Double-ring shock absorber based on variable rigidity, shock absorption platform system and cantilever beam structure system
By adjusting the stiffness through structural rotation using a dual-ring vibration damper, the problem of passive adaptive stiffness adjustment in mid-to-high frequency vibration environments is solved, improving frequency domain adaptability and vibration reduction effect while reducing costs.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- SUZHOU DINGLING TECH CO LTD
- Filing Date
- 2025-06-09
- Publication Date
- 2026-05-08
AI Technical Summary
Existing technologies cannot achieve effective and continuous stiffness adjustment and vibration suppression in the mid-to-high frequency range without the need for external energy and control systems.
A variable stiffness double-ring vibration damper is adopted, which changes the contact stiffness by the relative rotation of the upper and lower ring structures, and achieves stiffness adjustment by utilizing the geometric changes of the structure itself.
It achieves continuous stiffness adjustment within the range of 0° to 90°, adapts to vibration environments in different frequency bands, avoids resonance, expands the frequency domain adaptability of vibration reduction, reduces manufacturing costs, and is suitable for multimodal vibration environments.
Smart Images
Figure CN224214628U_ABST
Abstract
Description
Technical Field
[0001] This relates to the fields of vibration control and structural dynamics, and in particular to a dual-ring passive vibration damping device with adjustable stiffness based on structural geometric characteristics. Background Technology
[0002] Vibration control technology is of great importance in modern industrial equipment, precision platforms, and electronic instruments. Prolonged exposure to vibration environments not only reduces equipment lifespan and measurement accuracy but can also lead to structural fatigue failure. Therefore, vibration suppression methods are constantly evolving, mainly including three categories: passive vibration reduction, active vibration reduction, and semi-active vibration reduction.
[0003] Passive vibration dampers are widely used in engineering applications due to their simple structure, good stability, and low cost. Examples include rubber pads, spring-damping systems, and vibration isolation seats. These types of vibration dampers rely on fixed structural parameters to achieve vibration attenuation in a specific frequency band. However, once their stiffness is determined, it cannot be dynamically adjusted. When faced with multi-frequency or changing operating conditions, resonance is likely to occur, making it impossible to maintain good performance.
[0004] In contrast, active vibration dampers collect vibration signals through sensors and adjust the actuator force input in real time via a control system to achieve dynamic vibration suppression. For example, in high-precision platforms and aerospace structures, active magnetic levitation vibration isolation devices can achieve excellent low-frequency vibration control. However, active systems typically suffer from drawbacks such as complex structure, high power consumption, high cost, and poor system robustness.
[0005] In recent years, semi-active vibration damping technology has emerged, combining the advantages of both passive and active systems to some extent by adjusting the stiffness or damping parameters inside the device. Examples include magnetorheological dampers and piezoelectric tuned mass dampers, which can achieve parameter adjustments within a limited range to cope with changes in external excitation. However, these systems still generally rely on electronic control loops or complex feedback logic, resulting in relatively high manufacturing costs and control difficulties.
[0006] In the pursuit of vibration reduction devices that require no external energy, are low-cost, and adaptive, some research has begun to focus on performance adjustment mechanisms resulting from changes in the structure's own morphology. For example, passive adjustability of stiffness or damping can be achieved by designing deformable units or composite structures. However, existing structures are mostly concentrated in low-frequency buffering scenarios, and there are still few passive stiffness adjustment mechanisms that work effectively in the mid-to-high frequency range (40Hz~100Hz). Moreover, the adjustment range is limited and the response capability is weak, making it difficult to meet the vibration reduction requirements in practical engineering.
[0007] In summary, existing technologies have the drawback of being unable to achieve effective and continuous stiffness adjustment and vibration suppression in the mid-to-high frequency range by utilizing structural geometric changes without the need for external energy and control systems. Utility Model Content
[0008] To address the shortcomings of existing technologies that cannot achieve effective and continuous stiffness adjustment and vibration suppression in the mid-to-high frequency range through structural geometric changes without the need for external energy and control systems, the technical solution provided by this utility model is as follows:
[0009] A dual-ring vibration damper based on variable stiffness, comprising:
[0010] An upper ring structure and a lower ring structure are arranged opposite to each other and are rotatably connected by a connecting member;
[0011] Both the upper and lower annular structures include two parallel crossbeams and two semi-elliptical plates symmetrically arranged at both ends of the crossbeams, forming a closed structure.
[0012] The upper annular structure and the lower annular structure have aligned screw holes at their center. The connecting member passes through the screw holes to enable the upper annular structure to rotate relative to the lower annular structure within a preset angle range.
[0013] The contact stiffness between the upper annular structure and the lower annular structure changes with their relative rotation angle.
[0014] Furthermore, a preferred embodiment is provided in which the upper annular structure and the lower annular structure have the same structure.
[0015] Furthermore, a preferred embodiment is provided in which the crossbeam is a rectangular plate structure.
[0016] Furthermore, in a preferred embodiment, the relative rotation angle between the upper annular structure and the lower annular structure ranges from 0° to 90°.
[0017] Furthermore, a preferred embodiment is provided in which the major axis of the two semi-elliptical plates is 20 mm and the minor axis is 15 mm.
[0018] Furthermore, a preferred embodiment is provided in which the crossbeam and the semi-elliptical sheet are an integral structure manufactured by 3D printing.
[0019] Furthermore, a preferred embodiment is provided in which the 3D printing process uses PLA material and the printing infill rate is 15%.
[0020] Furthermore, a preferred embodiment is provided in which the connecting member is a metal bolt of specification M5.
[0021] A vibration damping platform system is also provided, including a load-bearing platform, a support base, and the aforementioned vibration damper disposed therebetween.
[0022] A cantilever beam structure system is also provided, including a cantilever beam and the aforementioned damper mounted below its free end.
[0023] Compared with the prior art, the advantages of the technical solution provided by the present invention are as follows:
[0024] This solution employs two sets of relatively rotatable double-ring structures to achieve passively adjustable structural stiffness. Specifically, when the relative rotation angle of the upper and lower ring structures changes, the overlap area between their semi-elliptical sheet structures changes, resulting in a continuous change in the overall contact stiffness of the system. This method of adjusting stiffness based on the degree of structural overlap can achieve continuous stiffness adjustment within the range of 0° to 90° without relying on external energy or control systems, adapting to vibration environments in different frequency bands. Compared to the shortcomings of traditional passive rubber pads with fixed stiffness, this method improves the frequency domain adaptability of the vibration damping device and avoids the risk of resonance.
[0025] By adjusting the thickness and width of the crossbeams in the double-ring structure, the overall stiffness and frequency response characteristics of the structure can be further precisely controlled. Experimental results show that as the crossbeam thickness increases from 2mm to 6mm, the vibration reduction bandwidth expands from 36Hz to 100Hz, demonstrating flexible adaptability to different target frequency bands. Compared with conventional non-adjustable structures, this scheme still exhibits significant regularity and controllability under changes in structural parameters, improving the design's fault tolerance and adjustable range.
[0026] This solution utilizes a parallel dual-unit structure to effectively expand the system's vibration reduction frequency bandwidth. After installing two dual-ring vibration isolators in parallel, their stiffness is twice that of a single device. Simulation and experimental data both show that the transmissivity decay curve extends towards lower frequencies, covering a vibration reduction range from 35Hz to 100Hz. Compared to most existing structures that are only effective in a single frequency band, this method achieves frequency domain performance expansion through simple physical superposition, requiring no additional control algorithms or sensor feedback, making it more suitable for multimodal vibration environments in industrial settings.
[0027] This solution utilizes 3D-printed PLA material combined with low infill ratio manufacturing, significantly reducing device manufacturing costs. Furthermore, by coupling and adjusting material stiffness and geometric parameters, it achieves synergistic optimization of elastic modulus and contact characteristics. Compared to traditional metal vibration damping structures that rely on high-precision machining, this device offers advantages such as simple manufacturing processes, fast design response, and rapid iterative upgrades, making it suitable for both mass production and customized design scenarios.
[0028] The aforementioned structural device was applied to mid-to-high frequency vibration experiments at the free end of a cantilever beam. Results showed that the maximum transmissibility attenuation reached over 20 dB within the 40 Hz to 100 Hz range. The attenuation performance was most significant when the structure was adjusted to a 60° angle, verifying the superior vibration reduction capability of the device under passive, adaptive conditions. Compared to traditional passive vibration dampers that only function near a fixed frequency, this structure achieves a significant correlation between the adjustment angle and vibration performance, improving dynamic response efficiency in practical applications.
[0029] It is suitable for working scenarios such as precision platforms, cantilever structures, or electronic equipment mounting bases that require passive, adaptive vibration reduction in mid-to-high frequency vibration environments ranging from 40Hz to 100Hz. Attached Figure Description
[0030] Figure 1 This is a schematic diagram of the double-ring structure at multiple angles from 0° to 90°.
[0031] Figure 2 This is a structural dimension diagram of a single ring structure;
[0032] Figure 3 Force-displacement curves at different rotation angles;
[0033] Figure 4 A comparison chart of experimental and theoretical stiffness;
[0034] Figure 5 The curves show the comparison between the simulated and experimental transfer rates;
[0035] Figure 6 A comparison curve of the transmission rate with and without shock absorbers;
[0036] Figure 7 This represents the change in transmissivity at different rotation angles.
[0037] Where 1 represents a crossbeam and 2 represents a semi-elliptical sheet. Detailed Implementation
[0038] To make the advantages and benefits of the technical solution provided by the present invention clearer, the technical solution provided by the present invention will now be described in further detail with reference to the accompanying drawings, specifically:
[0039] Implementation Method 1: This implementation method provides a dual-ring vibration damper based on variable stiffness, comprising:
[0040] An upper ring structure and a lower ring structure are arranged opposite to each other and are rotatably connected by a connecting member;
[0041] Both the upper and lower annular structures include two parallel crossbeams and two semi-elliptical plates symmetrically arranged at both ends of the crossbeams, forming a closed structure.
[0042] The upper annular structure and the lower annular structure have aligned screw holes at their center. The connecting member passes through the screw holes to enable the upper annular structure to rotate relative to the lower annular structure within a preset angle range.
[0043] The contact stiffness between the upper annular structure and the lower annular structure changes with their relative rotation angle.
[0044] The upper and lower ring structures have the same structure.
[0045] The crossbeam is a rectangular plate structure.
[0046] The relative rotation angle between the upper annular structure and the lower annular structure ranges from 0° to 90°.
[0047] The major axis of the two semi-elliptical plates is 20 mm, and the minor axis is 15 mm.
[0048] The crossbeam and the semi-elliptical sheet are an integral structure, manufactured using 3D printing technology.
[0049] The 3D printing process uses PLA material with a printing infill rate of 15%.
[0050] The connecting component is a metal bolt, with a specification of M5.
[0051] Implementation Method Two: This implementation method provides a further detailed description of the technical solution provided in Implementation Method One. Specifically:
[0052] like Figure 1 As shown, a variable stiffness double-ring vibration damper is described. The device consists of two sets of identical ring components, namely an upper ring structure 1 and a lower ring structure 2. The two ring structures are assembled by a central connecting bolt to form an integrated adjustable structural unit with adjustable stiffness.
[0053] Each annular structure consists of a central crossbeam and two symmetrical semi-elliptical plates 2. The central crossbeam has a rectangular cross-section, preferably 90 mm in length, 20 mm in width, and 6 mm in thickness, and is used to support the overall structure and transfer external loads. The two ends of the crossbeam are connected to the two semi-elliptical plates 2 through transition sections. The two semi-elliptical plates 2 are arranged symmetrically, with their major axes parallel to the crossbeam, a major axis length of 20 mm, and a minor axis length of 15 mm, forming an approximately closed elliptical boundary.
[0054] The upper and lower annular structures are aligned and connected via bolt holes located at the center, preferably using M5 metal bolts and nuts for fastening. This ensures stable assembly while allowing the upper structure to rotate relative to the lower structure within a range of 0° to 90° around its central axis. Changes in the rotation angle directly alter the contact overlap area of the semi-elliptical plates in the two annular structures, thereby changing the overall contact stiffness.
[0055] In the initial state (i.e., the upper and lower ring structures are completely overlapped, and the rotation angle is 0°), the two semi-elliptical plates in region 2 are completely overlapped, resulting in maximum structural stiffness. The overall system stiffness measurement is approximately 1.2 kN / mm. In this state, the device can be used in high-stiffness support applications, effectively transferring loads and suitable for resisting low-amplitude, high-frequency vibrations.
[0056] When users need to reduce system stiffness to lower the resonance response, the upper annular structure can be manually rotated slowly to form a certain angle relative to the lower annular structure. Typical angles include 30°, 60°, and 90°. As the rotation angle increases, the actual overlap area between the two semi-elliptical plates decreases, leading to a reduction in contact stiffness. Experimental results show that when the angle reaches 90°, the structural stiffness can be reduced to approximately 0.5 kN / mm, achieving a stiffness adjustment range of approximately 2.4 times.
[0057] Furthermore, to enhance the device's adaptability to vibrations at different frequency bands in practical engineering applications, the thickness and width parameters of the crossbeam can be adjusted by optimizing them. For example, increasing the crossbeam thickness from 2 mm to 6 mm significantly raises the device's natural frequency and expands the vibration reduction bandwidth to approximately 100 Hz. Simultaneously, increasing the crossbeam width from 10 mm to 30 mm accelerates the structural response speed and advances the vibration reduction start frequency, making it more suitable for environments with rapidly changing frequency interference signals.
[0058] In terms of structural combination, this invention also supports the parallel use of multiple vibration damper units. In the experiment, when two identical double-ring vibration dampers were connected in parallel to the free end of the cantilever beam via a connecting plate, the overall system stiffness was approximately twice that of a single structure. Meanwhile, simulation and experimental data showed that the transmissibility attenuation of this combined structure was significantly improved in the 35Hz to 100Hz range, with a maximum vibration reduction amplitude of over 20 dB, effectively expanding the vibration reduction bandwidth.
[0059] The device is integrally formed using PLA material through 3D printing, with a printing infill rate set at 15% to ensure a balance between elasticity and sufficient rigidity. This forming method not only reduces manufacturing costs but also facilitates rapid iteration and mass production. The overall device is compact and lightweight, making it easy to install on experimental platforms, precision equipment bases, or under structurally sensitive components.
[0060] In practical applications, the device is fixedly connected to the target structure with bolts, and an appropriate rotation angle is set to match the operating frequency range of the target structure, thereby achieving passive, passive structural vibration isolation and energy dissipation. It achieves vibration control in the mid-to-high frequency range (approximately 40~100Hz) without requiring a power supply, signal input, or controller, making it suitable for precision measuring equipment, electronic bases, optical platforms, and other applications.
[0061] In summary, this device achieves passive adjustment of structural stiffness by changing the overlapping area caused by structural rotation. It has advantages such as simple structure, low manufacturing cost, wide adjustable range, wide adaptability frequency band, and no need for external energy input. It is an innovative passive vibration reduction structural solution that combines engineering practicality and economy.
[0062] Implementation Method 3: Combination Figure 1-7 This embodiment describes the technical solution provided above in further detail through specific examples. Specifically:
[0063] The purpose of this invention is to provide a double-ring vibration damper with adjustable stiffness through changes in its own geometric characteristics. It has the advantages of not requiring external energy, having a compact structure, and adjustable parameters, and can effectively suppress structural vibrations in the mid-to-high frequency range.
[0064] To achieve the above objectives, this utility model provides the following technical solution:
[0065] The vibration damper comprises two annular structures stacked one on top of the other and fixed together by bolts and nuts. Each annular structure includes a central crossbeam 1 and two symmetrically arranged semi-elliptical plates 2. By rotating the position of the upper annular structure relative to the lower annular structure, the contact area between the two can be changed, thereby adjusting the overall stiffness of the system.
[0066] Specifically, the dimensions of beam 1 are 90 mm × 20 mm × 6 mm, and the major axis of the semi-elliptical plate 2 is 20 mm, and the minor axis is 15 mm. The structural material is PLA, and considering a 15% printing infill rate, the corrected elastic modulus is approximately 0.375 GPa. After the two annular components are stacked, their rotation angle adjustment range is 0° to 90°. Experiments show that the stiffness can decrease from 1.2 km / mm to 0.5 km / mm within this rotation angle range, an adjustment range of 2.4 times.
[0067] This invention can further expand the stiffness configuration by connecting multiple vibration dampers in series or in parallel. For example, by connecting two double-ring vibration dampers in parallel, the overall stiffness is doubled, and the transmission rate decrease range is extended to low frequencies, which can meet the needs of medium and low frequency vibration control in the range of 30 Hz to 100 Hz.
[0068] The beneficial effects are as follows: the structural design is simple and the manufacturing cost is low, making it suitable for 3D printing integrated molding; the stiffness adjustment is passive, adapting to various variable working conditions; experiments show that the device can effectively suppress vibration in the 40 Hz~100 Hz frequency band, with the transmission rate decreasing by more than 20 dB; it can be expanded into a multi-layer stacked type to adapt to application requirements with different load masses, thicknesses, and widths.
[0069] Example 1: See Figure 1 , Figure 3 and Figure 4 Two ring structures are stacked on top of each other and connected by M5 bolts and nuts, with the rotation angle manually adjustable. At 0°, the two semi-elliptical plates 2 are maximally overlapped, resulting in maximum system stiffness. By gradually rotating to 90°, the contact area decreases, and the stiffness drops to approximately 40% of its original value. The stiffness-displacement curve is shown below. Figure 3 As shown, the comparison between experimental and theoretical values is shown in the figure. Figure 4 The maximum error is controlled within 5%.
[0070] Example 2: See Figures 5 to 7 A double-ring vibration damper was installed at the free end of an aluminum alloy cantilever beam with dimensions of 300×30×4 mm³, and a 250 g mass block was added. A 0.1 m / s² sweep frequency excitation was applied through an exciter. The simulation was performed using COMSOL software for frequency domain analysis, with the boundary set as a fixed support at the beam root. Figure 5 The simulation and experimental results were compared to verify the reliability of the model. Figure 6 The transmission rate curves of DRI dampers without and with DRI dampers were compared, showing a significant attenuation after installation in the 40 Hz to 100 Hz range. Figure 7 The changes in transmissivity under different rotation angles are further demonstrated, illustrating that angle adjustment has controllable vibration reduction capabilities in practical applications.
[0071] Example 3: Considering the impact of changes in multiple structural parameters on vibration reduction performance, including thickness, width, and number. When the structural thickness increases from 2 mm to 6 mm, the vibration reduction bandwidth expands from 36 Hz to 100 Hz; when the width increases from 10 mm to 30 mm, the effective vibration reduction starting frequency is advanced, and the vibration reduction response is faster; when the number of rings increases from 1 set to 2 sets in parallel, the vibration reduction range expands to 35 Hz~100 Hz, and the system adaptability is enhanced.
[0072] These experimental results demonstrate that the vibration damper has strong tolerance to changes in structural parameters and is suitable for various environmental requirements.
[0073] The above description of several specific embodiments further details the technical solution provided by the present invention in order to highlight the advantages and benefits of the technical solution provided by the present invention. However, the above-described specific embodiments are not intended to limit the present invention. Any reasonable modifications and improvements to the present invention, combinations of embodiments, and equivalent substitutions based on the spirit and principles of the present invention should be included within the protection scope of the present invention.
Claims
1. A dual-ring vibration damper based on variable stiffness, characterized in that, include: An upper ring structure and a lower ring structure are arranged opposite to each other and are rotatably connected by a connecting member; Both the upper and lower annular structures include two parallel crossbeams and two semi-elliptical plates symmetrically arranged at both ends of the crossbeams, forming a closed structure. The upper annular structure and the lower annular structure have aligned screw holes at their crossbeam centers. The connecting member passes through the screw holes to enable the upper annular structure to rotate relative to the lower annular structure within a preset angle range. The contact stiffness between the upper annular structure and the lower annular structure changes with their relative rotation angle.
2. The dual-ring vibration damper based on variable stiffness according to claim 1, characterized in that, The upper and lower ring structures have the same structure.
3. A double-ring vibration damper based on variable stiffness according to claim 1, characterized in that, The crossbeam is a rectangular plate structure.
4. A double-ring vibration damper based on variable stiffness according to claim 1, characterized in that, The relative rotation angle between the upper annular structure and the lower annular structure ranges from 0° to 90°.
5. A double-ring vibration damper based on variable stiffness according to claim 1, characterized in that, The major axis of the two semi-elliptical plates is 20 mm, and the minor axis is 15 mm.
6. A double-ring vibration damper based on variable stiffness according to claim 1, characterized in that, The crossbeam and the semi-elliptical sheet are an integral structure, manufactured using 3D printing technology.
7. A double-ring vibration damper based on variable stiffness according to claim 6, characterized in that, The 3D printing process uses PLA material with a printing infill rate of 15%.
8. A double-ring vibration damper based on variable stiffness according to claim 7, characterized in that, The connecting component is a metal bolt, with a specification of M5.
9. A vibration damping platform system, characterized in that, It includes a load-bearing platform, a support base, and a vibration damper as described in claim 1 disposed therebetween.
10. A cantilever beam structure system, characterized in that, It includes a cantilever beam and a damper as described in claim 1, mounted below its free end.