Asymmetric vibrating feeder

Abstract

The invention provides an asymmetric vibrating feeder, and relates to the field of vibrating conveying equipment. Comprising an asymmetric vibrator and a bearing body used for bearing materials. The asymmetric vibrator comprises at least two groups of pendulum bob groups with parallel rotating axes, and a driving mechanism for driving the pendulum bob groups to rotate and keeping a constant rotating speed ratio and a fixed phase difference between the pendulum bob groups; the asymmetric vibrator is connected with the bearing body and used for driving the bearing body to vibrate in a reciprocating mode in the material conveying direction. Wherein the asymmetric vibrator is configured to generate a periodic excitation force, so that the acceleration of the supporting body in the conveying direction is not equal to the acceleration in the opposite direction in a vibration period. Asymmetric vibration acceleration is achieved through the phase difference of the two pendulum bob sets different in size in the rotating process, materials can be conveyed in a horizontal sliding mode, the situation that the materials are broken due to throwing impact is avoided, layered separation of the mixed materials with the density and the particle size is prevented, and the device is compact in structure, easy to install and low in cost.

Description

Technical Field

[0001] This invention relates to the field of vibratory conveying equipment, and more specifically, to an asymmetric vibratory feeder. Background Technology

[0002] Vibrating feeders are widely used in bulk material conveying processes. Existing vibrating feeders mostly use symmetrical vibrators as the excitation source, with the excitation direction typically forming a certain angle with the material's bearing plane, causing the material to undergo a throwing motion within the trough. This throwing motion results in repeated impacts between the material and the trough during the rising and falling process, easily leading to material breakage. Simultaneously, the mixture undergoes stratification and segregation during the throwing process due to differences in particle density and size, affecting product uniformity. Furthermore, to achieve inclined excitation, traditional equipment requires an additional excitation frame, increasing the overall height and space occupied by the equipment. The generated vertical vibration force also places higher demands on the structural strength of the trough and the vibration resistance of the installation foundation, resulting in bulky, expensive, and complex equipment. Summary of the Invention

[0003] The purpose of this invention is to provide an asymmetric vibrating feeder that has a compact structure, causes little damage to materials, is less likely to cause stratification, and has low requirements for the installation foundation.

[0004] To solve the above-mentioned technical problems, the technical solution adopted by the present invention is as follows: An asymmetric vibrating feeder, comprising: Asymmetric vibrators and load-bearing bodies for carrying materials; The asymmetric vibrator includes at least two sets of pendulums with parallel rotation axes, and a drive mechanism for driving the pendulum sets to rotate and maintaining a constant speed ratio and a fixed phase difference between them. The asymmetric vibrator is connected to the carrier and is used to drive the carrier to reciprocate along the material conveying direction; The asymmetric vibrator is configured to generate periodic excitation force such that the acceleration of the carrier in the conveying direction is not equal to the acceleration in the opposite direction during one vibration cycle.

[0005] Furthermore, in this invention, the direction of the excitation force generated by the asymmetric vibrator is parallel to the bottom plane of the support body.

[0006] Furthermore, in this invention, the asymmetric vibrator includes a first pendulum group and a second pendulum group with different structural parameters or motion parameters; wherein, the centrifugal force amplitude of the first pendulum group is greater than the centrifugal force amplitude of the second pendulum group. The drive mechanism is configured such that the rotational angular velocity of the second pendulum group is N times that of the first pendulum group, where N is a real number greater than 1, and the second pendulum group leads the first pendulum group by a preset angle in the initial phase.

[0007] Furthermore, in this invention, N equals 2, and the preset angle is 90°.

[0008] Furthermore, in this invention, the maximum centrifugal force generated by the second pendulum assembly is 1 / 2 of the maximum centrifugal force generated by the first pendulum assembly.

[0009] Furthermore, in this invention, the asymmetric vibrator also includes a vibration box; the pendulum assembly is disposed inside the vibration box; and the opposite side walls of the carrier are detachably connected to the opposite side walls of the vibration box.

[0010] Furthermore, in this invention, each set of pendulum groups includes at least one pendulum; each of the pendulums is mounted on a corresponding pendulum shaft via a clamping connector; both ends of the pendulums are mounted on the vibration box via bearing seats, and the pendulum shaft and the corresponding bearing seat are connected by an expansion sleeve structure.

[0011] Furthermore, in this invention, the driving mechanism includes: An asynchronous motor is provided on one side of the vibration box and is connected to one of the pendulum shafts via a V-belt drive component. A synchronous toothed belt drive assembly; used to transmit the output power of the asynchronous motor to each of the pendulum groups, and to maintain the constant speed ratio and fixed phase difference between the at least two pendulum groups; The tensioning mechanism is located in the vibration chamber and tensions the synchronous toothed belt drive assembly.

[0012] Furthermore, in this invention, the tensioning mechanism includes: An adjustment component, configured to perform linear displacement adjustment; An elastic element is connected to the adjustment assembly; The mounting base is connected to the elastic element; The tensioning pulley is tensioned with the toothed belt of the synchronous toothed belt drive assembly and is mounted on the mounting base; The elastic element is compressed or released by changing its displacement by operating the adjustment component, and the elastic element applies a constant clamping force to the tension wheel through the tension wheel mounting seat.

[0013] Furthermore, the present invention also includes a vibration isolation device, which is disposed between the vibration box and / or the carrier and the external support structure, for attenuating and isolating the vibration generated by the asymmetric vibrator from being transmitted to the outside.

[0014] The present invention has at least the following advantages or beneficial effects: This invention, by setting up an asymmetric vibrator containing at least two sets of pendulums and configuring a drive mechanism to maintain a constant speed ratio and fixed phase difference, can synthesize a periodic asymmetric excitation force. This excitation force causes the carrier to generate accelerations of different magnitudes along the conveying direction and in the opposite direction within one vibration cycle, thereby driving the material to achieve a periodic composite motion of following and sliding within the carrier. This fundamentally avoids material breakage caused by throwing impacts and prevents the separation of density and particle size in the mixture. Furthermore, the asymmetric vibrator directly drives the carrier to reciprocate along the material conveying direction, ensuring that the excitation direction of the equipment is highly consistent with the conveying direction. It also eliminates the need for the complex excitation frame required in traditional equipment to achieve tilting excitation, significantly reducing the overall height and space occupation of the equipment. At the same time, since the excitation force generated by asymmetric vibration has no vertical component and the horizontal excitation force is relatively small after optimization, the carrier mainly bears alternating stress in the horizontal direction. Therefore, the carrier structure does not need to be excessively strengthened to resist strong vertical impacts, thus enabling a lighter design, saving steel, and reducing manufacturing costs. The equipment in this application has a small overall excitation force, a single direction, and is easy to control. It only requires a simple vibration isolation device to effectively isolate the transmission of vibration to the external foundation, thereby significantly reducing the requirements for the strength and anti-resonance performance of the installation foundation and reducing the investment in foundation construction. It also achieves low-acceleration and low-impact material conveying. Compared with the traditional high-energy-consuming throwing conveying, it can significantly reduce the driving power and achieve the effect of energy-saving operation. Attached Figure Description

[0015] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 A schematic diagram of the overall structure of the asymmetric vibrating feeder provided in the embodiment of the application; Figure 2 This is an enlarged schematic diagram of a portion of the structure of the asymmetric vibrating feeder provided in the embodiment of the application. Figure 3 A schematic diagram of the pendulum assembly provided in the embodiment of the application; Figure 4A schematic diagram of the drive mechanism provided in the embodiments of the application; Figure 5 A schematic diagram of the tensioning mechanism provided in the embodiments of the application; Figure 6 A schematic diagram of the excitation force curve during operation of the asymmetric vibrating feeder provided in the application embodiment.

[0017] Reference numerals in the attached figures: 1. Asymmetric vibrator; 11. First pendulum group; 12. Second pendulum group; 13. Synchronous toothed belt drive assembly; 14. Pendulum shaft; 15. Vibration box; 16. Bearing seat; 17. Expansion sleeve structure; 18. Asynchronous motor; 19. V-belt pulley drive component; 2. Bearing body; 3. Tensioning mechanism; 31. Adjusting screw; 32. Fixed seat; 33. Slide rod; 34. Spring; 35. Slider; 36. Tensioning wheel; 4. Vibration isolation device. Detailed Implementation

[0018] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, 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. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations.

[0019] Therefore, the following detailed description of the embodiments of the invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the invention without inventive effort are within the scope of protection of the invention. Example

[0020] Please refer to Figures 1-6 The figure shown is a schematic diagram of the asymmetric vibrating feeder in an embodiment of the present invention; This embodiment provides an asymmetric vibrating feeder, the core of which lies in achieving a "sliding-following" conveying mode for materials within the conveying trough through asymmetric vibration excitation, completely avoiding throwing motion and the numerous problems it brings. The asymmetric vibrating feeder includes an asymmetric vibrator 1 and a carrier body 2 for carrying the material. The asymmetric vibrator 1 includes at least two sets of pendulums with parallel rotation axes, and a drive mechanism for driving the pendulum sets to rotate and maintaining a constant speed ratio and fixed phase difference between them. This drive mechanism ensures a strict and stable motion coordination relationship between the pendulum sets, driving the entire two sets of pendulums to rotate periodically, achieving an asymmetric acceleration reciprocating vibration form, enabling it to generate a predetermined asymmetric vibration waveform. The asymmetric vibrator 1 is connected to the carrier body 2, driving it to reciprocate along the material conveying direction. The vibrator is configured to generate a periodic excitation force, such that within a complete vibration cycle, the acceleration a1 along the conveying direction of the carrier body 2 is not equal in magnitude to the acceleration a2 along the opposite direction, thereby enabling the material to be conveyed in a directional sliding manner.

[0021] Furthermore, the excitation force generated by the asymmetric vibrator 1 is parallel to the bottom bearing plane of the support body 2, thus completely eliminating the vertical vibration component in traditional equipment. Purely horizontal vibration means that the material is only subjected to horizontal inertial force. As long as the positive acceleration is less than the static friction acceleration threshold between the material and the tank (a1 < μg), the material will move forward with the tank; while when the negative acceleration is greater than this threshold (a2 > μg), the material will slide forward on the tank due to inertia. This cycle repeats, and the material gains a net forward displacement in each vibration cycle, achieving smooth conveying without throwing, thereby fundamentally avoiding material breakage and stratification of the mixture. Simultaneously, horizontal vibration eliminates the need for an inclined excitation frame, greatly reducing equipment height and space requirements, and the horizontal vibration force is more easily absorbed by the vibration isolation device 4, significantly reducing the strength and vibration damping requirements of the installation foundation.

[0022] It should be noted that the material is placed on the support 2, and there is static friction between the contact surfaces of the two. Let the mass of the material be m, the acceleration due to gravity be g, and the coefficient of static friction between the material and the support 2 be μ. Then the maximum static friction force is: F max =μ*m*g; The maximum acceleration that this frictional force can provide to the material is: a max = F max / m = μg. That is, as long as there is no relative sliding between the material and the support 2, the acceleration provided by static friction will not exceed μg.

[0023] When a1 < μg (the positive acceleration is small), when the carrier 2 accelerates in the positive direction with an acceleration a1, the material tends to lag behind the carrier 2 due to inertia. The static friction will try to drive the material to accelerate together. Since a1 ≤ μg, the required acceleration force m*a1 does not exceed the maximum static friction force μmg. Therefore, the static friction is sufficient to make the material completely follow the movement of the carrier 2. There is no relative sliding between the two, and the material moves forward together with the carrier 2.

[0024] When a2 > μg (the reverse acceleration is large), and the support body 2 accelerates in the opposite direction with an acceleration of a2 (i.e., moves rapidly backward), the material tends to maintain its forward momentum due to inertia. The static friction force is directed backward at this time, attempting to pull the material backward with the acceleration. Since a2 > μg, the required acceleration force m*a2 exceeds the maximum static friction force μmg. Therefore, the static friction force is insufficient to provide the material with the same large backward acceleration, and the material will slide forward relative to the support body 2.

[0025] That is, within a complete vibration cycle, in the forward acceleration phase (when 'a' is small), the material moves forward with the carrier 2 (without slippage). In the reverse acceleration phase (when 'a' is large), the material slides forward due to inertia (sliding forward relative to the carrier 2). Although the carrier 2 vibrates back and forth, due to the asymmetry between sliding and following motion, the material gains a net forward displacement in each cycle, thus achieving continuous directional conveying. For different materials with varying coefficients of friction with the surface of the carrier 2, the vibration frequency can be changed by adjusting the torque of the pendulum (by adding counterweights or adjusting the pendulum angle to change the lever arm) or by changing the speed of the drive motor using a frequency converter. Ultimately, this changes the relationship between the magnitude of acceleration 'a' and the product of gravitational acceleration and friction, adapting to the conveying characteristics of different materials and enabling offline or online speed adjustment.

[0026] In a preferred embodiment, the aforementioned asymmetric vibrator 1 includes a first pendulum group 11 and a second pendulum group 12 with different structural or kinematic parameters. The centrifugal force amplitude generated by the first pendulum group 11 (large pendulum group) is greater than that of the second pendulum group 12 (small pendulum group), forming a combination of large and small amplitudes. The drive mechanism is configured such that the rotational angular velocity of the second pendulum group 12 is N times that of the first pendulum group 11 (N>1), and the second pendulum group 12 initially leads the first pendulum group 11 by a preset angle. By carefully designing the amplitude ratio, speed ratio, and phase difference of the two pendulum groups, their synergistic effect can synthesize an ideal, asymmetric periodic excitation force waveform.

[0027] In a specific and optimized embodiment, N equals 2, the preset angle is 90°, and the maximum centrifugal force generated by the second pendulum assembly 12 is half that of the first pendulum assembly 11. This parameter combination has been verified in practice to produce an asymmetric acceleration curve highly suitable for material sliding conveying, such as… Figure 6 As shown.

[0028] In a preferred embodiment, the asymmetric vibrator 1 further includes a sealed vibration chamber 15, specifically comprising an internal box-shaped housing and protective covers disposed above and below the box-shaped housing. The pendulum assembly is disposed inside the box-shaped housing, while the transmission components are located within the protective covers. This design is compact and dustproof. The carrier 2 is a trough-type conveying housing, and its opposite side walls are fixed to the opposite side walls of the vibration chamber 15 via a detachable connection method (e.g., bolt clamping). This clamping installation method allows for certain machining and installation errors, is manufacturing and assembly-friendly, and provides high rigidity, effectively transmitting vibration.

[0029] Inside the vibratory housing 15, each pendulum group includes at least one eccentric pendulum. To achieve precise phase adjustment (for changing the conveying direction), each pendulum is mounted on its pendulum shaft 14 via a clamping coupling (such as a sleeve). Loosening the clamping coupling allows the pendulum to be rotated individually to adjust its phase angle, and re-tightening it secures it. Both ends of the pendulum shaft 14 are supported on the vibratory housing 15 by flange-type bearing seats 16, and the pendulum shaft 14 and the inner ring of the bearing seat 16 are preferably connected by a sleeve structure 17 to ensure tightness and alignment of the shaft connection.

[0030] In a preferred embodiment, the aforementioned drive mechanism specifically includes an asynchronous motor 18, a synchronous toothed belt drive assembly 13, and a tensioning mechanism 3. The asynchronous motor 18 is located on one side of the vibration chamber 15, and its output shaft drives one of the pendulum shafts 14 via a V-belt pulley drive assembly 19 as the primary power input. The synchronous toothed belt drive assembly 13 is responsible for transmitting power from the drive shaft to all pendulum shafts 14, and strictly ensuring a constant 2:1 speed ratio and a fixed 90° phase relationship between each shaft. Its slip-free meshing characteristics ensure precise and stable motion.

[0031] To compensate for minor elongation or slack in the synchronous toothed belt during operation, a tensioning mechanism 3 is provided. This mechanism includes an adjustable assembly with linear displacement, an elastic element (such as a spring 34) connected to it, and a mounting base connected to the elastic element and on which a tensioning pulley 36 is mounted. By rotating the adjusting screw 31 to change its displacement, the spring 34 can be compressed or released. The spring 34 then applies a continuous and constant clamping force to the tensioning pulley 36 through the mounting base, thereby always keeping the synchronous toothed belt in optimal tension and ensuring transmission accuracy.

[0032] One specific implementation includes a fixed base 32, a slide rod 33, a spring 34, and an adjusting screw 31. Two fixed bases 32 are fixed to the vibration chamber 15, and the slide rod 33 is fixed between the two fixed bases 32. Two sliders 35 are slidably mounted on the slide rod 33. The spring 34 abuts between the two sliders 35 and is sleeved on the outside of the slide rod 33. The adjusting screw 31 is threaded through one of the fixed bases 32 and connected to one of the sliders 35. The other slider 35 is equipped with a tensioning wheel 36. This structure cleverly transforms manual adjustment into control of the preload of the spring 34, thereby achieving automatic and constant tension output.

[0033] To further isolate the impact of equipment vibration on the external structure, a vibration isolation device 4 is also included. This vibration isolation device 4 is installed between the vibration chamber 15 and / or the load-bearing body 2 and the external supporting structure (such as a foundation or steel frame) to attenuate and isolate the vibration generated by the asymmetric vibrator 1 from transmission to the outside. The vibration isolation device 4 can be composed of components such as rubber springs 34, metal springs 34, or air springs 34. Figure 1 As shown, the vibration isolation device in this embodiment is fixed by connecting lugs provided on the outer walls of the vibration box 15 and the bearing 2. The vibration isolation device includes a rod and rubber springs 34 provided at both ends of the rod, which are used to support the entire equipment and isolate vibration. They are mainly distributed at the four corners of the entire equipment. Since the vibration in this application is mainly horizontal and the excitation force is relatively small after optimization, only simple vibration isolation measures are needed to achieve excellent vibration isolation effect, further reducing the investment and maintenance costs of the installation foundation.

[0034] In one specific embodiment, two sets of pendulum groups are arranged in parallel, namely a first pendulum group 11 (large pendulum group) and a second pendulum group 12 (small pendulum group). Each pendulum group consists of two eccentric pendulums, and the four pendulums are arranged in a rectangular shape. Each pendulum is fixed to its respective pendulum shaft 14 by a sleeve structure 17. The two ends of the pendulum shaft 14 are supported on the vibration box 15 by flange-type bearing seats 16, and the shaft and the inner ring of the bearing seat 16 are also fastened by sleeves. The drive mechanism consists of an asynchronous motor 18, a V-belt drive component 19, a synchronous toothed belt drive assembly 13, and a tensioning mechanism 3. The asynchronous motor 18 is fixed to one side of the box and drives the pendulum shaft 14 of one of the second pendulum groups 12 through the V-belt drive component 19. Figure 4As shown, synchronous toothed pulleys are fixed on the shaft, the shaft of the second pendulum group 12, and the shafts of the two first pendulum groups 11. One or more idler pulleys are also provided on the circumference, forming a closed-loop transmission system connected by synchronous toothed belts. The gear ratio of this system is precisely calculated to ensure that the rotational speed of the second pendulum group 12 is twice that of the first pendulum group 11 (ω2=2ω1), and by installing aligned gears, it is ensured that the second pendulum group 12 leads the first pendulum group 11 by 90 degrees in initial phase (θ2=2θ1+90°). Simultaneously, by designing the static torque (m2r2) of the second pendulum group 12 to be 1 / 8 of the static torque (m1r1) of the first pendulum group 11, it is ensured that the maximum centrifugal force generated by the second pendulum group 12 during operation is 1 / 2 that of the first pendulum group 11.

[0035] When the equipment is working, the asynchronous motor 18 drives two sets of pendulum sets to rotate at a fixed speed ratio and phase difference. The resultant force of the centrifugal force generated by the two in the horizontal direction (parallel to the bottom surface of the support body 2) forms a force like... Figure 6 The asymmetric periodic excitation force F(t) is shown. This force acts on the carrier 2, causing it to vibrate horizontally. Within one cycle T, the peak value of the excitation force is smaller in the positive half-cycle (conveying direction), corresponding to a carrier acceleration a1 < μg (μ is the friction coefficient between the material and the trough, g is the acceleration due to gravity), and the material moves forward with the trough; the peak value is larger in the negative half-cycle (opposite direction), corresponding to a carrier acceleration a2 > μg, and the material slides forward on the trough due to inertia. The material gains a net forward displacement in each cycle, thus achieving smooth and low-damage conveying. When it is necessary to change the conveying direction, simply stop the machine, loosen the expansion sleeve of the pendulum in the first pendulum group 11, rotate it on the shaft by about 180°, and then relock it. At this time, the phase relationship between the two pendulum groups changes, resulting in... Figure 6 The excitation force waveform shown is flipped on the time axis, so that the net sliding force on the material is reversed, thus realizing reverse conveying.

[0036] The beneficial effects of the embodiments of this application are as follows: This application utilizes a horizontal asymmetric vibration bearing 2, requiring only a simple trough and pipe structure, eliminating the need for an additional vibration frame that would increase the equipment's size. Furthermore, since it only vibrates horizontally, the vibration isolation device 4 effectively eliminates the impact of vibration on the supporting structure, thus reducing the requirements and investment for the installation foundation. The asymmetric feeder's acceleration 'a' only needs to overcome the product of gravitational acceleration 'g' and friction factor 'u', resulting in a small acceleration and requiring less material to increase equipment strength. Due to its low strength requirements, the asymmetric feeder can employ a lightweight design, resulting in a smaller self-weight for the same conveying capacity and less energy required to drive the bearing 2's vibration, thus saving energy. The material in the asymmetric feeder experiences only horizontal vibration, without vertical vibration force. Driven by horizontal asymmetric vibration, the material slides and is conveyed, successfully transforming the material conveying mode from "throwing" to "sliding." Therefore, the material does not bounce or fall, making it less prone to breakage; the material slides and moves horizontally without stratification or segregation. Since the equipment is driven by asymmetric vibration force, the peak waveform of the large excitation force can be seen from the excitation force period curve. Therefore, the large pendulum group and the small pendulum group can reverse the acceleration relationship by changing the phase relationship through the toothed belt pulley. This can achieve the flipping of the peak waveform of the large excitation force in the direction of the coordinate axis, thereby reversing the material conveying direction. The expansion sleeve structure 17 adopted in this design can achieve fine and free adjustment of the phase angle.

[0037] The above are merely preferred embodiments of the present invention and are not intended to limit the present invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. An asymmetric vibrating feeder, characterized in that, include: Asymmetric vibrators and load-bearing bodies for carrying materials; The asymmetric vibrator includes at least two sets of pendulums with parallel rotation axes, and a drive mechanism for driving the pendulum sets to rotate and maintaining a constant speed ratio and a fixed phase difference between them. The asymmetric vibrator is connected to the carrier and is used to drive the carrier to reciprocate along the material conveying direction; The asymmetric vibrator is configured to generate periodic excitation force such that the acceleration of the carrier in the conveying direction is not equal to the acceleration in the opposite direction during one vibration cycle.

2. The asymmetric vibrating feeder according to claim 1, characterized in that, The direction of the excitation force generated by the asymmetric vibrator is parallel to the bottom plane of the support body.

3. The asymmetric vibrating feeder according to claim 1, characterized in that, The asymmetric vibrator includes a first pendulum group and a second pendulum group with different structural or kinematic parameters; wherein the centrifugal force amplitude of the first pendulum group is greater than that of the second pendulum group. The drive mechanism is configured such that the rotational angular velocity of the second pendulum group is N times that of the first pendulum group, where N is a real number greater than 1, and the second pendulum group leads the first pendulum group by a preset angle in the initial phase.

4. The asymmetric vibrating feeder according to claim 3, characterized in that, The value of N is 2, and the preset angle is 90°.

5. The asymmetric vibrating feeder according to claim 3, characterized in that, The maximum centrifugal force generated by the second pendulum assembly is 1 / 2 of the maximum centrifugal force generated by the first pendulum assembly.

6. The asymmetric vibrating feeder according to claim 2, characterized in that, The asymmetric vibrator also includes a vibration box; the pendulum assembly is disposed inside the vibration box; the opposite side walls of the carrier are detachably connected to the opposite side walls of the vibration box.

7. The asymmetric vibrating feeder according to claim 6, characterized in that, Each set of pendulums includes at least one pendulum; each of the pendulums is mounted on a corresponding pendulum shaft via a clamping connector; both ends of each pendulum are mounted on the vibration box via bearing seats, and the pendulum shaft and the corresponding bearing seat are connected by an expansion sleeve structure.

8. The asymmetric vibrating feeder according to claim 6, characterized in that, The drive mechanism includes: An asynchronous motor is provided on one side of the vibration box and is connected to one of the pendulum shafts via a V-belt drive component. A synchronous toothed belt drive assembly; used to transmit the output power of the asynchronous motor to each of the pendulum groups, and to maintain the constant speed ratio and fixed phase difference between the at least two pendulum groups; The tensioning mechanism is located in the vibration chamber and tensions the synchronous toothed belt drive assembly.

9. The asymmetric vibrating feeder according to claim 8, characterized in that, The tensioning mechanism includes: An adjustment component, configured to perform linear displacement adjustment; An elastic element is connected to the adjustment assembly; The mounting base is connected to the elastic element; The tensioning pulley is tensioned with the toothed belt of the synchronous toothed belt drive assembly and is mounted on the mounting base; The elastic element is compressed or released by changing its displacement by operating the adjustment component, and the elastic element applies a constant clamping force to the tension wheel through the tension wheel mounting seat.

10. The asymmetric vibrating feeder according to claim 6, characterized in that, It also includes a vibration isolation device, which is disposed between the vibration box and / or the load-bearing body and the external support structure, for attenuating and isolating the vibration generated by the asymmetric vibrator from being transmitted to the outside.

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