rear side of the vibrating plate, the rotation center line connecting the two second connecting lugs on the rear side of the mounting bracket, and the two lifting rods connecting them also constitute another parallelogram mechanism.

[0019] The parallelogram mechanism on the front and rear sides has the same structure to keep the vibrating plate stable during vibration and prevent it from tilting; the front and rear sides are two sides along the width of the belt.

[0020] Furthermore, it also includes multiple synchronizing pins;

[0021] Each synchronous pin is simultaneously inserted into the rotating connection end of any two hoisting links that need to be synchronized, so as to ensure the synchronous movement of the four hoisting links.

[0022] Furthermore, the lifting linkage is configured as two;

[0023] The lower ends of the two lifting rods are rotatably connected to the midpoint of the length of the front or rear side of the vibrating support plate, respectively. The upper ends of the lifting rods are rotatably connected to the mounting bracket. The front and rear sides are the two sides in the width direction of the belt.

[0024] Furthermore, the angle between the vibration direction of the vibration source and the static tilt direction of the hoisting link is 90°.

[0025] Furthermore, it also includes a surface cleaning assembly, which includes a cleaning baffle and a push linkage;

[0026] The cleaning baffle is an A-shaped symmetrical plate structure, and the side wall of the cleaning baffle slides against the back of the return belt; the cleaning baffle is located on the upstream side, which is closer to the direction of movement of the return belt than the vibrating plate.

[0027] The two ends of the push rod are rotatably connected to the crossbeams of the vibrating support plate and the cleaning baffle, respectively.

[0028] According to a second aspect of the present invention, a method for generating the tapping amplitude of a belt vibratory beater is also provided. The method is applied to a belt vibratory beater and includes the following steps:

[0029] Determine the initial tapping amplitude of the vibratory sweeper based on the temperature of the belt operating environment, and then carry out the tapping operation.

[0030] A triaxial accelerometer is used to collect the transient vibration response signal of the belt at a preset position downstream of the vibrating beater sweeper;

[0031] Vibration characteristic parameters are extracted from the transient vibration response signal, and the impact intensity index is calculated; the vibration characteristic parameters include: peak acceleration a peak Vibration dominant frequency f dominant Vibration decay time T decay ;

[0032] Impact strength index I satisfies the following condition:

[0033] ;

[0034] Compare I with the preset target impact strength index I ref By comparison, the tapping amplitude adjustment ΔA is obtained through a PI control algorithm; ΔA satisfies the following conditions:

[0035] ;

[0036] Among them, K p and K i These are the proportional coefficient and the integral coefficient, respectively, with values ​​ranging from 0.3 to K. p ≤0.8, 0.05≤K i ≤0.15; T decay The time it takes for the vibration amplitude to decay from its peak value to 10%;

[0037] The current tapping amplitude is adjusted using △A, and the adjusted tapping amplitude is subjected to safety limiting. The result is then output to the vibration motor of the vibrating sweeper for the next tapping control, thus achieving closed-loop adaptive adjustment of the tapping amplitude. The upper limit of the tapping amplitude is 50mm, and the lower limit is 10mm.

[0038] Furthermore, I is compared with the preset target impact strength index I. ref By comparison, the tapping amplitude adjustment ΔA is obtained through a PI control (Proportional-Integral Control) algorithm; ΔA satisfies the following conditions:

[0039] ;

[0040] Among them, K p and K i These are the proportional coefficient and the integral coefficient, respectively, with values ​​ranging from 0.3 to K. p ≤0.8, 0.05≤Ki ≤0.15;

[0041] The current tapping amplitude will be adjusted using △A. The adjusted amplitude will then be subject to safety limiting and output to the vibrating motor of the vibrating sweeper for the next tapping control, thus achieving closed-loop adaptive adjustment of the tapping amplitude. This can be replaced with:

[0042] If f dominant <60Hz and T decay >400ms, increasing the tapping amplitude of the vibrating sweeper;

[0043] If a peak If the weight exceeds 40g and the temperature is less than 5°C, a brittleness risk warning will be issued and the tapping operation will be suspended.

[0044] This invention has at least one of the following beneficial effects:

[0045] In this invention, the vibrating beater mechanism suspends the vibrating plate above the return belt by setting up a mounting bracket and a lifting linkage. The inclination angle of the lifting linkage is consistent with the movement direction of the return belt. This structural design ensures that the vibrating plate is always in a floating connection state, rather than a strictly controlled movement state. Therefore, when material rolling off the belt enters between the vibrating plate and the belt, the vibrating plate will be lifted. Compared with the mechanical structure of the prior art where the moving space of the beating roller is relatively fixed, the downward vibration force applied by the vibrating plate of this invention is not strongly restricted by the structure. This also avoids passing all the downward vibration force through the material and acting directly on the belt, thereby avoiding increasing the local stress on the belt and preventing the crushing damage to the belt caused by falling material.

[0046] Meanwhile, the contact between the vibrating plate and the belt in this invention is surface contact, which, compared to the line contact between the striking roller and the belt in the prior art, results in a larger force-bearing area and more uniform striking force. This helps to prevent the striking area from being concentrated precisely in the more brittle areas of the belt, such as the belt root. Furthermore, since the striking plate is planar while the striking roller is curved, the bending stress on the belt when the striking plate strikes it is relatively small, further preventing damage to the more brittle areas of the belt.

[0047] In addition, since the vibrating pallet in this invention is in surface contact with the belt, the vibrating pallet can apply a greater vibration force while ensuring that the belt is not damaged. This can more effectively shake the high-rigidity, large-angle belt, making it easier for the material to fall off. Attached Figure Description

[0048] To more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings used in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0049] Figure 1 This is an overall structural diagram of the large-angle belt vibration beater sweeper provided in an embodiment of the present invention;

[0050] Figure 2 This is a structural diagram showing the arrangement of the large-angle belt vibrating beater cleaner in a large-angle belt conveyor, as provided in an embodiment of the present invention.

[0051] Figure 3 This is a structural diagram showing the arrangement of the inclined belt vibrating beater cleaner in an inclined belt conveyor according to an embodiment of the present invention. The installation hanger, installation bracket and vibration cover are omitted.

[0052] Figure 4 This is a connection structure diagram of the vibrating beater sweeper and the surface sweeping assembly provided in an embodiment of the present invention;

[0053] Figure 5 This is a structural diagram illustrating the working principle of the vibrating beater sweeper and the surface sweeping assembly provided in the embodiments of the present invention.

[0054] Figure 6 This is a flowchart illustrating a method for generating the beat amplitude of a belt vibration beater sweeper, as provided in an embodiment of the present invention.

[0055] Figure Labels

[0056] 1. Install the hanger; 2. Lifting rod; 21. Second connecting lug; 3. Vibration support plate; 31. Vibration cover; 32. First connecting lug; 40. Vibration motor; 41. Vibration transmission bracket; 5. Synchronous pin; 60. Cleaning baffle; 61. Crossbeam; 62. Push rod; 70. Belt; 71. Install the bracket. Detailed Implementation

[0057] 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.

[0058] As one possible embodiment of the present invention, such as Figure 1As shown, a belt vibrating beater cleaner is provided. This belt vibrating beater cleaner can be used to clean the accumulated material on belt conveyors with large angles, herringbone belt conveyors and other belt conveyors. It includes: a mounting bracket 1, a lifting rod 2, a vibrating support plate 3 and a vibration source.

[0059] Mounting bracket 1 is positioned above the return belt.

[0060] In the application of steep-angle belt conveyors, their main function is to transport materials from a lower position to a higher position. Typically, the steep-angle belts at both the inlet and outlet ends are arranged horizontally. In this example, the mounting bracket 1 is designed to be fixedly connected to the mounting support 71 at the outlet end of the steep-angle belt. Specifically, the mounting bracket 1 can adopt a two-unit gantry structure to facilitate the subsequent floating and hoisting of the vibrating pallet 3 above the return belt.

[0061] In this embodiment, as Figure 2 and Figure 3 As shown, the vibratory beater mechanism is located at the discharge end of the steep-angle belt. This configuration offers the following benefits: First, after discharge, the steep-angle belt turns downwards via the redirecting roller, entering its return stroke. Because the belt 70 undergoes some bending deformation as it passes the redirecting roller, the material adhering to the belt 70 may experience reduced adhesion. Therefore, during subsequent vibratory beating, the material is more easily separated from the belt 70 and falls off, resulting in a more effective cleaning effect. Second, on the discharge side, the return belt is horizontal, allowing for closer contact between the vibratory support plate 3 and the belt 70, improving the cleaning effect. Simultaneously, the ample space beneath the return belt facilitates the installation of a receiving device to promptly remove any fallen material.

[0062] The two ends of the lifting link 2 are rotatably connected to the mounting bracket 1 and the vibrating support plate 3, respectively. The length of the lifting link 2 is greater than the distance between the mounting bracket 1 and the return belt. The lifting link 2 is inclined relative to the return belt, and the end of the lifting link 2 connected to the vibrating support plate 3 is closer to the downstream of the return belt's direction of movement.

[0063] The main function of the lifting link 2 is to achieve a floating connection between the mounting bracket 1 and the vibrating support plate 3. To achieve this floating connection, the key is that both ends of the lifting link 2 need to be in a rotating state to allow it to swing. In this embodiment, the lifting link 2 swings around the upper connection point as the center, thus achieving the floating effect. Simultaneously, to prevent the lifting link 2 from forming a perpendicular state with the return belt, which would prevent the link from swinging, this embodiment designs the lifting link 2 to be longer, so that it always maintains its tilted state (e.g., ...). Figure 5(The angle a in the middle). Therefore, even when the vibrating support plate 3 is at its lowest position, the lifting link 2 itself remains tilted, avoiding the lifting link 2 from forming a perpendicular state with the belt 70, thereby ensuring smooth swing and preventing jamming.

[0064] Specifically, such as Figures 1 to 3 As shown, the lifting linkage 2 can be set to four.

[0065] The vibrating support plate 3 has a first connecting lug 32 at each of its four corner points, and the mounting bracket 1 has a second connecting lug 21 at each of its four corner points. The lower end of each lifting link 2 is rotatably connected to a first connecting lug 32, and the upper end is rotatably connected to the corresponding second connecting lug 21. The line connecting the rotation centers of the two first connecting lugs 32 on the front side of the vibrating support plate 3, the line connecting the rotation centers of the two second connecting lugs 21 on the front side of the mounting bracket 1, and the two lifting links 2 connecting them together form a parallelogram mechanism.

[0066] The rotation center line connecting the two first connecting lugs 32 on the rear side of the vibrating support plate 3, the rotation center line connecting the two second connecting lugs 21 on the rear side of the mounting bracket 1, and the two lifting rods 2 connecting them also constitute another parallelogram mechanism.

[0067] The parallelogram structure on the front and rear sides is the same, so that the vibrating support plate 3 can maintain a stable posture during vibration and not tilt; in this embodiment, the front and rear sides are the two sides in the width direction of the belt 70.

[0068] In addition, there can be two hoisting rods 2.

[0069] The lower ends of the two lifting rods 2 are rotatably connected to the midpoint of the length of the front or rear side of the vibrating support plate 3, respectively, and the upper ends are rotatably connected to the mounting bracket 1. Specifically, a connecting beam can be set between the two gantry-type mounting brackets 1, and the upper ends of the lifting rods 2 are rotatably connected to the connecting beam, thereby forming a simply supported suspension structure, which is suitable for single vibration source beating scenarios with narrower conveyor belts.

[0070] The two lifting rods 2 are rotatably connected to the midpoints of the two sides of the vibrating support plate 3.

[0071] Furthermore, it also includes multiple synchronous pins 5.

[0072] like Figures 2-4 As shown, each synchronous pin 5 is simultaneously rotated and passed through the rotating connection end of any two hoisting links 2 that need to be synchronized, so as to ensure the synchronous movement of the four hoisting links 2.

[0073] In practical applications, to achieve effective vibration and tapping of various parts of the conveyor belt (i.e., belt 70), the length of the vibrating pallet 3 is usually designed to be consistent with the width of the conveyor belt. However, when the width of the conveyor belt increases to a preset width threshold, a single vibration source will not be able to fully drive all parts of the vibrating pallet 3. Specifically, when the width of the conveyor belt (i.e., the length of the vibrating pallet 3) exceeds a certain critical value (i.e., the preset width threshold), a single vibration motor 40 cannot effectively transmit vibration energy to the entire vibrating pallet 3 area, resulting in problems such as amplitude attenuation, insufficient tapping force, and reduced cleaning effect at both ends or in the middle of the pallet. At this time, multiple vibration sources must be configured. Therefore, the preset width threshold needs to be adaptively determined by those skilled in the art based on the tapping effect under actual working conditions. For example, if the amplitude decreases significantly after the conveyor belt width exceeds 1.5m, it is recommended to set multiple vibration motors 40. The preset width threshold can be 1.8m.

[0074] However, when multiple vibration sources are installed, slight synchronization differences may exist between the vibration motors 40, which can cause deviations in the vibration amplitude or direction of different areas of the vibrating support plate 3, resulting in asynchronous movement of the lifting linkage 2. Therefore, a synchronization pin structure 5 was designed to eliminate this deviation.

[0075] By employing a synchronous pin design, the tilting or jamming of the vibrating pallet 3 caused by asynchronous movement of the lifting linkage 2 is successfully eliminated, ensuring stable operation throughout the vibration process. Driven by the vibrating motor 40, the vibrating pallet 3 periodically taps the bottom of the return belt, using the swing of the lifting linkage 2 to compensate for the slight displacement of the belt 70 during operation, while maintaining constant contact pressure, thereby improving cleaning efficiency. This structure not only enhances the stability of the cleaning device but also extends the service life of the equipment, making it particularly suitable for complex working environments with high humidity and easily sticky materials. During long-term operation, this structure effectively reduces maintenance frequency and downtime costs, demonstrating excellent reliability and adaptability. Through mechanical balance design, vibration energy is precisely transmitted to the cleaning area, avoiding ineffective losses and reducing interference with surrounding components. The overall device structure is compact and simple, facilitating installation and commissioning, and is especially suitable for space-constrained industrial scenarios.

[0076] The vibration source is fixedly connected to the vibration support plate 3 so as to drive the hoisting rod 2 to swing back and forth around the end connected to the installation hanger 1.

[0077] Specifically, the angle between the vibration direction of the vibration source and the static tilt direction of the hoisting link 2 is [80°, 100°].

[0078] Preferably, the angle between the vibration direction of the vibration source and the static tilt direction of the lifting link 2 is 90°. When the angle is 90°, the kinetic energy output by the vibration source can be converted into the swinging power of the lifting link 2 to the maximum extent, effectively improving the vibration transmission efficiency. At this time, the vibration direction is perpendicular to the link axis, avoiding component force loss and ensuring that the vibrating support plate 3 maintains a stable amplitude during reciprocating motion. This angle design can also reduce lateral wear at the link hinge, reduce motion resistance, and thus extend the service life of key connecting components. When multiple vibration sources work together, this angle configuration is more conducive to the consistency of vibration phase between units and reduces interference. Combined with the role of the synchronous pin 5, the overall system can still maintain good dynamic balance under high-frequency operation, ensuring continuous and stable material cleaning operation. In addition, the working mode of the vibration motor 40 can adopt a high-frequency, low-amplitude mode. Specifically, the vibration frequency can be 60-120Hz: to generate "micro-resonance" between the material and the belt 70, which is conducive to separation; the vibration amplitude can be 1-8mm: to avoid large impact forces directly acting on the rigid belt structure and damaging the brittle parts of the belt 70.

[0079] like Figure 1 As shown, the vibration source includes at least one vibration motor 40 and a vibration transmission bracket 41. The vibration transmission bracket 41 transmits the vibration force of the vibration motor 40 evenly to the vibration support plate 3.

[0080] The vibration motor 40 is fixed to the inner side of the vibration support plate 3 via a vibration transmission bracket 41. The vibration transmission bracket 41 includes a motor mounting base and multiple vibration transmission stiffeners. The upper end of each vibration transmission stiffener is fixedly connected to the motor mounting base, and the lower end of each stiffener is fixedly connected to the bottom surface and / or side wall surface of the vibration support plate 3. The multiple vibration transmission stiffeners are staggered. Each vibration transmission stiffener has a trapezoidal plate structure that is smaller at the top and larger at the bottom.

[0081] The vibration transmission stiffener adopts a trapezoidal structure design with a smaller top and a larger bottom. Its main function is to transmit the power generated by the vibration motor 40 to various areas of the vibration support plate 3 more widely. In addition, the staggered layout of multiple vibration stiffeners can enhance the connection strength between the vibration motor 40 and the vibration support plate 3, thereby avoiding connection breakage or material fatigue caused by vibration and preventing damage.

[0082] Furthermore, such as Figure 2 As shown, it also includes: a vibration cover 31, which is fixedly mounted on the vibration support plate 3, and a shock-absorbing pad is sandwiched between the vibration cover 31 and the vibration support plate 3. The shock-absorbing pad can be a rubber pad. The vibration cover 31 and the vibration support plate 3 together form a closed space, which effectively isolates and protects the vibration source and prevents foreign objects from entering.

[0083] In this embodiment, the vibrating beater mechanism suspends the vibrating support plate 3 above the return belt by setting up a mounting bracket 1 and a lifting connecting rod 2. The tilt angle of the lifting connecting rod 2 is consistent with the movement direction of the return belt. This structural design ensures that the vibrating support plate 3 is always in a floating connection state, rather than a strictly controlled movement state. Therefore, when material rolling off the belt 70 enters between the vibrating support plate 3 and the belt 70, the vibrating support plate 3 will be lifted. Compared with the mechanical structure of the prior art where the moving space of the beating roller is relatively fixed, the downward vibration force applied by the vibrating support plate 3 of this invention is not strongly restricted by the structure. This also avoids the downward vibration force being entirely transmitted through the material and directly acting on the belt 70, thereby avoiding increasing the local stress of the belt 70 and preventing the crushing damage to the belt 70 caused by falling material.

[0084] Meanwhile, in this embodiment, the contact between the vibrating plate 3 and the belt 70 is a surface contact. Compared to the line contact between the striking roller and the belt 70 in the prior art, the force-bearing area of ​​the striking area is larger, and the striking force is more uniform. This helps to avoid the striking area being concentrated precisely in the more brittle areas of the belt 70, such as the root of the belt 70. In addition, since the striking plate is flat and the striking roller is curved, the bending stress on the belt 70 when the striking plate strikes it is relatively small, thereby further avoiding damage to the more brittle areas of the belt 70.

[0085] In addition, since the vibrating pallet 3 and the belt 70 are in surface contact in this embodiment, the vibrating pallet 3 can apply a greater vibration force while ensuring that the belt 70 is not damaged. This can more effectively shake the high-rigidity, large-angle belt, making it easier for the material to fall off.

[0086] As another possible embodiment of the present invention, such as Figure 3 As shown, the large-angle belt vibratory beater sweeper also includes a surface sweeping assembly, which includes a sweeping baffle 60 and a push linkage 62.

[0087] The cleaning baffle 60 is an A-shaped symmetrical plate structure, and its sidewall slides against the back of the return belt. The cleaning baffle 60 is positioned upstream of the vibrating support plate 3, closer to the direction of the return belt's movement.

[0088] The two ends of the push rod 62 are rotatably connected to the crossbeam 61 of the vibrating support plate 3 and the cleaning baffle 60, respectively. Furthermore, to further prevent the cleaning baffle 60 from shifting vertically and detaching from the belt 70 surface, this embodiment can also set the junction between the push rod 62 and the crossbeam 61 as a clearance fit, allowing the push rod 62 to undergo a certain amount of vertical displacement, thereby counteracting the upward pulling effect of the vibrating support plate 3 on the push rod 62 as a whole. Additionally, the angle between the push rod 62 and the horizontal direction can be adjusted to better guide the push rod 62 to swing vertically, thus counteracting the upward pulling effect of the vibrating support plate 3 on the push rod 62 as a whole. Simultaneously, driven by the movement of the belt 70 itself, the push rod 62 will continuously push the connecting rod 62 in the horizontal direction, meaning that the two ends of the push rod 62 are always under clamping force in the horizontal direction.

[0089] In addition, even if the cleaning baffle 60 undergoes vertical displacement, the amount of displacement will be extremely small. When displacement occurs, the tail of the cleaning baffle 60 will lift up, while the tip will remain in contact with the belt 70. This state will not only maintain a certain cleaning effect on the material on the belt 70, but also create a certain vibration and beating effect on the belt 70 due to the repeated lifting and lowering of the tail of the cleaning baffle 60. Thus, the movement of the cleaning baffle 60 can generate primary vibration and beating, which, combined with the subsequent vibration and beating structure, will perform secondary beating, further improving the cleaning effect of accumulated material.

[0090] At the discharge end of the steeply inclined belt, all the material is dumped, but some material is more likely to slide onto the return belt below. This often results in material getting stuck between the vibrating support plate 3 and the belt 70, increasing the risk of localized material accumulation on the belt 70. Although the vibration beater mechanism in the aforementioned embodiment can alleviate the damage to the localized stress on the belt 70 caused by falling material, further measures are needed to prevent falling material from entering between the beater mechanism and the belt 70, such as... Figure 4 and Figure 5 As shown, a surface cleaning component has been added to this example.

[0091] The A-shaped cleaning baffle 60 in this component is located upstream of the vibratory tapping mechanism and is connected to the vibratory support plate 3 via a push rod 62. Figure 5As shown, since the vibrating pallet 3 oscillates continuously during its movement, the arc-shaped path formed during its oscillation has a certain horizontal component. This structure utilizes this characteristic by connecting the cleaning baffle 60 to the vibrating pallet 3 via the linkage 62. Therefore, the horizontal path component formed by the vibrating pallet 3 during its movement is transferred to the cleaning baffle 60, thereby causing the cleaning baffle 60 to generate a certain horizontal reciprocating vibration on the belt 70. This helps to move some of the material that falls on the belt 70 along the outer edge of the cleaning baffle 60 to the outside of the belt 70, thereby reducing the possibility of falling material posing a risk between the vibrating pallet 3 and the belt 70.

[0092] According to the above embodiments, such as Figure 5 As shown, the inclination of the lifting link 2 indicates that the link is closer to a vertical state. Therefore, during vibration, the arc-shaped swing path it forms is typically a circular arc close to the lower part of a complete circle. In this path segment, the horizontal component is more prevalent, while the vertical component is relatively smaller. In other words, in the motion trajectory of the connection between the vibrating support plate 3 and the pushing link 62, the horizontal trajectory component is significantly larger than the vertical trajectory component.

[0093] Furthermore, the push link 62 is positioned closer to horizontal, and the sweeping baffle 60 has a greater weight. This allows the end of the push link 62 hinged to the sweeping baffle 60 to serve as the center, while the other end swings under the drive of the vibrating support plate 3. Simultaneously, based on the layout of the push link 62, the vertical component of the arc-shaped motion trajectory formed by its swinging end is greater than the horizontal component. This vertical component can roughly offset the vertical component formed by the vibrating support plate 3 during its swing, thus minimizing the risk of the sweeping baffle 60 being pulled up vertically during vibration and detaching from the belt 70 surface. At the same time, because the horizontal component is smaller and less likely to offset the horizontal trajectory formed by the vibrating support plate 3 during its swing, more horizontal motion can be transferred to the sweeping baffle 60, making it easier for it to form a horizontal reciprocating motion closely adhering to the belt 70 surface.

[0094] As another possible embodiment of the present invention, such as Figure 6 As shown, a method for generating the beating amplitude of a belt vibrating beater is also provided. This method is applied to a belt vibrating beater and includes the following steps:

[0095] S100: Determine the initial tapping amplitude of the vibratory sweeper based on the temperature of the belt 70 operating environment, and carry out the tapping operation.

[0096] Specifically, the initial tapping amplitude A0 can be determined as follows:

[0097] When the ambient temperature T < 5°C, set the initial tapping amplitude to 15-25mm;

[0098] When 5°C≤T≤35°C, the initial tapping amplitude is set to 30~40 mm;

[0099] When T>35°C, set the initial tapping amplitude to 20-30 mm.

[0100] S200: Uses a three-axis accelerometer to collect the transient vibration response signal of the belt 70 at a preset position downstream of the vibrating beater sweeper.

[0101] Specifically, the vibration energy of the belt is transmitted through a mechanical path: idler roller → bearing → support → bracket. The support, acting as a "rigid intermediary," indirectly but accurately reflects the belt's vibration state. Therefore, a triaxial accelerometer (such as a high-performance MEMS accelerometer) is installed on the idler roller support or belt bracket 70, 1-2 meters downstream of the beater, to avoid direct impact. The beater trigger signal serves as the starting source for synchronous acquisition, simultaneously acquiring the triaxial vibration acceleration signal within 500ms after the beater, with a sampling rate of no less than 2000 Hz. Simultaneously, a digital low-pass filter can be used to suppress high-frequency noise in the time-domain signal. A magnetic base or bolts are used for fixation to ensure a rigid connection between the sensor and the belt bracket. Additionally, rubber pads or damping brackets can be added to isolate steady-state vibrations (such as motor vibration) caused by continuous operation of external vibration sources, thus highlighting the transient beater signal.

[0102] The triaxial accelerometer is placed downstream of the vibratory sweeper because after each beat, if the belt is clean (70°), the vibration decays quickly; if there is still material buildup, the vibration damping is high and decays slowly. The downstream signal can be directly correlated with the cleaning result. The downstream area is relatively "clean," far from the discharge port, reversing rollers, and other major vibration sources, resulting in lower background noise. Furthermore, the downstream feedback signal can be used to adjust the parameters for the next beat in real time, forming a closed-loop logic of "beat → measurement → adjustment."

[0103] S300: Extracts vibration characteristic parameters from transient vibration response signals and calculates the impact intensity index. Vibration characteristic parameters include: peak acceleration a. peak Vibration dominant frequency f dominant Vibration decay time T decay .

[0104] The accelerometer collects the vibration acceleration signal a(t) that varies with time. FFT converts a(t) into a frequency-amplitude relationship A(f), i.e., a spectrum. The dominant vibration frequency f... dominantThe dominant frequency (also known as the primary frequency) refers to the frequency component with the most concentrated energy in the frequency domain of a vibration signal. It can be obtained from a spectrum diagram and reflects the main oscillation characteristics of the belt system under slapping excitation. In belt cleaning control systems, it is an important indicator for judging the state of material accumulation, etc.

[0105] Impact strength index I satisfies the following condition:

[0106] .

[0107] S400: Compare I with the preset target impact strength index I ref The tapping amplitude adjustment ΔA is obtained through a PI control algorithm. ΔA satisfies the following condition:

[0108] ;

[0109] Among them, K p and K i These are the proportional coefficient and the integral coefficient, respectively, with values ​​ranging from 0.3 to K. p ≤0.8, 0.05≤K i ≤0.15. T decay This is the time it takes for the vibration amplitude to decay from its peak value to 10%.

[0110] The impact intensity index serves as a bridge connecting the "slapping action" and the "belt response," and is a "core sensing indicator" for achieving intelligent adaptive control. By integrating the vibration response characteristics of the belt after slapping, it can reflect the energy transfer effect, cleaning effectiveness, and belt structural safety status of the slapping process from multiple dimensions. It not only tells the system "how hard it hits," but also reveals "how the belt feels," making it crucial for achieving "precise cleaning and safe operation" in this technical solution. In this step, a closed-loop feedback control system "guided by target impact intensity" is constructed. This is the core closed-loop control mechanism in the entire adaptive control system, enabling the slapping amplitude to be dynamically adjusted according to the actual response, achieving both precise control of the cleaning effect and dual protection of belt safety.

[0111] In low-temperature environments, the material of belt 70 becomes hard and brittle, and fixed high-amplitude pounding can easily cause surface cracks or joint damage to belt 70. At the same time, insufficient pounding force can also lead to inadequate cleaning. This solution can dynamically adjust the pounding intensity according to the actual cleaning effect, minimizing the problems of "insufficient cleaning" or "excessive impact".

[0112] S500: The current tapping amplitude is adjusted using △A, and the adjusted tapping amplitude is subjected to safety limiting processing. This adjusted amplitude is then output to the vibration motor 40 of the vibrating sweeper for the next tapping control, achieving closed-loop adaptive adjustment of the tapping amplitude. The upper limit of the tapping amplitude is 50mm, and the lower limit is 10mm. These upper and lower limits can be adaptively adjusted according to the actual scenario; this is only an illustrative example.

[0113] Specifically, the amplitude of the next tap is A1 = A0 + △A. If the calculated A1 is within [10mm, 50mm], A1 can be output directly. If it is outside [10mm, 50mm], the closer endpoint value needs to be used as A1.

[0114] In addition, S400 and S500 in this method can also be replaced with:

[0115] S600: If f dominant <60Hz and T decay >400ms, increasing the tapping amplitude of the vibrating sweeper.

[0116] When the beater strikes the belt 70, the belt 70 and its attached materials (material residue, snow, ice, etc.) constitute a dynamic system. Its vibration characteristics (such as frequency components, decay rate, and amplitude) are affected by the "load mass" and "interfacial adhesion strength." Specific characteristics are as follows:

[0117] Clean belts (i.e., belts with little or no material accumulation): lightweight, smooth surface, corresponding to fast vibration response, rich high frequency, and rapid attenuation.

[0118] Material-accumulating belts: These belts have a large added mass and high damping, resulting in a slow vibration response, low-frequency dominance, strong energy absorption, and slow attenuation. Therefore, based on these characteristics, the degree of material accumulation after 70 beats of the belt can be determined.

[0119] S700: If a peak If the weight exceeds 40g and the temperature is less than 5°C, a brittleness risk warning will be issued and the tapping operation will be suspended.

[0120] The detection of a peak acceleration during the impact on belt 70 indicates that it has been subjected to a severe transient impact. The magnitude of the peak acceleration not only signifies excessive impact force but also reflects whether belt 70 can effectively buffer and dissipate impact energy. In low-temperature environments, belt 70's brittleness increases, making it unable to effectively buffer and dissipate impact energy through its own wave deformation, thus leading to a higher peak acceleration. Therefore, combining the peak acceleration with the ambient temperature can generate a brittleness risk warning. This helps to minimize the risk of material fatigue, microcrack propagation, and even joint tearing caused by impact under such conditions.

[0121] The above solution offers the following technical advantages: it automatically adjusts the beating strategy based on ambient temperature to prevent brittle fracture caused by low temperatures, thus significantly extending the service life of belt 70; it utilizes the vibration response characteristics generated after beating to evaluate the cleaning effect and impact intensity in real time, forming a closed-loop control system to improve cleaning accuracy and system stability; and it analyzes the main frequency and decay time to determine the degree of material accumulation and dynamically adjust the beating intensity to achieve a highly efficient and energy-saving operating mode. This technical solution not only solves the drawbacks of traditional beating cleaning devices that rely on a "one-size-fits-all" approach, but also achieves the dual goals of efficient cleaning and belt 70 protection through multi-source sensing, intelligent decision-making, and closed-loop execution.

[0122] The above are merely specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in the present invention should be included within the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be determined by the scope of the claims.

Claims

1. A method for generating the tapping amplitude of a belt vibratory beater sweeper, characterized in that, The method is applied to a belt vibration beater cleaner, and the method includes the following steps: Determine the initial tapping amplitude of the vibratory sweeper based on the temperature of the belt operating environment, and then carry out the tapping operation. A triaxial accelerometer is used to collect the transient vibration response signal of the belt at a preset position downstream of the vibrating beater sweeper; Vibration characteristic parameters are extracted based on the transient vibration response signal, and the impact intensity index is calculated; the vibration characteristic parameters include: peak acceleration a peak Vibration dominant frequency f dominant Vibration decay time T decay ; The impact strength index I satisfies the following condition: ； Compare I with the preset target impact strength index I ref By comparison, the tapping amplitude adjustment ΔA is obtained through a PI control algorithm; ΔA satisfies the following conditions: ； Among them, K p and K i These are the proportional coefficient and the integral coefficient, respectively, with values ​​ranging from 0.3 to K. p ≤0.8, 0.05≤K i ≤0.15; T decay The time it takes for the vibration amplitude to decay from its peak value to 10%; The current tapping amplitude is adjusted using △A, and the adjusted tapping amplitude is subjected to safety limiting. The result is then output to the vibration motor of the vibrating sweeper for the next tapping control, thus achieving closed-loop adaptive adjustment of the tapping amplitude. The upper limit of the tapping amplitude is 50mm, and the lower limit is 10mm. The belt vibrating beater cleaner includes: a mounting bracket, a lifting rod, a vibrating support plate, and a vibration source; The mounting bracket is connected to the mounting support of the belt conveyor so that the mounting bracket is erected above the return belt; The two ends of the hoisting link are rotatably connected to the mounting bracket and the vibrating support plate, respectively; the length of the hoisting link is greater than the distance between the mounting bracket and the return belt; the hoisting link is inclined relative to the return belt, and the end of the hoisting link connected to the vibrating support plate is closer to the downstream of the return belt's direction of movement. The vibration source includes at least one vibration motor and a vibration transmission bracket. The vibration motor is fixed to the inner side of the vibration support plate via a vibration transmission bracket; The vibration transmission bracket includes a motor mounting base and multiple vibration transmission stiffeners. The upper end of the vibration transmission rib is fixedly connected to the motor mounting base, and the lower end of the vibration transmission rib is fixedly connected to the bottom surface and / or side wall surface of the vibration support plate; multiple vibration transmission ribs are staggered with each other; the vibration transmission rib is a trapezoidal plate structure with a smaller upper part and a larger lower part. The hoisting linkage is configured as four; The vibration support plate is provided with a first connecting lug at each of its four corner points, and the mounting bracket is provided with a second connecting lug at each of its four corner points. The lower end of each lifting link is rotatably connected to a first connecting lug, and the upper end is rotatably connected to a corresponding second connecting lug; The rotation center line connecting the two first connecting lugs on the front side of the vibrating plate, the rotation center line connecting the two second connecting lugs on the front side of the mounting bracket, and the two lifting rods connecting them together form a parallelogram mechanism. The rotation center line connecting the two first connecting lugs on the rear side of the vibrating plate, the rotation center line connecting the two second connecting lugs on the rear side of the mounting bracket, and the two lifting rods connecting them also constitute another parallelogram mechanism. The parallelogram mechanism on the front and rear sides has the same structure to keep the vibrating support plate stable during vibration and prevent it from tilting; the front and rear sides are two sides along the width of the belt. It also includes a surface cleaning assembly, which includes a cleaning baffle and a push linkage; The cleaning baffle is an A-shaped symmetrical plate structure, and the side wall of the cleaning baffle slides against the back of the return belt; the cleaning baffle is located on the upstream side closer to the direction of movement of the return belt than the vibrating plate. The two ends of the push rod are rotatably connected to the crossbeams of the vibrating support plate and the cleaning baffle, respectively.

2. The method for generating the tapping amplitude of a belt vibrating beater sweeper according to claim 1, characterized in that, It also includes multiple synchronizing pins; Each of the aforementioned synchronizing pins is simultaneously rotated and passed through the rotating connection ends of any two of the lifting links that need to be synchronized, in order to ensure the synchronicity of the movement of the four lifting links.

3. The method for generating the tapping amplitude of a belt vibrating beater sweeper according to claim 1, characterized in that, The hoisting linkage is configured as two; The lower ends of the two lifting rods are rotatably connected to the midpoint of the length of the front or rear side of the vibrating support plate, respectively. The upper ends of the lifting rods are rotatably connected to the mounting bracket. The front and rear sides are the two sides in the width direction of the belt.

4. The method for generating the beating amplitude of a belt vibrating beater sweeper according to claim 1, characterized in that, Compare I with the preset target impact strength index I ref By comparison, the tapping amplitude adjustment ΔA is obtained through a PI control algorithm; ΔA satisfies the following conditions: ； Among them, K p and K i These are the proportional coefficient and the integral coefficient, respectively, with values ​​ranging from 0.3 to K. p ≤0.8, 0.05≤K i ≤0.15; The current tapping amplitude will be adjusted using △A. The adjusted amplitude will then be subject to safety limiting and output to the vibrating motor of the vibrating sweeper for the next tapping control, thus achieving closed-loop adaptive adjustment of the tapping amplitude. This can be replaced with: If f dominant <60Hz and T decay >400ms, increasing the tapping amplitude of the vibrating sweeper; If a peak If the weight exceeds 40g and the temperature is less than 5°C, a brittleness risk warning will be issued and the tapping operation will be suspended.

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