Annular bending-twisting variable-frequency vibration absorber based on planetary gear and design method thereof

Abstract

The invention relates to an annular bending-twisting variable-frequency vibration absorber based on a planetary gear and a design method thereof. The vibration absorber comprises a rigidity-variable elastic device and an annular mass block. The variable-rigidity elastic device comprises an inner ring, an outer ring and a plurality of planetary gear units. The planetary gear unit comprises a gear ring, a sun gear and a plurality of planetary gears; the outer side face of the gear ring is provided with two outwards-extending bosses used for connecting the inner ring and the outer ring. The connecting position of the gear ring and the inner ring is a first connecting position, the connecting position of the gear ring and the outer ring is a second connecting position, the first connecting position and the second connecting position are located in the same radial direction of the outer ring, or the first connecting position and the second connecting position are located in two different radial directions of the outer ring. According to the scheme, the beneficial effect that the vibration absorption frequency is adjustable in a large range can be achieved, and the vibration absorption device can be independently used and can also be used for bending-torsional vibration control over trusses, pipelines, shaft systems and the like or serve as a variable-stiffness structure of a variable-frequency signal generator and a sensor.

Description

Technical Field

[0001] This invention relates to the field of vibration control technology, and in particular to a ring-shaped bending-torsional frequency-converting vibration absorber based on planetary gears and its design method. Background Technology

[0002] In the design and operation of large rotating machinery such as ships, aircraft, and hydropower plants, vibration of the pipeline shaft system remains a core challenge. The causes of shaft vibration are complex, stemming not only from imbalances and misalignments within the shaft itself and internal excitations generated by components such as bearings and gears, but also from the coupling effects of external factors such as fluid pressure pulsations within the pipeline and deformation of the equipment foundation. Such intense shaft vibration can trigger a series of serious consequences. In terms of mechanical components, it can directly lead to premature failure of critical components such as bearings and seals, and may also cause loosening and fatigue cracking of connecting pipeline joints. In terms of acoustic performance, it is a major noise source that degrades the acoustic stealth performance of underwater vehicles and reduces sonar detection range, severely impacting the detection and stealth capabilities of underwater vehicles in complex underwater environments.

[0003] To effectively control the transmission of vibrations in pipeline shafting systems and ensure the safe and stable operation of the system, vibration isolation and damping technologies have become crucial. Taking ship propulsion systems as an example, elastic bases and flexible couplings are commonly used to isolate the transmission of main engine vibrations to the shafting and hull. Traditional passive vibration isolation measures can achieve significant results in the mid-to-high frequency range, but they fall short when dealing with the unavoidable low-frequency torsional and lateral resonances during shafting start-up and shutdown. Moreover, in pursuing vibration isolation efficiency, traditional passive vibration isolation measures often have to sacrifice the system's axial load-bearing capacity and impact resistance. This is a problem that cannot be ignored for modern high-end equipment, as it not only requires good vibration isolation performance but also has high requirements for axial load-bearing capacity and impact resistance. Therefore, developing a pipeline shafting vibration control technology that can balance low-frequency vibration isolation, high load-bearing capacity, and high reliability has become an urgent need for improving the overall performance of modern high-end equipment.

[0004] To compensate for the shortcomings of traditional vibration isolation technology in low-frequency and specific frequency band control, various vibration absorption technologies have emerged and gradually become an important component of pipeline shaft vibration control systems. Vibration absorbers and vibration isolators operate on different principles. Vibration isolators aim to "block" the transmission path of vibration, while vibration absorbers "absorb" and dissipate vibration energy by generating a resonance at their natural frequency that is out of phase with the controlled structure. For example, for the prominent torsional vibration problem in shaft systems, dynamic vibration absorbers installed on the shaft can effectively suppress the resonance peaks caused by engine order vibrations and propeller blade frequency excitation, thus alleviating torsional vibration of the shaft to a certain extent.

[0005] However, traditional passive vibration absorbers have a significant drawback: their absorption frequency band is fixed. Once the shaft speed changes and deviates from the design conditions, their vibration control effectiveness drops sharply, failing to meet the vibration control requirements of the shaft under different operating conditions. To overcome this deficiency, adaptive tuning vibration absorption technology and active vibration absorption devices have been further developed. These advanced technologies can dynamically adjust their natural frequency or directly apply action force by monitoring the shaft speed and vibration state in real time, thereby achieving efficient and precise suppression of specific order vibrations under varying operating conditions. Organically combining these advanced vibration absorption technologies with foundation vibration isolation systems to form a "active-passive fusion" composite vibration control scheme has become a cutting-edge research direction for solving broadband, variable-condition vibration problems in pipeline shaft systems, and is expected to provide more reliable guarantees for the stable operation of large rotating machinery. Summary of the Invention

[0006] The technical problem to be solved by the present invention is to provide a ring-shaped bending and torsion frequency-converting vibration absorber based on planetary gears and its design method.

[0007] To achieve the above-mentioned objectives, the present invention provides a ring-shaped bending-torsional frequency-converting vibration absorber based on planetary gears, comprising: a variable stiffness elastic device, and a ring-shaped mass block connected to the outside of the variable stiffness elastic device. The variable stiffness elastic device includes: an inner ring, an outer ring, and multiple planetary gear units arranged between the inner ring and the outer ring; The planetary gear unit includes: a ring gear, a sun gear, and multiple planetary gears; Two protruding bosses for connecting the inner ring and the outer ring are provided at relative positions on the outer side of the gear ring. The position where the protruding boss of the gear ring connects with the inner ring is the first connection position, and the position where it connects with the outer ring is the second connection position. The first connection position and the second connection position are located in the same radial direction of the outer ring, or the first connection position and the second connection position are located in two different radial directions of the outer ring.

[0008] According to one aspect of the invention, the annular bending-torsional frequency-converting vibration absorber is based on an inner ring sleeved on a pipeline shaft structure to suppress radial and / or torsional vibrations of the pipeline shaft structure.

[0009] According to one aspect of the invention, the absorption frequency range and adjustment factor of the annular bending-torsional frequency absorber are adjusted by changing the material of at least one structure in the variable stiffness elastic device; and / or, the absorption frequency range and adjustment factor of the annular bending-torsional frequency absorber are adjusted by changing the gear ring structure parameters of the gear ring in the planetary gear unit; wherein the gear ring structure parameters include: the radius of the gear ring and the radial thickness of the gear ring.

[0010] According to one aspect of the invention, in the variable stiffness elastic device, two adjacent planetary gear units are arranged in a mirror-symmetric manner; or, in the variable stiffness elastic device, the included angle between the two radial directions where the first connection position and the second connection position of all planetary gear units are located is consistent, and the first connection position and the second connection position are periodically distributed along the clockwise / counterclockwise direction.

[0011] According to one aspect of the present invention, a first hollow structure is provided at the position where the inner ring connects with the outer protrusion, penetrating the inner ring body along the inner ring axial direction. The position where the outer ring connects to the protruding boss is provided with a second hollow structure that penetrates the outer ring body along the outer ring axis.

[0012] According to one aspect of the invention, in the planetary gear unit, a driver may be optionally employed to drive the sun gear and a plurality of planetary gears to rotate within the gear ring.

[0013] According to one aspect of the invention, the driver is configured in a one-to-one correspondence with the planetary gear unit, or multiple planetary gear units are connected to the same driver based on a transmission structure.

[0014] According to one aspect of the invention, the annular mass block is composed of a plurality of equally divided mass block portions; The inner ring is composed of multiple equally divided inner ring sections; The outer ring is composed of multiple equally divided outer ring sections; The number of the mass block portion, the inner ring portion, and the outer ring portion is the same.

[0015] According to one aspect of the invention, it further includes: a clamp; The clamps are located on the outside of the annular mass block and are used to simultaneously fasten multiple mass block sections, multiple inner ring sections, and multiple outer ring sections. The end of the mass block portion is provided with a first docking structure for docking and positioning; The end of the inner ring portion is provided with a second docking structure for docking and positioning; The outer ring portion is provided with a third docking structure for docking and positioning at its end; There are four planetary gears, and the four planetary gears are arranged at equal intervals along the circumference of the sun gear.

[0016] To achieve the above-mentioned objective, this invention provides a design method for the aforementioned planetary gear-based annular bending-torsional frequency converter vibration absorber, comprising the following steps: S1. Obtain the outer diameter and vibration frequency of the pipeline shaft system structure; S2. Based on the outer diameter of the pipeline shaft system structure, the inner diameter of the inner ring is determined, as well as the absorption frequency range and adjustment factor of the annular bending torsion frequency absorber are determined; S3. Based on the obtained vibration absorption frequency range and adjustment factor, design the gear ring structure parameters and select the materials for each structure in the variable stiffness elastic device; S3. Based on the obtained gear ring structure parameters, design the dimensions and meshing transmission parameters of the sun gear and planetary gears to complete the construction of the planetary gear unit; S4. Obtain the number and arrangement of planetary gear units, and determine the outer diameter of the inner ring, the inner and outer diameters of the outer ring, and the inner and outer diameters of the annular mass block based on the obtained planetary gear unit dimensions, thus completing the construction of the annular bending-torsional frequency converter vibration absorber.

[0017] According to one aspect of the present invention, the annular bending-torsional frequency-converting vibration absorber of this invention can achieve the beneficial effect of a wide range of adjustable vibration absorption frequencies. It can simultaneously adjust the radial and torsional resonant frequencies and can be used as a standalone integrated vibration absorber or for multi-directional vibration control of systems such as trusses, pipelines, and shafts. Furthermore, it can also serve as a variable stiffness structure for frequency converters and sensors, making this invention widely applicable.

[0018] According to one aspect of the present invention, the vibration absorption frequency range of this solution can be autonomously adjusted in real time, enabling the comprehensive vibration absorption performance of pipeline shaft system structures (including pipelines and shaft system structures) in multiple directions, with low frequency broadband and active adjustability.

[0019] According to one aspect of the present invention, the vibration absorption frequency range and adjustment factor can be flexibly adjusted by flexibly adjusting the material of at least one structure in the variable stiffness elastic device and / or by changing the gear ring structure parameters in the planetary gear unit, thereby effectively improving the flexibility and applicability of the present invention. Attached Figure Description

[0020] Figure 1 This is a structural diagram of the annular bending-torsional frequency converter vibration absorber of the present invention; Figure 2 This is a structural diagram of the planetary gear unit of the present invention, wherein, Figure 2 (a) shows a schematic diagram of the position of the planetary gears in a low-stiffness state of the planetary gear unit. Figure 2 (b) shows a schematic diagram of the position of the planetary gears in a high-rigidity state of the planetary gear unit; Figure 3 This is a diagram of a metamaterial pipeline or metamaterial shaft structure formed by connecting the annular bending-torsional frequency-converting vibration absorber of the present invention with a pipeline or shaft structure. Figure 4 This is a diagram showing the arrangement of a planetary gear unit according to one embodiment of the present invention; Figure 5 This is a diagram showing the arrangement of a planetary gear unit according to another embodiment of the present invention; Figure 6 This is a diagram showing the arrangement of a planetary gear unit according to another embodiment of the present invention; Figure 7 This is a diagram illustrating one driving method of the annular bending-torsional frequency converter vibration absorber of the present invention, wherein... Figure 7 (a) shows the front view of the annular bending-torsional frequency converter vibration absorber. Figure 7 (b) shows the rear view of the annular bending-torsional frequency converter vibration absorber. Figure 7 (c) shows a side view of the annular bending-torsional frequency converter vibration absorber; Figure 8 This is a disassembled structural diagram of the annular bending-torsional frequency converter vibration absorber of the present invention, which is easy to install; Figure 9 This is an installation structure diagram of the annular bending-torsional frequency converter vibration absorber and its piping or shaft system according to the present invention; Figure 10 This is a physical image of the annular bending-torsional frequency converter vibration absorber of the present invention; Figure 11 The figure shows the experimental results of the radial frequency response of the annular bending-torsional frequency converter vibration absorber of the present invention. Figure 11 (a) shows the method of applying the radial frequency in the radial frequency response experiment. Figure 11 (b) shows the frequency response curves of the annular bending-torsional frequency absorber under different rotation angles of the planetary gear in the radial frequency response experiment; Figure 12 The torsional frequency response experiment and results of the annular bending-torsional frequency converter vibration absorber of the present invention are as follows: Figure 12 (a) shows the method of applying the torsional frequency in the torsional frequency response experiment. Figure 12 (b) shows the frequency response curves of the annular bending-torsional frequency absorber under different rotation angles of the planetary gear in the torsional frequency response experiment; Figure 13 The figures show the finite element simulation results of the radial and torsional frequency responses of the metamaterial pipeline or metamaterial shaft system structure of the present invention. Figure 13 (a) A graph showing the finite element simulation results of the radial frequency response. Figure 13 (b) shows the finite element simulation results of the torsional frequency response. Detailed Implementation

[0021] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the embodiments will be briefly described below. Obviously, the drawings described below are merely some embodiments of the present invention, and those skilled in the art can obtain other drawings based on these drawings without creative effort.

[0022] In describing embodiments of the present invention, the terms "longitudinal," "lateral," "upper," "lower," "front," "rear," "left," "right," "vertical," "horizontal," "top," "bottom," "inner," and "outer" express orientations or positional relationships based on the orientations or positional relationships shown in the relevant drawings. They are only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, the above terms should not be construed as limitations on the present invention.

[0023] The present invention will now be described in detail with reference to the accompanying drawings and specific embodiments. The embodiments cannot be described in detail here, but the embodiments of the present invention are not limited to the following embodiments.

[0024] like Figure 1 As shown, according to one embodiment of the present invention, a planetary gear-based annular bending-torsional frequency-converting vibration absorber includes: a variable stiffness elastic device 1, and an annular mass block 2 connected to the outside of the variable stiffness elastic device 1; in this embodiment, the variable stiffness elastic device 1 includes: an inner ring 11, an outer ring 12, and a plurality of planetary gear units 13 arranged between the inner ring 11 and the outer ring 12; wherein, the opposite ends of the planetary gear units 13 are fixedly connected to the outer side of the inner ring 11 and the inner side of the outer ring 12, respectively, to achieve fixed installation of the planetary gear units 13 between the inner ring 11 and the outer ring 12. In this embodiment, the planetary gear units 13 are fixedly connected to the inner ring 11 and the outer ring 12 by integral molding, or they can be fixed to each other by welding, riveting, threaded connection, bonding, snap-fitting, etc., to improve the flexibility of the construction and use of this solution.

[0025] In this embodiment, the inner ring 11, the outer ring 12, and the annular mass block 2 can all be configured as a circular ring structure. This ensures the structural uniformity of this solution in the circumferential direction, so that the annular bending and torsion frequency converter vibration absorber of this solution has a consistent vibration absorption capacity at all positions, making the vibration absorption performance of this solution more beneficial.

[0026] In this embodiment, the planetary gear unit 13 includes a ring gear 131, a sun gear 132, and a plurality of planetary gears 133. The sun gear 132, planetary gears 133, and ring gear 131 are connected by meshing, thus the rotation of the sun gear 132 drives the rotation and position change of the planetary gears 133 on the ring gear 131. The plurality of planetary gears 133 are evenly distributed at equal intervals around the sun gear 132 to ensure the structural symmetry of the planetary gear unit 13.

[0027] In this embodiment, to facilitate the fixed connection of the planetary gear unit 13, two protruding bosses 131a for connecting the inner ring 11 and the outer ring 12 are provided at opposite positions on the outer side of the gear ring 131. In this embodiment, the position where the protruding bosses 131a of the gear ring 131 are connected to the inner ring 11 is the first connection position, and the position where they are connected to the outer ring 12 is the second connection position. The first connection position and the second connection position are located in the same radial direction of the outer ring 12, or the first connection position and the second connection position are located in two different radial directions of the outer ring 12, so that after the planetary gear unit 13 is installed, the extension direction of its protruding bosses 131a can have an angle with the radial direction of the outer ring 12.

[0028] Through the above settings, different arrangement methods can be used to make the annular torsional frequency converter of this solution have different matching ranges for the absorption frequency of torsional vibration, thus making this solution more flexible and superior in vibration absorption performance. Specifically, by changing the connection method of the planetary gear unit 13, the distribution of its high stiffness position and low stiffness position can be made different, so that the component of torsional stiffness exhibits different changes, thereby achieving matching for the absorption frequency of torsional vibration. In particular, by arranging the first connection position and the second connection position in different radial directions, different included angles can be formed between adjacent planetary gear units 13, thus making the matching for the absorption frequency more flexible and diverse.

[0029] In this embodiment, the annular mass block 2 and the outer ring 12 can be fixed to each other by means of bonding, welding, locking connectors, nesting, etc., so as to maintain a reliable and tight connection.

[0030] Combination Figure 1 and Figure 2As shown, according to one embodiment of the present invention, there are four planetary gears 133, and the four planetary gears 133 are arranged at equal angular intervals along the circumference of the sun gear 132. Thus, the system is divided into two groups of two planetary gears 133 each. The center of each group of planetary gears 133 is on the same straight line as the center of the sun gear 132, and the lines connecting the centers of the two groups of planetary gears 133 are perpendicular to each other. Specifically, the centers of the first group of planetary gears 133 are respectively... A 1 and A 2. The centers of the second set of planetary gears 133 are respectively B 1 and B 2, and the center of the sun gear 132 is O Then the line connecting the centers of the gears A 1- O - A 2 and B 1- O - B 2 are mutually perpendicular.

[0031] Combination Figure 1 and Figure 3 As shown, according to one embodiment of the present invention, the annular bending-torsional frequency-converting vibration absorber is based on an inner ring 11 sleeved on a pipeline shaft system structure to suppress radial and / or torsional vibrations of the pipeline shaft system structure. Specifically, the vibration transmission path can be directly transmitted to the annular mass block 2 along the direction of the inner ring 11, the planetary gear unit 13, and the outer ring 12, thereby achieving vibration absorption. In this embodiment, the pipeline shaft system structure includes: pipelines and shafts; furthermore, the annular bending-torsional frequency-converting vibration absorber can be periodically installed along the axial direction of the pipeline or shaft system to form a metamaterial pipeline or metamaterial shaft system structure, thereby further improving the suppression effect on radial and axial torsional vibrations of the pipeline and shaft system.

[0032] According to one embodiment of the present invention, the vibration absorption frequency range and adjustment factor (i.e., the adjustment factor of the maximum vibration absorption frequency relative to the minimum vibration absorption frequency) of the annular bending-torsional frequency converter can be adjusted by changing the material of at least one structure in the variable stiffness elastic device 1. Specifically, using high-stiffness materials to manufacture the sun gear and planetary gears can shift the highest resonant frequency of the annular bending-torsional frequency converter towards higher frequencies. Of course, other materials in the variable stiffness elastic device 1 can also be adjusted, and the specific adjustments can be determined according to the usage environment and load. In this embodiment, using high-stiffness materials for the sun gear and planetary gears mainly increases the maximum vibration absorption frequency, but has a relatively small impact on the minimum vibration absorption frequency. Therefore, the adjustment factor of this solution can be increased by using high-stiffness materials.

[0033] Furthermore, the absorption frequency range and adjustment factor of the annular torsional frequency converter can be adjusted by changing the structural parameters of the gear ring 131 in the planetary gear unit 13. The gear ring structural parameters include the radius and radial thickness of the gear ring 131. Specifically, a larger radius and thinner radial thickness of the gear ring 131 result in a wider absorption frequency range and a larger adjustment factor for the annular torsional frequency converter. In particular, increasing the radius and decreasing the radial thickness of the gear ring 131 can shift the lowest resonant frequency of the absorber to a lower frequency, while keeping the highest resonant frequency essentially unchanged.

[0034] like Figure 4 , Figure 5 As shown, according to one embodiment of the present invention, in the variable stiffness elastic device 1, two adjacent planetary gear units 13 are arranged in a mirror-symmetric manner; specifically, when the first connection position of the gear ring 131 connecting to the inner ring 11 and the second connection position connecting to the outer ring 12 are in the same radial direction of the outer ring 12, they can be equally spaced in the circumferential direction of the outer ring 12 based on an equal-interval angle, thereby making them present a mirror-symmetric manner, see [reference]. Figure 4 As shown; of course, when the first connection position connecting the gear ring 131 to the inner ring 11 and the second connection position connecting it to the outer ring 12 are located in different radial directions of the outer ring 12, two mirror-arranged planetary gear units 13 can be used as a group, and multiple groups of planetary gear units 13 can be arranged at equal intervals in the circumferential direction of the outer ring 12 to achieve mutual installation and arrangement. Among them, in the same group of planetary gear units 13, from the inner ring 11 to the outer ring, the extension direction of the protruding bosses 131a of the two planetary gear units 13 is arranged in a way that is either far away from each other or close to each other; thus, based on the mirror-arranged planetary gear unit group 13 and the equal-interval distribution of multiple groups of planetary gear units 13, the two groups of planetary gear units 13 also have a mirror symmetry effect, see Figure 5 As shown.

[0035] In another embodiment, in the variable stiffness elastic device 1, the included angles between the two radial directions of the first and second connection positions of all planetary gear units 13 are consistent, and the first and second connection positions are periodically distributed along a clockwise / counterclockwise direction. This results in the periodically arranged planetary gear units 13 exhibiting the same arrangement angle between the inner ring 11 and the outer ring 12. (See [reference]) Figure 6 As shown.

[0036] like Figure 1As shown, according to one embodiment of the present invention, a first hollow structure 11a is provided at the position where the inner ring 11 connects to the outer protrusion 131a, penetrating the body of the inner ring 11 along the axial direction. The first hollow structure 11a can be a through-hole structure, and the cross-section of the through-hole structure can be rectangular, arc-shaped, elliptical, or similar, with a length greater than the width. Alternatively, a mesh structure can be further filled into the through-hole structure to give its hollow portion different support and conduction capabilities, resulting in controllable mechanical properties at the position where it connects to the outer protrusion 131a. In this embodiment, the cross-sectional length of the first hollow structure 11a is greater than the circumferential dimension of the outer protrusion 131a's cross-section along the inner ring 11, so that the setting range of the first hollow structure 11a is greater than the end face range of the outer protrusion 131a. This reduces the rigidity of the connection position, adjusts the resonant frequency, and makes the vibration absorption performance of this solution more beneficial.

[0037] In this embodiment, a second hollow structure 12a is provided at the position where the outer ring 12 connects to the protruding boss 131a, penetrating the body of the outer ring 12 along its axial direction. The second hollow structure 12a can be a through-hole structure, with the cross-section of the through-hole structure being rectangular, arc-shaped, elliptical, or similar, where the length of the cross-section is greater than the width. Alternatively, a mesh structure can be further filled into the through-hole structure to give its hollow portion different support and conduction capabilities, resulting in controllable mechanical properties at the position where it connects to the protruding boss 131a. In this embodiment, the cross-sectional length of the second hollow structure 12a is greater than the circumferential dimension of the protruding boss 131a, so that the setting range of the second hollow structure 12a is larger than the end face range of the protruding boss 131a. This reduces the rigidity of the connection position, allowing for adjustment of the resonant frequency and making the vibration absorption performance of this solution more beneficial.

[0038] like Figure 2 As shown, according to one embodiment of the present invention, in the planetary gear unit 13, a driver may be optionally employed to drive the sun gear 132 and a plurality of planetary gears 133 to rotate within the gear ring 131. In this embodiment, the protruding boss 131a of the gear ring 131 is the force application point of the planetary gear unit 13, and is angular. θ express y The angle between the shaft and the line connecting the center of any set of planetary gears 133 (i.e. θ =∠ A 1 Oy Therefore, under the active driving action of the actuator, the stiffness of the entire planetary gear unit 13 can be adjusted during the rotation of the sun gear 132 and the two sets of planetary gears 133. θ When the angle is 0°, the stiffness of planetary gear unit 13 is at its maximum; when θWhen the angle is 45°, the stiffness of planetary gear unit 13 is at its minimum.

[0039] In this embodiment, the driver and planetary gear unit 13 are configured in a one-to-one correspondence. Alternatively, multiple planetary gear units 13 are connected to the same driver based on a transmission structure, wherein the transmission structure can be a gear transmission structure. In this embodiment, when using a gear transmission structure, some planetary gear units 13 can be connected to the same gear transmission structure, or all planetary gear units 13 can be connected to the same gear transmission structure, thus achieving flexibility in driver configuration.

[0040] like Figure 7 As shown, according to one embodiment of the present invention, the first hollow structure 11a and the second hollow structure 12a can also be used to install a motor and a coupling gear, thereby driving the annular bending-torsional frequency converter to adjust the resonant frequency. To balance the connection and the effect of adjusting the resonant frequency, vibration isolation treatment can be applied between the positions connected to the first hollow structure 11a and the second hollow structure 12a based on the aforementioned mesh structure or rubber ring, so as to effectively ensure the vibration absorption performance of this solution.

[0041] In this embodiment, when the driver and planetary gear units 13 are arranged in a one-to-one correspondence, the driver's support can be connected based on the first hollow structure 11a and the second hollow structure 12a corresponding to the planetary gear unit 13; wherein, the output shaft of the driver is directly connected to the center of the sun gear 132. When multiple planetary gear units 13 are connected to the same driver based on the transmission structure, the driver and gear transmission structure can be installed based on the first hollow structure 11a and the second hollow structure 12a within the relevant range; wherein, the driver and gear transmission structure are arranged on the same side or opposite sides of the planetary gear units 13, the driver is connected to the center of the sun gear 132 of one of the planetary gear units 13, and the gear transmission structure is connected to the sun gear 132 of each planetary gear unit 13, thereby achieving simultaneous operation under the same driver. In this embodiment, the gear transmission structure is composed of multiple gears coupled in sequence, and each gear is coaxially connected to the sun gear 132. Thus, during the rotation of one sun gear 132, the sun gears 132 of the other planetary gear units 13 can be driven, achieving the corresponding synchronous operation effect.

[0042] Combination Figure 1 and Figure 8 As shown, according to one embodiment of the present invention, the annular mass block 2 is composed of multiple equally divided mass block parts; specifically, the annular mass block 2 can be set to two mass block parts. Of course, the number of mass block parts can also be adjusted according to the overall size of the annular bending and torsion frequency converter vibration absorber, for example, 3, 4, etc., which can be set according to specific actual needs.

[0043] Furthermore, the inner ring 11 is composed of multiple equally divided inner ring parts; specifically, the inner ring 11 can be set to two inner ring parts. Of course, the number of inner ring parts can also be adjusted according to the overall size of the annular bending and twisting frequency converter vibration absorber, for example, 3, 4, etc., which can be set according to specific actual needs.

[0044] Furthermore, the outer ring 12 is composed of multiple equally divided outer ring parts; specifically, the outer ring 12 can be set to two outer ring parts. Of course, the number of outer ring parts can also be adjusted according to the overall size of the annular bending and twisting frequency converter vibration absorber, for example, 3, 4, etc., which can be set according to specific actual needs.

[0045] In this embodiment, the number of mass block portions, inner ring portions, and outer ring portions is the same. Therefore, multiple vibration absorber portions for splicing the annular bending-torsional frequency converter can be formed based on the connecting action of the planetary gear units 13, facilitating its assembly and disassembly with the pipeline shaft system. In this embodiment, the inner ring portion, outer ring portion, and the arranged gear ring 131 can be integrally formed using methods such as wire cutting or 3D printing. The materials used can be metal, rubber, resin, etc., and can be determined according to the usage environment and load.

[0046] like Figure 9 As shown, according to one embodiment of the present invention, the annular bending-torsional frequency converter based on planetary gears further includes: a clamp 3; wherein the clamp 3 is disposed on the outer side of the annular mass block 2, for simultaneously fastening multiple mass block parts, multiple inner ring parts, and multiple outer ring parts; to achieve fixed installation with the pipeline shaft system structure; wherein, at least one clamp 3 can be disposed on the outer side of the annular bending-torsional frequency converter for fastening, and its radial clamping force can achieve a tight fit with the pipeline shaft system structure. In this embodiment, the clamp 3 can be an open-type stainless steel annular clamp, with its locking bolt located on the outer side. By tightening the locking bolt, the clamp generates a uniform radial clamping force, which tightly fixes the two semi-circular ring components to the pipeline or shaft system and ensures sufficient contact pressure to achieve effective vibration transmission.

[0047] In this embodiment, the end of the mass block portion is provided with a first docking structure for docking and positioning. The first docking structure is a protrusion and groove structure with a matching shape. For the same mass block portion, the first docking structure at both ends adopts the distribution of protrusion and groove structures to enable the two mass block portions to be positioned and installed in a mutually cooperating manner at the ends, so as to make the accuracy and reliability of this solution higher during the installation process.

[0048] In this embodiment, the end of the inner ring portion is provided with a second docking structure for docking and positioning; wherein, the second docking structure is a protruding groove structure with a matching shape. For the same inner ring portion, the second docking structures at both ends adopt the distribution of protruding structures and groove structures to enable the two inner ring portions to be positioned and installed in a mutually cooperating manner at the ends, so as to make the accuracy and reliability of this solution higher during the installation process.

[0049] In this embodiment, the end of the outer ring portion is provided with a third docking structure for docking and positioning; wherein, the third docking structure is a protruding groove structure with a matching shape. For the same inner ring portion, the distribution of the third docking structures at both ends of the inner ring portion enables the two outer ring portions to be positioned and installed in a mutually cooperating manner at the ends, so as to make the accuracy and reliability of this solution higher during the installation process.

[0050] According to one embodiment of the present invention, a design method for the aforementioned planetary gear-based annular bending-torsional frequency converter vibration absorber includes the following steps: S1. Obtain the outer diameter and vibration frequency of the pipeline shaft system structure; S2. Based on the outer diameter of the pipeline shaft system structure, the inner diameter of the inner ring 11 is determined, as well as the absorption frequency range and adjustment factor of the annular bending torsion frequency absorber are determined. S3. Based on the obtained absorption frequency range and adjustment factor, the gear ring structure parameters of the gear ring 131 are designed, and the materials of each structure in the variable stiffness elastic device 1 are selected. In this embodiment, the absorption frequency range and adjustment factor of the annular bending-torsional frequency converter can be adjusted by changing the gear ring structure parameters of the gear ring 131 in the planetary gear unit 13. The gear ring structure parameters include the radius of the gear ring 131 and the radial thickness of the gear ring 131. Specifically, the larger the radius of the gear ring 131 and the thinner the radial thickness, the wider the absorption frequency range and the larger the adjustment factor of the annular bending-torsional frequency converter in this solution. In particular, increasing the radius of the gear ring 131 and decreasing its radial thickness can shift the lowest resonant frequency of the vibration absorber to a lower frequency, while keeping the highest resonant frequency essentially unchanged. Furthermore, by changing the material of at least one structure in the variable stiffness elastic device 1, the absorption frequency range and adjustment factor of the annular bending-torsional frequency-converting vibration absorber can be adjusted. Specifically, using high-stiffness materials to manufacture the sun gear and planetary gears can shift the highest resonant frequency of the annular bending-torsional frequency-converting vibration absorber to a higher frequency. Of course, other materials in the variable stiffness elastic device 1 can also be adjusted, the specifics of which can be determined according to the operating environment and load.

[0051] S3. Based on the obtained gear ring structure parameters, the dimensions and meshing transmission parameters of the sun gear 132 and planet gear 133 are designed to complete the construction of the planet gear unit 13; in this embodiment, the meshing transmission parameters include: module and number of teeth.

[0052] S4. Obtain the number and arrangement of planetary gear units 13, and determine the outer diameter of the inner ring 11, the inner and outer diameters of the outer ring 12, and the inner and outer diameters of the annular mass block 2 based on the obtained outer dimensions of the planetary gear units 13, thus completing the construction of the annular bending-torsional frequency converter vibration absorber.

[0053] To further illustrate the vibration reduction effect of the annular bending-torsion frequency converter vibration absorber of the present invention, the following description is provided in conjunction with specific embodiments.

[0054] The parameters of the annular torsional frequency converter vibration absorber are as follows: In a single planetary gear unit 13, the outer radius of the gear ring 131 is 13.1 mm, the inner radius is 12.5 mm, the gear module is 0.5, and the number of teeth is 48; the sun gear 132 has 24 teeth; and the planetary gear 133 has 12 teeth. The outer radius of the inner ring 11 is 18 mm, and the inner radius is 23 mm. The outer radius of the outer ring 12 is 53 mm, and the inner radius is 57 mm. The inner ring 11, outer ring 12, and planetary gear unit 13 are made of resin. The outer radius of the annular mass block 2 is 70 mm, the inner radius is 57 mm, and the material is stainless steel. The overall axial length of the annular torsional frequency converter vibration absorber is 20 mm. See the physical diagram for details. Figure 10 .

[0055] The radial resonant frequency of the annular bending-torsional frequency converter was experimentally tested. The test protocol is described in [reference needed]. Figure 11 (a) Radial excitation was applied to the annular bending-torsional frequency converter, and the frequency response of the annular bending-torsional frequency converter at different rotation angles of the planetary gear 133 was obtained. The experimental results are shown in [reference]. Figure 11 (b). The radial response is... ,in, Indicates radial response acceleration, Indicates the radial response amplitude. It represents angular frequency.

[0056] Experimental results show that the radial first-order resonant frequency of the annular bending-torsional frequency absorber ( f = ( / 2π) can be adjusted from 90Hz to 300Hz.

[0057] The torsional resonance frequency of the annular bending-torsional frequency converter was experimentally tested. The test protocol is described in [reference needed]. Figure 12(a) To more easily excite the torsional vibration of the annular bending-torsional frequency converter, an aluminum alloy arm was added to the annular mass block 2 of the annular bending-torsional frequency converter. Tangential excitation was applied to the absorber, and the torsional frequency response of the aluminum alloy arm under different rotation angles of the planetary gear 133 was obtained. The experimental results are shown in [reference]. Figure 12 (b). The torsional response is... ,in, Indicates torsional response acceleration, Indicates the amplitude of the torsional response. It represents angular frequency.

[0058] Experimental results show that the torsional first-order resonant frequency of the annular bending-torsional frequency absorber can be adjusted from 25Hz to 70Hz.

[0059] See Figure 3 The annular torsional frequency absorber can be periodically installed on pipelines or shaft systems to form metamaterial pipelines or shaft systems, further enhancing the suppression effect on radial and axial torsional vibrations of pipelines or shaft systems. The radial and torsional frequency responses of the metamaterial pipeline or shaft system were calculated using the finite element method. The metamaterial pipeline or shaft system comprises 10 periodic cells (i.e., a combination of the unit length of the pipeline or shaft system and the annular torsional frequency absorber), with a cell length of 0.2m (i.e., a unit length of 0.2m for the pipeline or shaft system). The pipeline or shaft system and the annular mass block 2 are made of aluminum alloy, while the inner ring 11, outer ring 12, and planetary gear unit 13 are made of resin. The frequency response results of the metamaterial structure at different rotation angles of the planetary gear 133, obtained based on finite element calculations, are shown in [reference missing]. Figure 13 (a) and Figure 13 (b) According to the finite element simulation results, the radial frequency response of metamaterial pipelines or metamaterial shaft systems can generate a bandgap, and the frequency range of the bandgap can be adjusted from 164Hz-205Hz to over 443Hz-500Hz. The torsional frequency response can also generate a bandgap, and the frequency range of the bandgap can be adjusted from 68Hz-82Hz to 164Hz-209Hz.

[0060] The experimental and simulation results above show that the annular bending-torsional frequency-converting vibration absorber proposed in this scheme can achieve a wide range of adjustable vibration absorption frequency and has comprehensive vibration reduction performance that can absorb both radial and torsional vibrations simultaneously.

[0061] The above description is merely an example of a specific solution of the present invention. For any devices and structures not described in detail herein, it should be understood that they are implemented using common devices and methods already available in the art.

[0062] The above description is merely one embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the invention by those skilled in the art. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

Claims

1. A ring-shaped torsional frequency converter vibration absorber based on planetary gears, characterized in that, include: A variable stiffness elastic device (1) and an annular mass block (2) connected to the outside of the variable stiffness elastic device (1). The variable stiffness elastic device (1) includes: an inner ring (11), an outer ring (12), and a plurality of planetary gear units (13) arranged between the inner ring (11) and the outer ring (12). The planetary gear unit (13) includes: a gear ring (131), a sun gear (132), and a plurality of planetary gears (133). Two protruding bosses (131a) for connecting the inner ring (11) and the outer ring (12) are provided on the outer side of the toothed ring (131) at relative positions. The position where the protruding boss (131a) of the gear ring (131) is connected to the inner ring (11) is the first connection position, and the position where it is connected to the outer ring (12) is the second connection position. The first connection position and the second connection position are in the same radial direction of the outer ring (12), or the first connection position and the second connection position are in two different radial directions of the outer ring (12).

2. The annular bending-torsional frequency converter based on planetary gears according to claim 1, characterized in that, The annular bending-torsional frequency-converting vibration absorber is based on an inner ring (11) sleeved on the pipeline shaft structure to suppress radial and / or torsional vibrations of the pipeline shaft structure.

3. The annular bending-torsional frequency converter based on planetary gears according to claim 1 or 2, characterized in that, The absorption frequency range and adjustment factor of the annular bending-torsional frequency absorber can be adjusted by changing the material of at least one structure in the variable stiffness elastic device (1); and / or, the absorption frequency range and adjustment factor of the annular bending-torsional frequency absorber can be adjusted by changing the gear ring structure parameters of the gear ring (131) in the planetary gear unit (13); wherein the gear ring structure parameters include: the radius of the gear ring (131) and the radial thickness of the gear ring (131).

4. The annular bending-torsional frequency converter based on planetary gears according to claim 1 or 2, characterized in that, In the variable stiffness elastic device (1), two adjacent planetary gear units (13) are arranged in a mirror symmetrical manner; or, in the variable stiffness elastic device (1), the included angle between the two radial directions of the first connection position and the second connection position of all planetary gear units (13) is consistent, and the first connection position and the second connection position are periodically distributed along the clockwise / counterclockwise direction.

5. The annular bending-torsional frequency converter based on planetary gears according to claim 1 or 2, characterized in that, The inner ring (11) is connected to the outer protrusion (131a) at the position where a first hollow structure (11a) is provided that penetrates the body of the inner ring (11) along the axial direction of the inner ring (11). The outer ring (12) is provided with a second hollow structure (12a) that runs through the body of the outer ring (12) along the axial direction of the outer ring (12) at the position where the outer ring (12) connects with the outer protrusion (131a).

6. The annular bending-torsional frequency converter based on planetary gears according to claim 1 or 2, characterized in that, In the planetary gear unit (13), a driver may be optionally employed to drive the sun gear (132) and a plurality of planetary gears (133) to rotate within the gear ring (131).

7. The annular bending-torsional frequency converter based on planetary gears according to claim 6, characterized in that, The driver is configured to correspond one-to-one with the planetary gear unit (13), or multiple planetary gear units (13) are connected to the same driver based on the transmission structure.

8. The annular bending-torsional frequency converter based on planetary gears according to claim 1 or 2, characterized in that, The annular mass block (2) is composed of multiple equally divided mass block parts; The inner ring (11) is composed of multiple equally divided inner ring parts; The outer ring (12) is composed of multiple equally divided outer ring parts; The number of the mass block portion, the inner ring portion, and the outer ring portion is the same.

9. The annular bending-torsional frequency converter based on planetary gears according to claim 8, characterized in that, Also includes: Clamp (3); The clamp (3) is set on the outside of the annular mass block (2) for simultaneously fastening multiple mass block parts, multiple inner ring parts and multiple outer ring parts; The end of the mass block portion is provided with a first docking structure for docking and positioning; The end of the inner ring portion is provided with a second docking structure for docking and positioning; The outer ring portion is provided with a third docking structure for docking and positioning at its end; There are four planetary gears (133), and the four planetary gears (133) are arranged at equal intervals along the circumference of the sun gear (132).

10. A design method for the annular bending-torsional frequency converter based on planetary gears as described in any one of claims 1 to 9, characterized in that, Includes the following steps: S1. Obtain the outer diameter and vibration frequency of the pipeline shaft system structure; S2. Based on the outer diameter of the pipeline shaft system structure, the inner diameter of the inner ring (11) is determined, and the absorption frequency range and adjustment multiple of the annular bending torsion frequency absorber are determined; S3. Based on the obtained vibration absorption frequency range and adjustment factor, the gear ring structure parameters of the gear ring (131) are designed, and the materials of each structure in the variable stiffness elastic device (1) are selected; S3. Based on the obtained gear ring structure parameters, the dimensions and meshing transmission parameters of the sun gear (132) and planet gear (133) are designed to complete the construction of the planet gear unit (13); S4. Obtain the number and arrangement of planetary gear units (13), and determine the outer diameter of the inner ring (11), the inner and outer diameters of the outer ring (12), and the inner and outer diameters of the annular mass block (2) based on the obtained planetary gear unit (13) dimensions, and complete the construction of the annular bending and torsion frequency converter vibration absorber.

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