A quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling
By using the design of elastic gap limiting and linkage coupling, the stability and vibration isolation effect of the quasi-zero stiffness vibration isolator are improved, solving the problems of insufficient performance and complex structure of existing vibration isolators in the low frequency range, and making it suitable for various working conditions.
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
- 2026-06-26
AI Technical Summary
Existing quasi-zero stiffness vibration isolators suffer from problems such as complex structure, unstable vibration isolation effect, and difficulty in adapting to changes in the mass of the vibration isolation target and changes in external excitation load in practical applications.
By employing a design that combines gap elastic limiting and linkage coupling, the linkage mechanism and linear spring constraint assembly achieve a balance between negative and positive stiffness, providing stable vibration isolation performance.
The structure of the vibration isolator has been simplified, the vibration isolation effect has been improved, the vibration isolation bandwidth has been expanded, and the adaptability has been strengthened. It can effectively isolate low-frequency vibrations and solve the problem of insufficient performance of traditional linear vibration isolators in the low-frequency range.
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Figure CN224414235U_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 based on gap elastic limiting and linkage coupling. Background Technology
[0002] With the increasing demand for low-frequency vibration control, quasi-zero stiffness (QZS) vibration isolators have been widely used in many engineering fields. While existing linear vibration dampers have addressed vibration issues to some extent, their isolation performance in the low-frequency range is poor. Therefore, to improve low-frequency vibration isolation performance, researchers have gradually introduced nonlinear stiffness elements, enabling isolators to effectively enhance their isolation effect in the low-frequency band. Quasi-zero stiffness isolators achieve quasi-zero stiffness characteristics within a specific frequency range through the design of a special negative stiffness structure. This design effectively extends the isolation bandwidth of the isolator while maintaining high static stiffness, thereby improving the system's load-bearing capacity.
[0003] Traditional quasi-zero stiffness vibration isolators mainly consist of two key components: a vertical spring and a transverse spring. Through proper design, the stiffness characteristics of these two components interact, generating negative stiffness within a specific dynamic range, which cancels out the positive stiffness of the springs, thus achieving quasi-zero stiffness characteristics at the static equilibrium position. The greatest advantage of this design is that it can significantly extend the isolation bandwidth of the isolator while maintaining high static stiffness, thereby enhancing the system's load-bearing capacity.
[0004] However, existing quasi-zero stiffness isolators still face several challenges in practical applications. First, many QZS isolator designs rely on a single type of stiffness element, making it difficult to maintain stable isolation performance over a wide excitation range. To optimize isolation performance, many studies have introduced multiple spring combinations or other nonlinear structures. While this can improve isolation performance, it also increases the structural complexity of the isolator and may lead to instability under dynamic excitation. Furthermore, existing QZS isolators often fail to adapt quickly to changes in the target mass and external excitation load, resulting in deviations from the quasi-zero stiffness range, a significant decrease in isolation effectiveness, and potentially structural instability under large deformations. Additionally, existing designs often optimize isolation through multiple spring configurations. While this theoretically improves performance, in practical applications, the interaction of multiple nonlinear structures can lead to instability and require complex adjustments.
[0005] In summary, existing QZS vibration isolators still face some technical bottlenecks in terms of performance optimization and application stability. 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 based on gap elastic limiting 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 gap elastic limiting and linkage coupling, comprising: a linkage mechanism, a linear spring constraint assembly, a vibration isolation plate, and a mounting base;
[0008] The linkage mechanism includes links AB, AC, A'B', and A'C', all of which have the same length; the linear spring constraint assembly includes a connecting spring, two support springs, and a limiting spring.
[0009] 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' of the connecting rods are connected by a horizontally placed connecting spring to form an X-shaped assembly.
[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] The E end of the limiting spring EF is fixed on the mounting base, and the F end is spaced at a preset distance from the inner side of the vibration isolation plate.
[0013] Optionally, the E end of the limiting spring EF is fixedly disposed in the middle of the mounting base.
[0014] Optionally, the stiffness k of the limiting spring u With respect to the stiffness k of the supporting spring z The ratio η ranges from 0.1 to 0.9.
[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 preset distance between the limiting spring and the vibration isolation plate is in the range of 0.02 to 0.1.
[0017] Secondly, 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 gap elastic limiting and linkage coupling as described in any of the first aspects;
[0018] The mounting base of the quasi-zero stiffness vibration isolator is fixed;
[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 based on gap elastic limiting 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 gap elastic limiting 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 existing technologies, the above-described technical solution of this utility model achieves the following beneficial effects: A quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling, by setting a connecting spring as a gap elastic limiting device, whose two ends are respectively connected to the linkage mechanism to form a coupling structure, works together to provide efficient and stable vibration isolation performance for the quasi-zero stiffness vibration isolator under conditions such as load changes and vibration frequency changes. The gap elastic limiting device realizes the positive stiffness compensation characteristic of the vibration isolator under large deformation through a unique elastic element setting, and enhances the adaptability and stability of the vibration isolator. The linkage mechanism is used to adjust the nonlinear negative stiffness of the system and improve the vibration isolation bandwidth. Through the balance mechanism of negative stiffness and positive stiffness, quasi-zero stiffness characteristics are achieved at the static equilibrium position, enabling the system to adapt to large load fluctuations and provide a stable and efficient vibration isolation effect; and it is suitable for various working conditions. This vibration isolator can effectively reduce the transmission of low-frequency vibrations and provide a relatively stable vibration isolation effect under various working conditions. The structure of the quasi-zero stiffness vibration isolator has been simplified, reducing manufacturing costs while improving product reliability and stability, and making it more adaptable. It has also improved vibration isolation performance, effectively isolating low-frequency vibrations and significantly expanding the vibration isolation bandwidth, especially performing excellently in the low-frequency range, thus solving the problem of insufficient performance of traditional linear vibration isolators in the low-frequency range. Attached Figure Description
[0027] Figure 1 This is a structural schematic diagram of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling provided by this utility model;
[0028] Figure 2 This is an experimental and simulation comparison curve of the transmissivity of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling provided by this utility model and a traditional linear vibration isolation system.
[0029] Figure 3 This utility model provides a dimensionless restoring force F of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling. r and stiffness K r Schematic diagram showing the variation of structural pre-compression height Y;
[0030] Figure 4 This is a schematic diagram of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling provided by this utility model;
[0031] Figure 5 This is a three-dimensional view of a quasi-zero stiffness vibration isolator platform based on gap elastic limiting 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.
[0032] In the above figures, the reference numerals are:
[0033] 1 is a vibration isolation plate, 2 is a mounting base, and k z To support the spring, k a For connecting springs, x1 is the displacement of the vibration isolation target, y is the displacement of the vibration isolation plate in the vertical direction, and h is the preset distance. Detailed Implementation
[0034] 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.
[0035] The following description, in conjunction with a preferred embodiment, illustrates the content involved in the above embodiments.
[0036] Example 1
[0037] like Figure 1 As shown, this utility model provides a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling, including: linkage mechanism, linear spring constraint assembly, vibration isolation plate 1 and mounting base 2;
[0038] The linkage mechanism includes links AB, AC, A'B', and A'C', all of which have the same length; the linear spring constraint assembly includes a connecting spring, two support springs, and a limiting spring.
[0039] 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' of the connecting rods are connected by a horizontally placed connecting spring to form an X-shaped assembly.
[0040] 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.
[0041] 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.
[0042] The E end of the limiting spring EF is fixed on the mounting base 2, and the F end is spaced at a preset distance from the inner side of the vibration isolation plate 1.
[0043] In this embodiment of the invention, two support springs provide the main stiffness adjustment function, providing vertical support force to support the vibration isolation target placed on the vibration isolation plate, ensuring that the vibration isolator maintains a stable vibration isolation effect under different working conditions. The linkage mechanism, by changing the relative positions between components, allows the quasi-zero stiffness isolator to adjust the compression / tension length of the linear spring constraint components under different excitation conditions, providing flexible negative stiffness control. Specifically, the linkage mechanism achieves fine nonlinear negative stiffness adjustment by adjusting the relative positions between each link, further improving the isolation bandwidth and system stability. The limiting spring, as a vertical gap elastic limiter, is responsible for controlling the positive stiffness compensation characteristics of the quasi-zero stiffness isolator. Within a certain range of motion amplitude, it can make contact to provide a positive stiffness compensation effect, balancing the excessive negative stiffness generated by the X-linkage structure of the quasi-zero stiffness isolator, achieving quasi-zero stiffness characteristics at the static equilibrium point. Specifically, the design of the gap elastic limiter can regulate the system to quasi-zero stiffness under low-frequency variable load vibration, enabling the isolator to effectively reduce the transmission of low-frequency vibrations.
[0044] like Figure 1 As shown in the figure, the preset distance between the F end of the limiting spring EF and the inner side of the vibration isolation plate 1 is represented by h, and the displacement generated by the vibration isolation plate 1 in the vertical direction is represented by y. When low-frequency excitation is applied to the vibration isolation target, there are two cases in which the vibration isolator can achieve quasi-zero stiffness characteristics.
[0045] When the vertical displacement of the vibration isolation plate 1 is less than the preset distance h, that is, when the vibration isolation plate 1 is not in contact with the limiting spring, the two support springs are compressed and generate elastic force in the vertical direction. The relative positions between the links of the linkage mechanism change, the angle between link AB and link AC decreases, the angle between link A'B' and link A'C' decreases, the length of the connecting spring is compressed, and elastic force is generated in the horizontal direction. This elastic force is decomposed into a vertical support force through the linkage mechanism. The support force generated by the support spring and the connecting spring is used to maintain the stability of the vibration isolation target placed on the vibration isolation plate 1. At this time, the support spring provides positive stiffness in the vertical direction, and the connecting spring provides negative stiffness in the vertical direction through the linkage mechanism.
[0046] When the vertical displacement of the vibration isolation plate 1 is greater than or equal to the preset distance h, the two support springs are compressed and generate elastic force in the vertical direction. The relative positions of the links in the linkage mechanism change, the angle between links AB and AC continues to decrease, the angle between links A'B' and A'C' continues to decrease, the length of the connecting spring is further compressed, and elastic force is generated in the horizontal direction. This elastic force is decomposed into a vertical support force through the linkage mechanism. The limiting spring begins to compress and generates elastic force in the vertical direction. The support force generated by the support spring, connecting spring, and limiting spring is used to maintain the stability of the vibration isolation target placed on the vibration isolation plate 1. At this time, the support spring provides positive stiffness, the connecting spring provides negative stiffness in the vertical direction through the linkage mechanism, and the limiting spring provides additional positive stiffness to prevent the mechanism from folding and failing due to over-compression. The positive and negative stiffness generated in the quasi-zero stiffness vibration isolator cancel each other out, achieving zero stiffness characteristics.
[0047] Furthermore, in practical engineering applications, the vibration isolation plate 1 in the quasi-zero stiffness vibration isolator can be simplified, and the vibration isolation target can be directly fixedly connected to the connecting rod and the support spring.
[0048] This embodiment of the invention employs a coupled structure of a linkage mechanism and a linear spring constraint assembly to achieve a balance between negative and positive stiffness at the static equilibrium point. This avoids the stability failure that occurs when using a linkage mechanism alone, while allowing for a larger negative stiffness operating range and supporting a wider quasi-zero stiffness bandwidth. This ensures that the vibration isolator can achieve quasi-zero stiffness characteristics in the low-frequency vibration range, thereby effectively isolating vibration and broadening the vibration isolation bandwidth. Figure 2 As shown in the figure, the vibration transmission rate of the vibration isolator is illustrated. The figure also shows the force transmission rate curves of the proposed vibration isolation system and the traditional linear vibration isolation system. Experimental and simulation results reveal that the resonant frequency of the proposed nonlinear vibration isolator system is significantly reduced, and the low-frequency bandwidth is decreased, demonstrating excellent improved vibration isolation performance.
[0049] Optionally, the E end of the limiting spring EF is fixedly disposed in the middle of the mounting base 2.
[0050] The limiting spring EF can be set at any suitable position on the mounting base 2. In this embodiment, it is preferably set in the middle of the mounting base 2 to provide support force in the middle position of the vibration isolation plate, which is beneficial to the stability of the vibration isolation target.
[0051] Optionally, the stiffness k of the limiting spring u With respect to the stiffness k of the supporting spring z The ratio η ranges from 0.1 to 0.9.
[0052] Optionally, the stiffness k of the connecting spring aWith respect to the stiffness k of the supporting spring z The ratio λ ranges from 1.5 to 4.
[0053] Optionally, the preset distance between the limiting spring and the vibration isolation plate is in the range of 0.02 to 0.1.
[0054] 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. The optimal parameter combination is then selected to construct a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling.
[0055] Furthermore, based on the above embodiments, by adjusting the link length and the angle between the links in the linkage mechanism, 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.
[0056] Furthermore, in practical engineering, quasi-zero stiffness vibration isolators are installed inside the frame during application. For example... Figure 4 As shown, a physical structural diagram of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling is presented, such as... Figure 5 The figure shows a three-view diagram of a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling.
[0057] The frame comprises three fixed columns, which connect the frame to the quasi-zero stiffness isolator. The upper ends of the two side columns are fixedly connected to the upper edge of the frame, and these columns pass through the vibration isolation plate and are fixedly connected to the mounting base. The middle column is fixedly connected to the vibration isolation plate. Under external excitation, the vibration isolation plate vibrates vertically along the fixed columns. The frame allows the quasi-zero stiffness isolator to be more securely fixed at the target location; the mounting base can more effectively and firmly fix it to the external vibration source.
[0058] In practical implementation, the connecting spring can be selected based on the operating frequency and load requirements of the quasi-zero stiffness isolator. For example, the spring stiffness can be adjusted by changing parameters such as its diameter, length, and material to ensure negative stiffness characteristics under low-frequency excitation. The connection method of the linkage mechanism is crucial to the stability of the isolator. In this embodiment, the connection method of the linkage mechanism ensures that the system can operate stably during vibration without excessive deformation or instability. The length, angle, and material selection of the linkage all affect the performance of the isolator, so these parameters need to be optimized during design. To achieve a balance between negative and positive stiffness in the quasi-zero stiffness isolator, the spring stiffness, the size of the gap elastic limiter, and the connection method of the linkage coupling structure need to be adjusted according to the operating environment of the isolator. In practical applications, the system performance can be further improved through experimentation and optimization.
[0059] like Figure 3 As shown, the parameters of the quasi-zero stiffness isolator affect the restoring force F. r and stiffness K r The impact.
[0060] exist Figure 3 In (a) and (d), the constraint stiffness ratio (limiting spring k) is... u and support spring k z The stiffness ratio η varies within the range of 0.1 to 0.9, the constraint gap D (preset distance) is set to 0.08, and the stiffness ratio (horizontal spring k) is... a and support spring k z The stiffness ratio λ is set to 3.
[0061] exist Figure 3 In (b) and (e), when η = 0.9 and λ = 4, the gap D is considered to vary from 0.02 to 0.10.
[0062] exist Figure 3 In (c) and (f), λ varies within the range of 1.5 to 4, while other parameters are fixed at η = 0.3 and D = 0.03. The horizontal distance parameter L... a and dimensionless rod length L s The value is fixed at 0.5. To reflect the system characteristics under typical operating conditions, the pre-compression height Y of the X-type linkage structure varies from 0.1 to 0.9.
[0063] Figure 3 (a) shows that when the precompression height Y exceeds the threshold, the restoring force F r Pointing towards the ground, the restoring force is positive. As the structure is compressed, the restoring force decreases and becomes negative, pointing upwards. When Y is less than 0.42 (e.g., L...), the restoring force is negative. uWhen η = 0.5 - D = 0.42, the spring in the constraint will contact the ground and provide additional negative resistance pointing upwards. Increasing the value of η can achieve greater restoring force when the pre-compression height Y varies between 0.42 and 0.1.
[0064] exist Figure 3 In (d), the stiffness k r The value decreases from positive to 0. When the terminal distance Y changes from 0.9 to 0.1, it becomes negative again. When the constraint stiffness η≠0, the total stiffness suddenly increases at Y=0.42. When Y<0.42, the total stiffness tends to increase with the increase of the stiffness ratio η.
[0065] Figure 3 Figures (b) and (e) show that when the structure is compressed from Y = 0.9 to Y = 0.4, the engagement of the constraints can increase the resistance and stiffness at the design location by changing the gap D. A smaller gap D in the spring constraint can lead to earlier engagement, which can produce stronger resistance and higher stiffness at the same pre-compression height Y.
[0066] 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 based on gap elastic limit and linkage coupling.
[0067] This invention provides a quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling. Combining a gap elastic limiting device with a linkage structure, a reasonable coupling mechanism achieves a balance between negative and positive stiffness, thus providing quasi-zero stiffness characteristics at the static equilibrium position and significantly improving the isolator's isolation bandwidth. Compared to traditional quasi-zero stiffness vibration isolators, this invention significantly simplifies system complexity through a reasonable structural design. It solves the problem of insufficient vibration isolation performance of traditional vibration isolators in the low-frequency range, making it particularly suitable for high-load, low-frequency vibration scenarios. It avoids redundant additional mechanical components, improving the reliability and manufacturing feasibility of the vibration isolator.
[0068] Example 2
[0069] 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 gap elastic limiting and linkage coupling as described in any one of Embodiment 1;
[0070] The mounting base of the quasi-zero stiffness vibration isolator is fixed;
[0071] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0072] 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 based on gap elastic limiting and linkage coupling as described in any one of Embodiment 1;
[0073] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator;
[0074] The mounting base of the quasi-zero stiffness isolator is used to receive external displacement excitation.
[0075] 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 gap elastic limiting and linkage coupling as described in any one of Embodiment 1;
[0076] The mounting base of the quasi-zero stiffness vibration isolator is fixed on the flexible foundation;
[0077] The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
[0078] 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.
[0079] 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 gap elastic limiting and linkage coupling, characterized in that, include: Linkage mechanism, linear spring constraint assembly, vibration isolation plate and mounting base; The linkage mechanism includes links AB, AC, A'B', and A'C', all of which have the same length; the linear spring constraint assembly includes a connecting spring, two support springs, and a limiting spring. 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' of the connecting rods are connected by a horizontally placed connecting spring to form an X-shaped assembly. 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. The E end of the limiting spring EF is fixed on the mounting base, and the F end is spaced at a preset distance from the inner side of the vibration isolation plate.
2. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The E end of the limiting spring EF is fixedly disposed in the middle of the mounting base.
3. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The stiffness k of the limiting spring u With respect to the stiffness k of the supporting spring z The ratio η ranges from 0.1 to 0.
9.
4. 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.
5. The quasi-zero stiffness vibration isolator as described in claim 1, characterized in that, The preset distance between the limiting spring and the vibration isolation plate ranges from 0.02 to 0.
1.
6. A single-layer force-excited vibration isolation system, characterized in that, include: The vibration isolation target and the quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling as described in any one of claims 1-5; The mounting base of the quasi-zero stiffness vibration isolator is fixed; The vibration isolation target is installed on the vibration isolation plate of the quasi-zero stiffness vibration isolator to receive external excitation force.
7. A single-layer bottom displacement-excited vibration isolation system, characterized in that, include: The vibration isolation target and the quasi-zero stiffness vibration isolator based on gap elastic limiting and linkage coupling as described in any one of claims 1-5; 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.
8. 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 gap elastic limiting and linkage coupling as described in any one of claims 1-5; 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.