A quasi-zero stiffness vibration isolator and vibration isolation system based on inerter and linkage coupling
By using a quasi-zero stiffness vibration isolator coupled with inertial capacitance and linkage, and by utilizing the amplified equivalent mass and frictional dissipation of the inertial capacitance, the problems of complex structure and unstable vibration isolation effect of existing vibration isolators are solved. This achieves wideband low-frequency vibration isolation and dynamic stability, and is suitable for scenarios such as marine equipment and flexible foundations.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Utility models(China)
- Current Assignee / Owner
- HUAZHONG UNIV OF SCI & TECH
- Filing Date
- 2025-07-09
- Publication Date
- 2026-07-07
AI Technical Summary
Existing quasi-zero stiffness vibration isolators have complex structures and unstable vibration isolation effects in practical applications, making it difficult to balance load-bearing capacity, vibration isolation bandwidth, and system dynamic stability.
A quasi-zero stiffness vibration isolator using inertial capacitance and linkage coupling is achieved by combining an X-shaped geometric nonlinear linkage structure, connecting springs, and an inertial container. The inertial container amplifies the equivalent mass, and energy dissipation is achieved by combining the Jenkins friction model. The ratio of inertial capacitance to the vibration isolation target mass is adjusted to achieve quasi-zero stiffness characteristics.
It significantly broadens the low-frequency vibration isolation bandwidth, improves the dynamic stability of the system, adapts to the vibration isolation performance optimization under different excitation conditions, reduces the resonance frequency, and improves the reliability and vibration isolation effect of the vibration isolator.
Smart Images
Figure CN224469568U_ABST
Abstract
Description
Technical Field
[0001] This utility model belongs to the field of vibration isolator technology, and more specifically, relates to a quasi-zero stiffness vibration isolator and vibration isolation system based on inertial capacitance and linkage coupling. Background Technology
[0002] With the increasing demand for low-frequency vibration control in fields such as shipbuilding, aerospace, and high-end equipment, quasi-zero stiffness (QZS) vibration isolation technology has become one of the important development directions for achieving efficient low-frequency vibration isolation. Traditional linear vibration isolators have good vibration isolation performance in the high-frequency range, but in the low-frequency range, they often suffer from problems such as limited natural frequency, narrow isolation bandwidth, and difficulty in balancing load capacity and vibration isolation effect. Therefore, researchers have gradually introduced geometrically nonlinear structures or negative stiffness elements, and through the design of specific mechanical mechanisms, enabled the vibration isolator to exhibit near-zero dynamic stiffness in a small amplitude range, thereby significantly expanding the effective isolation bandwidth while maintaining a high static load-bearing capacity.
[0003] Existing QZS vibration isolators typically use a combination of vertical springs and inclined or transverse springs to achieve a balance between negative and positive stiffness. For example, the QZS vibration isolator proposed by Carrella et al., which consists of a vertical spring and multiple inclined springs, has verified the effectiveness of geometric nonlinearity in low-frequency vibration isolation.
[0004] However, such designs often struggle to maintain stable quasi-zero stiffness characteristics over a wide range of excitation frequencies and are highly sensitive to external disturbances. When load-bearing capacity, vibration isolation bandwidth, and system dynamic stability need to be considered simultaneously, existing QZS structures often require the introduction of multiple sets of springs or complex multi-degree-of-freedom structures to adjust performance. This increases the design complexity and adjustment difficulty of the system to some extent, and may also trigger various nonlinear couplings, leading to fluctuations or even instability in vibration isolation performance.
[0005] On the other hand, in recent years, inertial containers, as passive dynamic elements, have been introduced into vibration isolation systems due to their ability to significantly amplify the equivalent inertia of a system, thereby further reducing the equivalent natural frequency and improving low-frequency vibration isolation capabilities. Nut-screw-flywheel type inertial containers have already found some application in vehicle suspension and building structure vibration isolation. However, there is still a lack of effective integration of inertial containers with QZS vibration isolators, and full utilization of their inertial amplification and frictional dissipation effects to achieve broadband isolation of low-frequency vibrations. Utility Model Content
[0006] In view of the shortcomings of related technologies, the purpose of this utility model is to provide a quasi-zero stiffness vibration isolator and vibration isolation system based on inertial capacitance and linkage coupling, which aims to solve the problems of complex structure and unstable vibration isolation effect faced by existing quasi-zero stiffness vibration isolators in practical applications.
[0007] To achieve the above objectives, in a first aspect, this utility model provides a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling, characterized in that it includes: a linkage structure, a spring assembly, an inertial container, a vibration isolation plate, and a mounting base;
[0008] The linkage structure includes rods AB, AC, A'B', and A'C', all of which have the same length; the spring assembly includes a connecting spring and two support springs.
[0009] The A ends of the rods AB and AC are connected by a hinge joint, and the A' ends of the rods A'B' and A' ends of the rods A'C' are connected by a hinge joint; the A ends and A' ends of the connecting rod are connected by a horizontally parallel connecting spring and an inertial container.
[0010] The C end of rod AC and the C' end of rod A'C' are fixedly hinged to the mounting base; the B end of rod AB and the B' end of rod A'B' are fixedly hinged to the vibration isolation plate.
[0011] The B end of the rod AB and the C end of the rod AC are connected by a vertical support spring, and the B' end of the rod A'B' and the C' end of the rod A'C' are connected by another vertical support spring.
[0012] A vibration isolation target is placed on the vibration isolation plate. The support spring provides positive stiffness in the vertical direction, and the connecting spring provides negative stiffness in the vertical direction through the linkage structure. The inertia container amplifies the equivalent mass of the vibration isolation target through inertia to reduce the resonant frequency (of the vibration isolation system).
[0013] The positive and negative stiffness generated in the quasi-zero stiffness isolator cancel each other out to achieve a quasi-zero stiffness state.
[0014] Optionally, the inertial container is a screw-flywheel type inertial container.
[0015] Optionally, the stiffness k of the connecting spring a With respect to the stiffness k of the supporting spring z The ratio λ ranges from 1.5 to 4.
[0016] Optionally, the inertia container and the connecting spring are integrated with an X-shaped linkage structure.
[0017] Secondly, this utility model also provides a single-layer force-excited vibration isolation system, comprising: a vibration isolation target and a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any of the first aspects;
[0018] The mounting base of the quasi-zero stiffness vibration isolator is fixedly installed;
[0019] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0020] Thirdly, this utility model also provides a single-layer bottom displacement excitation vibration isolation system, including: a vibration isolation target and a quasi-zero stiffness vibration isolator and vibration isolation target based on inertial capacitance and linkage coupling as described in any of the first aspects;
[0021] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator;
[0022] The mounting base of the quasi-zero stiffness isolator is used to receive external displacement excitation.
[0023] Fourthly, this utility model also provides a double-layer flexible foundation force-excited vibration isolation system, including: a vibration isolation target, a flexible foundation, and a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any of the first aspects;
[0024] The mounting base of the quasi-zero stiffness vibration isolator is fixed on the flexible foundation;
[0025] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0026] Compared with the prior art, the above technical solution conceived by this utility model can achieve the following beneficial effects: This utility model provides a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling. It adopts a combination structure of X-shaped geometric nonlinear linkage (linkage structure and support spring), connecting spring, and inertial capacitance coupling. When the linkage is under force, it can generate a nonlinear restoring force related to displacement through geometric nonlinear effects, thereby achieving a local negative stiffness range at a specific pre-compression height. This negative stiffness can be offset by the positive stiffness provided by the vertical spring, making the system exhibit quasi-zero stiffness characteristics near the equilibrium point, effectively reducing the natural frequency and widening the low-frequency vibration isolation bandwidth. The inertial container and the transverse spring convert relative displacement into the rotational inertia of the flywheel, amplifying the equivalent mass of the structure. By adjusting the mass ratio of inertial capacitance to the vibration isolation target mass, the low-frequency vibration isolation effect can be significantly enhanced, and the vibration isolation bandwidth and resonance peak position can be flexibly controlled. The linkage pre-compression height Y0 and the inertial capacitance coefficient I... B There is a significant coupling effect. With a large pre-compression, the connecting rod geometric nonlinearity dominates, and the inertial capacitance effect is relatively limited; with a smaller pre-compression, the inertial capacitance contribution becomes significant. Therefore, by reasonably adjusting Y0 and I... B It can optimize the vibration isolation performance under different excitation conditions. Attached Figure Description
[0027] Figure 1This is a structural schematic diagram of a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling provided by this utility model;
[0028] Figure 2 This utility model provides a dimensionless restoring force F of a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling. r and stiffness K r Schematic diagram showing the variation of structural pre-compression height Y;
[0029] Figure 3 This is a structural schematic diagram of a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling provided by this utility model;
[0030] Figure 4 This is a three-dimensional view of a quasi-zero stiffness vibration isolator platform based on inertial capacitance and linkage coupling provided by this utility model, wherein (a) is the front view, (b) is the bottom view, and (c) is the side view.
[0031] In the above figures, the reference numerals are:
[0032] 1 is the vibration isolation plate, 2 is the mounting base, k1 is the support spring, k2 is the connecting spring, I b Let x1 be the displacement of the vibration isolation target, and y0 be the displacement of the vibration isolation plate in the vertical direction. Detailed Implementation
[0033] To make the objectives, technical solutions, and advantages of this utility model clearer, the present utility model will be further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are merely illustrative of the present utility model and are not intended to limit the present utility model. Furthermore, the technical features involved in the various embodiments of the present utility model described below can be combined with each other as long as they do not conflict with each other.
[0034] The following description, in conjunction with a preferred embodiment, illustrates the content involved in the above embodiments.
[0035] Example 1
[0036] like Figure 1 As shown, this utility model provides a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling, characterized in that it includes: a linkage structure, a spring assembly, and an inertial capacitance I. b 1. Vibration isolation plate and 2. Mounting base;
[0037] The linkage structure includes rods AB, AC, A'B', and A'C', all of which have the same length; the spring assembly includes a connecting spring k2 and two support springs.
[0038] The A ends of rods AB and AC are connected by a hinge joint, and the A' ends of rods A'B' and A'C' are connected by a hinge joint; the A ends and A' ends of the connecting rods are connected by a horizontally parallel connecting spring k2 and an inertial container I. b Connected;
[0039] The C end of the rod AC and the C' end of the rod A'C' are fixedly hinged to the mounting base 2; the B end of the rod AB and the B' end of the rod A'B' are fixedly hinged to the vibration isolation plate 1.
[0040] The B end of the rod AB and the C end of the rod AC are connected by a vertical support spring, and the B' end of the rod A'B' and the C' end of the rod A'C' are connected by another vertical support spring.
[0041] A vibration isolation target is placed on the vibration isolation plate 1. The support spring provides positive stiffness in the vertical direction, and the connecting spring k2 provides negative stiffness in the vertical direction through the linkage structure. The inertial container I... b The equivalent mass of the vibration isolation target is amplified by inertia to reduce the resonant frequency;
[0042] The positive and negative stiffness generated in the quasi-zero stiffness isolator cancel each other out to achieve a quasi-zero stiffness state.
[0043] In this embodiment of the invention, the quasi-zero stiffness vibration isolator mainly includes an inertial container I. b And an X-shaped linkage structure nonlinear vibration isolation element. By combining the X-shaped geometrically nonlinear linkage structure with the inertial container I b Integration, utilizing the quasi-zero stiffness effect generated by geometric nonlinearity and the inertial container I b The combined effect of inertial amplification significantly reduces the natural frequency of the vibration isolation system in the low-frequency range, broadening the effective isolation bandwidth. Furthermore, addressing the unavoidable frictional damping effect within the inertial container, the design incorporates the Jenkins friction model to parameterize and model its nonlinear frictional force. The friction threshold can be obtained experimentally, resulting in a stick-slip transition and dynamically adjusting energy dissipation. This mechanism effectively suppresses resonance amplification caused by geometric nonlinearity and inertial capacitance, and improves the stability of the vibration isolator in the mid-to-high frequency range. Enhanced energy dissipation helps suppress nonlinear instability caused by large-amplitude excitation. Through multi-parameter coupling adjustment (such as connecting rod geometry, pre-compression height, connecting spring stiffness, and inertial container inertia coefficient), good low-frequency vibration isolation performance and system dynamic stability can be maintained, making it particularly suitable for high-efficiency vibration isolation requirements in marine equipment, flexible foundations, or low-frequency strongly coupled environments.
[0044] The inertial container is a screw-flywheel type. The inertial container introduces a proportional amplification effect between acceleration and inertial force. The inertial capacity coefficient of the inertial container can be adjusted by changing the flywheel mass and radius to provide a greater inertial effect at lower frequencies, thus widening the vibration isolation bandwidth. Furthermore, the inertial capacity coefficient I... B The parameters of the nut-screw, flywheel radius, and mass determine the design flexibility based on the target vibration isolation frequency band. A larger I... B Enhancing low-frequency inertial amplification ensures that the inertial amplification effect is fully utilized in the low-frequency range, but may cause amplification effects in the high-frequency range. It is necessary to combine Y0 (connecting rod pre-compression height) and connecting spring adjustment to avoid high-frequency side effects.
[0045] like Figure 1 As shown, the quasi-zero stiffness vibration isolator comprises an X-shaped geometrically nonlinear linkage structure, inertial capacitance elements, connecting springs, and supporting springs, forming a tunable negative stiffness-inertial capacitance coupled vibration isolation structure. Four equal-length linkages (AB, AC, A'B', A'C') are symmetrically hinged, forming a typical X-shaped planar structure. Ends B and B' are connected to the vibration isolation target, while C and C' are fixed to the mounting base 2 (foundation or excitation base). A and A' are intermediate hinge points. The longitudinal stiffness nonlinearity caused by lateral displacement is achieved through geometrically nonlinear deformation within the linkages. Simultaneously, a set of inertial capacitance elements based on a nut-screw structure is arranged in series between A and A' to introduce a proportional amplification effect between acceleration and inertial force. The inertial capacitance value of this element can be adjusted by changing the flywheel mass and radius to provide a greater inertial effect at lower frequencies, thus widening the vibration isolation bandwidth. Connecting spring k2 and supporting spring k1 jointly adjust the overall stiffness distribution of the vibration isolation system. The support springs provide the necessary load-bearing stiffness for the vibration isolation target, while the connecting springs, together with the geometric nonlinearity of the X-type connecting rods, form a quasi-zero stiffness characteristic. The parameters of the connecting springs (stiffness, initial length, etc.) and the pre-compression amount y0 of the structure are adjustable, which can adjust the width of the negative stiffness range and tune the nonlinear equivalent stiffness.
[0046] Furthermore, in practical engineering applications, the vibration isolation plate in the quasi-zero stiffness vibration isolator can be simplified, and the vibration isolation target can be directly fixed and hinged to the connecting rod and support spring.
[0047] Optionally, the stiffness k of the connecting spring a With respect to the stiffness k of the supporting spring z The ratio λ ranges from 1.5 to 4.
[0048] When designing a quasi-zero stiffness vibration isolator, parameter analysis is performed within the range of the above parameters to analyze the influence of each parameter on the equivalent stiffness, and the optimal parameter combination is selected to construct the quasi-zero stiffness vibration isolator.
[0049] This embodiment of the invention employs an X-shaped geometrically nonlinear linkage structure. When subjected to force, it generates a nonlinear restoring force related to displacement through geometrical nonlinear effects, thereby achieving a local negative stiffness range at a specific pre-compression height. This negative stiffness can cancel out the positive stiffness provided by the vertical spring, causing the system to exhibit quasi-zero stiffness characteristics QZS near the equilibrium point, effectively reducing the natural frequency and widening the low-frequency vibration isolation bandwidth. The inertia container converts relative displacement into the rotational inertia of the flywheel, amplifying the equivalent mass of the structure. By adjusting the mass ratio of the inertia container to the target vibration isolation mass, the low-frequency vibration isolation effect can be significantly enhanced, and the vibration isolation bandwidth and resonance peak position can be flexibly controlled. The ratio of the linkage pre-compression height (Y0) to the inertia container coefficient (I) B There is a significant coupling effect. When the pre-compression is large, the geometric nonlinearity of the connecting rod dominates, and the inertial capacitance effect is relatively limited; when the pre-compression decreases, the inertial capacitance contribution becomes significant. Therefore, by reasonably adjusting Y0 and I... B It can optimize the vibration isolation performance under different excitation conditions.
[0050] like Figure 2 As shown, the quasi-zero stiffness isolator achieves a dynamic balance between equivalent negative stiffness and positive stiffness at and near its static equilibrium point, resulting in quasi-zero stiffness. This significantly reduces the natural frequency of the isolation system and expands the low-frequency isolation bandwidth. Experimental and simulation results show that the resonant frequency of the isolation system constructed by the quasi-zero stiffness isolator based on inertial capacitance and linkage coupling provided in this embodiment is significantly lower than that of the traditional linear isolator, the peak displacement transmissibility is effectively suppressed, and the low-frequency isolation effect is significantly improved.
[0051] In multiple simulations and experimental verifications, the quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling provided by this invention has been successfully applied in typical scenarios such as marine equipment and precision instrument platforms, demonstrating good suppression effects on low-frequency impacts and continuous vibrations. Its structural design principles can be extended to other vibration isolation applications, such as marine engineering, aerospace, and vehicle suspension, and are expected to significantly improve the operational safety and service life of various equipment systems.
[0052] Furthermore, based on the above embodiments, by adjusting the link length and the angle between the links in the linkage structure, the vibration isolator can adapt to different vibration conditions, including excitations of different amplitudes and frequencies. Adjusting the nonlinear stiffness of the system under different excitation conditions ensures that the vibration isolator maintains good vibration isolation performance even with changes in load or vibration frequency, avoiding the performance degradation problem caused by stiffness instability in traditional designs. This makes the quasi-zero stiffness vibration isolator of this solution widely adaptable and able to meet the needs of various industrial applications.
[0053] Furthermore, in practical engineering, quasi-zero stiffness vibration isolators are installed inside the frame during application. For example... Figure 3As shown, a physical structural diagram of a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling is presented, such as... Figure 4 The figure shows a three-view diagram of a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling.
[0054] The frame includes two fixed columns, which connect the frame to the quasi-zero stiffness isolator. The upper ends of the fixed columns on both sides are fixedly connected to the upper edge of the frame, and the fixed columns on both sides pass through the vibration isolation plate and are fixedly connected to the mounting base. Under the action of external excitation force, the vibration isolation plate vibrates vertically along the fixed columns. The frame allows the quasi-zero stiffness isolator to be more stably fixed in the target position; the mounting base can more effectively and firmly fix it to the external vibration source.
[0055] This utility model improves upon key parameters such as pre-compression height Y0 and structural horizontal width L. q The stiffness ratio η of the connecting spring and the support spring, and the initial length L of the connecting spring. h System design and optimization were conducted, establishing a tunable quasi-zero stiffness range coupled with an inertial capacitance amplification effect. This mechanism is used to adjust the system's geometric nonlinearity; the smaller the value of Y0, the higher the pre-compression of the connecting rod and the more significant the negative stiffness effect. However, excessively low Y0 will suppress the inertial effect of the inertial container, affecting the low-frequency vibration isolation performance brought about by inertial capacitance amplification. Therefore, Y0 needs to be adjusted in conjunction with I... B Coordination and matching lead to coupled optimal design. Inertia coefficient I B The design can be flexibly tailored to the target vibration isolation frequency band, determined by the nut-screw parameters, flywheel radius, and mass. A larger I... B Improving low-frequency inertial amplification may cause amplification effects in the high-frequency region; therefore, it is necessary to adjust Y0 and the connecting spring to avoid high-frequency side effects. The stiffness ratio η of the connecting spring and the support spring, and the initial spring length L... h This determines the coverage range of the negative stiffness range and the LFVI (low-frequency isolation range). Increasing the η value can widen the negative stiffness range and extend the performance of QZS; L h The change will affect the equivalent arm of the connecting rod, adjusting the negative stiffness effect.
[0056] Based on the specific engineering installation constraints, the optimal set of parameter configurations is selected from multiple sets of parameter configurations to construct a quasi-zero stiffness vibration isolator, which has the same beneficial effects as the quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling in Example 1.
[0057] This embodiment of the invention achieves a dynamic balance between equivalent negative and positive stiffness at and near the static equilibrium point by coordinating the parameters of the X-shaped connecting rod's geometric nonlinear structure with those of the connecting and supporting springs, combined with the additional inertia introduced by the inertial container unit, resulting in quasi-zero stiffness characteristics. The combination of the connecting rod's geometric design and the connecting and supporting springs allows the vibration isolator to exhibit nonlinear stiffness variations under different excitation amplitudes. This allows for adjustment of dynamic stiffness according to load changes and operating conditions, preventing instability or degradation of vibration isolation performance caused by large vibrations or load variations. The required stiffness curve can be flexibly achieved by adjusting the connecting rod length, connection angle, and horizontal spacing. The integrated screw-flywheel-based inertial container provides a significant inertial amplification effect, further reducing the equivalent natural frequency and improving low-frequency vibration isolation capability. Simultaneously, the embedded friction unit (such as a Jenkins element) generates controllable dry friction during flywheel rotation, dissipating excess vibration energy through stick-slip transition, effectively mitigating resonance peak amplification and instability caused by geometric nonlinearity. Experimental identification results also verify the rationality and stability of this friction effect. Compared to the traditional QZS structure, this invention emphasizes the coupling and adjustment characteristics between parameters. For example, the connecting rod pre-compression height Y0 and the inertial-capacitance ratio I... B This allows for complementary adjustment; when the pre-compression height is large, it can fully release the negative stiffness range caused by geometric nonlinearity; simultaneously, it can appropriately reduce I. B This design avoids the amplification of high-frequency vibrations caused by inertia capacitance, achieving superior vibration isolation performance. In this embodiment, the inertia container, friction unit, and X-type linkage structure are efficiently integrated, avoiding the shortcomings of traditional QZS solutions which require multiple sets of tilting springs, limiting mechanisms, or complex multi-stage adjustment mechanisms. The entire design is easily realized through conventional machining and assembly, featuring a compact structure, flexible adjustment, and good engineering scalability.
[0058] This utility model provides a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling. It employs an X-shaped geometrically nonlinear linkage structure combined with a vertical spring. By rationally designing geometric parameters such as linkage length, horizontal spacing, and width, a significant geometrically nonlinear negative stiffness effect is generated at a specific pre-compression height, balancing with the positive stiffness spring to form quasi-zero stiffness characteristics. The inertia-mass ratio of the inertial capacitance can be flexibly designed by adjusting the flywheel size and lead screw parameters, significantly enhancing the low-frequency vibration isolation effect. Furthermore, the isolation bandwidth and resonance peak position can be flexibly adjusted to meet different low-frequency vibration isolation requirements. This solves the problems of structural complexity and unstable isolation effect faced by existing quasi-zero stiffness vibration isolators in practical applications, achieving wideband low-frequency vibration isolation, improving the reliability of the isolator, and significantly reducing energy consumption and maintenance costs during operation.
[0059] Example 2
[0060] This utility model also provides a single-layer force-excited vibration isolation system, including: a vibration isolation target and a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any one of Embodiment 1;
[0061] The mounting base of the quasi-zero stiffness vibration isolator is fixedly installed;
[0062] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0063] In an alternative embodiment, the present invention also provides a single-layer bottom displacement excitation vibration isolation system, comprising: a vibration isolation target and a quasi-zero stiffness vibration isolator and vibration isolation target based on inertial capacitance and linkage coupling as described in any one of Embodiment 1;
[0064] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator;
[0065] The mounting base of the quasi-zero stiffness isolator is used to receive external displacement excitation.
[0066] In an alternative embodiment, the present invention also provides a double-layer flexible foundation force-excited vibration isolation system, comprising: a vibration isolation target, a flexible foundation, and a quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any one of Embodiment 1, the vibration isolation target, and the flexible foundation;
[0067] The mounting base of the quasi-zero stiffness vibration isolator is fixed on the flexible foundation;
[0068] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0069] The quasi-zero stiffness vibration isolator provided in Embodiment 1 of this utility model can be applied to various vibration isolation systems. Under different excitation forces, it can reduce the resonance frequency of the vibration isolation system and achieve quasi-zero stiffness characteristics.
[0070] Those skilled in the art will readily understand that the above description is merely a preferred embodiment of the present utility model and is not intended to limit the present utility model. Any modifications, equivalent substitutions, and improvements made within the spirit and principles of the present utility model should be included within the protection scope of the present utility model.
Claims
1. A quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling, characterized in that, include: Linkage structure, spring assembly, inertia container, vibration damping plate, and mounting base; The linkage structure includes rods AB, AC, A'B', and A'C', all of which have the same length; the spring assembly includes a connecting spring and two support springs. The rods AB and AC are connected at end A by a hinge joint, and the rods A'B' and A'C' are connected at end A' by a hinge joint; the ends A and A' are connected by a horizontally parallel connecting spring and an inertial container. The C end of rod AC and the C' end of rod A'C' are fixedly hinged to the mounting base; the B end of rod AB and the B' end of rod A'B' are fixedly hinged to the vibration isolation plate. The B end of the rod AB and the C end of the rod AC are connected by a vertical support spring, and the B' end of the rod A'B' and the C' end of the rod A'C' are connected by another vertical support spring. A vibration isolation target is placed on the vibration isolation plate. The support spring provides positive stiffness in the vertical direction, and the connecting spring provides negative stiffness in the vertical direction through the linkage structure. The inertia container amplifies the equivalent mass of the vibration isolation target through inertia to reduce the resonant frequency. The positive and negative stiffness generated in the quasi-zero stiffness isolator cancel each other out to achieve a quasi-zero stiffness state.
2. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The inertial navigation system is a screw-flywheel type inertial navigation system.
3. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The stiffness k of the connecting spring a With respect to the stiffness k of the supporting spring z The ratio λ ranges from 1.5 to 4.
4. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The inertial container and the connecting spring are integrated with an X-shaped linkage structure.
5. A single-layer force-excited vibration isolation system, characterized in that, include: Vibration isolation target and quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any one of claims 1-4; The mounting base of the quasi-zero stiffness vibration isolator is fixedly installed; The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
6. A single-layer bottom displacement-excited vibration isolation system, characterized in that, include: Vibration isolation target and quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any one of claims 1-4; The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator; The mounting base of the quasi-zero stiffness isolator is used to receive external displacement excitation.
7. A double-layer flexible foundation force-excited vibration isolation system, characterized in that, include: Vibration isolation target, flexible foundation, and quasi-zero stiffness vibration isolator based on inertial capacitance and linkage coupling as described in any one of claims 1-4; The mounting base of the quasi-zero stiffness vibration isolator is fixed on the flexible foundation; The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.