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摘要: 振动诱发的结构疲劳、动态失稳与功能退化严重影响装备的服役可靠性, 因此实施有效的隔振措施至关重要. 然而, 传统线性隔振结构受制于低静刚度与承载能力之间固有矛盾, 难以实现有效的低频振动隔离. 近年来, 准零刚度隔振结构因其能保持高静刚度的同时显著降低动刚度, 从而将隔振频率拓展至低频甚至超低频, 而受到广泛关注. 本文以典型准零刚度隔振结构的实现方式为切入点, 系统综述了斜弹簧式、连杆−弹簧式、凸轮−滚子式、屈曲梁/板/环式、永磁铁式、折纸式以及仿生式等多种准零刚度隔振结构的设计方法. 在此基础上, 进一步梳理了多层准零刚度隔振结构与多向准零刚度隔振结构的研究进展, 并总结了准零刚度隔振结构在交通运输、机械传动、医疗器械、土木工程及输流管道等领域的典型应用. 面对工业装备向高端化、精密化持续演进的趋势, 本文最后结合拓扑优化、数据驱动建模、主动控制及振动能量俘获等新兴研究方向, 对准零刚度隔振技术的未来发展进行了展望, 以期为该领域的深入研究提供参考.Abstract: Vibration-induced structural fatigue, dynamic instability, and functional degradation can significantly reduce the service reliability of engineering equipment, making effective vibration isolation essential. However, conventional linear vibration isolation structures are limited by the inherent trade-off between low static stiffness and load-bearing capacity, which restricts their performance at low frequencies. Quasi-zero-stiffness (QZS) vibration isolation structures have therefore attracted increasing attention because they combine high static stiffness with low dynamic stiffness, enabling vibration isolation at low and even ultra-low frequencies. This paper reviews typical QZS designs, including oblique-spring, linkage–spring, cam–roller, buckled beam/plate/ring, permanent-magnet, origami-inspired, and bio-inspired configurations. Recent developments in multilayer and multidirectional QZS vibration isolation structures are also summarized, together with representative applications in transportation, mechanical transmission, medical equipment, civil engineering, and fluid-conveying pipelines. Finally, future research directions are discussed, including topology optimization, data-driven modelling, active control, and vibration energy harvesting. This review aims to provide a useful reference for further development of QZS vibration isolation technology.
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图 4 斜弹簧准零刚度隔振结构. (a)三弹簧准零刚度结构(Carrella et al. 2007), (b)五弹簧准零刚度结构(Xu et al. 2014), (c)含两对斜弹簧的准零刚度结构(Zhao et al. 2021), (d)双侧阻尼多弹簧准零刚度结构(Hao et al. 2016), (e)半主动多弹簧准零刚度结构(Wen et al. 2021), (f)利用侧向弹簧刚度调控的半主动准零刚度结构(Ran et al. 2024)
图 5 斜连杆−弹簧准零刚度隔振结构. (a)经典杆簧式准零刚度结构(Zhang et al. 2004), (b)连杆−弹簧式准零刚度结构(Wang et al. 2018 ), (c)滑杆−弹簧式准零刚度结构(Liu et al. 2020), (d)引入非线性惯容器连杆−弹簧式准零刚度结构(Liu et al. 2021), (e) X形混合杠杆式准零刚度结构(Liu et al. 2015), (f)非对称结构X形准零刚度结构(Liu et al. 2024)
图 6 凸轮−滚子准零刚度隔振结构. (a)凸轮−滚子准零刚度结构(Zhou et al. 2015), (b)轮廓可设计凸轮−滚子准零刚度结构(Yao et al. 2020), (c)抛物线型凸轮−滚子准零刚度结构(Zuo et al. 2024), (d)弹簧−连杆与凸轮−滚子混合式准零刚度结构(Sun et al. 2025), (e)自适应凸轮−滚子混合式准零刚度结构(Ye et al. 2020), (f)具有时滞立方位移反馈的凸轮−滚子准零刚度结构(Cheng et al. 2016)
图 7 屈曲梁/板/环式准零刚度隔振结构. (a)欧拉屈曲梁式准零刚度结构(Huang et al. 2014), (b)滑动屈曲梁式准零刚度结构(Huang et al. 2014), (c)余弦梁与半圆拱并联式准零刚度结构(Dalela et al. 2022), (d)屈曲失稳与弯曲变形式准零刚度结构(Liang et al. 2024), (e)整体式柔性曲梁准零刚度结构(Hou et al. 2024), (f)拓扑优化式准零刚度结构(Xu et al. 2024)
图 8 磁力准零刚度隔振结构. (a)磁环式准零刚度结构(Xu et al. 2013), (b)多磁块式准零刚度结构(Wu et al. 2014), (c)长方体磁铁阵列准零刚度结构(Wu et al. 2022), (d)高阶稳定特征的磁力型准零刚度结构(Liu et al. 2024), (e)杠杆式磁力准零刚度结构(Yan et al. 2022), (f)可调磁力式准零刚度结构(Liang et al. 2024)
图 9 仿生准零刚度隔振结构. (a)受鸟腿启发的X形准零刚度结构(Wang et al. 2019), (b)考虑非对称结构的X形准零刚度结构(Wu et al. 2015), (c)受鸟腿启发的大行程准零刚度结构(Sun et al. 2018), (d)仿蛙腿结构准零刚度结构(Zeng et al. 2021), (e) 仿多边形骨架准零刚度结构(Yan et al. 2020), (f) 仿生M形准零刚度结构(蓝春波 et al. 2025), (g)仿蟑螂结构的准零刚度结构(Ling et al. 2022), (h)仿海马外骨骼准零刚度结构(王尚文 et al. 2026)
图 10 折纸准零刚度隔振结构.(a) Kresling圆柱折纸结构准零刚度结构(Ishida et al. 2017), (b) Fluidic origami蜂窝结构准零刚度结构(Sadeghi et al. 2019), (c) Miura-origami tube构型准零刚度结构(Han et al. 2021), (d) Tachi-Miura折纸构型准零刚度结构(Liu et al. 2021), (e) Miura-origami构型准零刚度结构(Han et al. 2024), (f)基于桁架−弹簧的Miura-origami构型准零刚度结构(Ye et al. 2022)
图 11 单层扭转准零刚度隔振结构. (a)凸轮滚子扭转准零刚度结构(Zhou et al. 2015), (b)磁力扭转准零刚度结构(Zheng et al. 2018), (c) 基于连杆−弹簧扭转准零刚度结构(王晓杰 et al. 2018), (d)斜弹簧式扭转准零刚度结构(Kim et al. 2015), (e)柔性杆元件和电磁元件扭转准零刚度结构(Xu et al. 2024), (f)基于张拉一体化准零刚度结构(Sun et al. 2025), (g) 双拉伸弹簧式扭转准零刚度结构(Noh et al. 2025), (h)基于曲梁几何设计的扭转准零刚度结构(Hu et al. 2026)
图 13 多层准零刚度隔振结构. (a)双层准零刚度隔振结构经典动力学模型(Gatti et al. 2010), (b)屈曲结构的双层准零刚度结构(Lu et al. 2017), (c) 凸轮滚子结构双层准零刚度结构(Lu et al. 2017), (d)基于X形结构的多层准零刚度结构(Sun et al. 2016), (e) 特定几何构形的曲线梁准零刚度结构(Zhang et al. 2021), (f)基于柔性结构单元多层准零刚度结构 (Zhou et al. 2024)
图 14 多向准零刚度隔振结构. (a)面内多向准零刚度结构(Liu et al. 2021), (b)基于剪式连杆−弹簧的多向准零刚度结构(Sun et al. 2015), (c) 基于X形连杆结构的准零刚度结构(Chai et al. 2022), (d)多向悬浮式准零刚度结构(Qi et al. 2025), (e)磁力式六自由度准零刚度结构(Zhou et al. 2017), (f)可调磁力式准零刚度结构(Hao et al. 2022)
表 1 准零刚度隔振系统核心术语与释义
术语名称 定义 隔振系统中的特点 准零刚度
(quasi-zero stiffness, QZS)系统在静平衡位置附近总刚度趋近于零 (通常取非负值以保证稳定性) 的一种非线性刚度特性. 能在保证足够静承载力的前提下显著降低系统固有频率, 从而大幅拓宽低频隔振频带, 是实现低频/超低频隔振的核心机制. 高静低动刚度 (high-static-low-dynamic stiffness, HSLDS) 系统同时具备“静态时高刚度”和“动态时低刚度”两种特性. 静态高刚度用于支撑重载、抵抗静变形; 动态低刚度用于降低固有频率. 解决了传统线性隔振系统“承载能力”与“低频隔振效果”之间的矛盾, 常作为准零刚度隔振系统的等效力学特性描述, 在工程隔振设计中应用广泛. 负刚度
(negative stiffness)力−位移曲线的斜率为负值, 即系统偏离平衡位置时, 其所受恢复力的方向与位移方向相同 (而非相反), 使系统处于不稳定状态. 单独存在时系统会失稳, 但与正刚度并联后, 能相互抵消正刚度, 从而合成极低的总刚度 (QZS). 它是实现高静低动刚度的关键调控机制 传递率
(transmissibility, 通常用T表示)指系统在稳态受迫振动下, 响应幅值 (传递出去的力或位移/加速度) 与激励幅值 (输入的扰动力或基础运动幅值) 的无量纲比值. 它是评判隔振效果好坏的最直接指标. 当 T<1 时, 表示系统起到了隔振作用 (传递力小于扰动力); 当T=1 时对应的频率即为起始隔振频率; 当 T>1 时, 系统反而放大了振动 (共振区). 起始隔振频率
(starting frequency of vibration isolation)隔振系统传递率T=1 时所对应的激励频率. 当激励频率高于该频率时, 系统进入有效隔振区 (T<1 ). 起始频率越低, 系统的低频隔振性能越优. 该频率越低, 代表系统的低频隔振能力越强. 在准零刚度隔振系统中, 由于固有频率被压至极低, 起始隔振频率也相应向低频端大幅移动. 共振频率
(resonance frequency)指系统幅频响应曲线中振幅达到峰值时所对应的激励频率. 对于准零刚度隔振系统, 由于其刚度随振幅变化呈现非线性特征, 共振频率不再是固定值, 而是随激励幅值的变化而发生偏移. 隔振设计的核心目标之一是避免或有效抑制该频率处的振动. 实际工程中需确保工作频率远离共振频率, 并通过阻尼或非线性刚度设计来抑制该频率处的剧烈振动. 共振峰值
(resonance peak amplitude)系统在共振频率点处振动响应 (位移、速度或加速度) 的最大幅值. 峰值大小直接影响设备运行安全和结构疲劳寿命. 在准零刚度隔振系统中, 通常利用非线性刚度的“硬化”或“软化”效应, 或通过增加阻尼, 来降低或限制峰值, 从而有效抑制共振区的剧烈振动. 动超标. 传递率峰值
(peak transmissibility)指在系统共振频率附近, 传递率−频率曲线上所达到的最大值 峰值大小由系统的阻尼比和非线性刚度共同决定. 阻尼越大, 峰值越低 (抑制共振), 但高频隔振性能会变差 (传递率回升). 传递率下降率
(decreasing rate of transmissibility)传递率随频率升高而下降的斜率或速度. 通常以 dB/octave (分贝/倍频程) 或 dB/decade (分贝/十倍频程) 为单位进行量化. 衡量隔振系统高频衰减能力的关键指标. 下降率越大, 意味着高频振动被衰减得越快, 隔振效果越好 表 2 不同类型准零刚度隔振结构对比
隔振结构类型 优点 局限性 参考文献 斜弹簧准零
刚度机构结构简单、便于制造、参数调节灵活、可靠性高以及理论体系相对成熟 准零刚度区间较窄; 变承载质量或大幅激励时隔振性能下降; 弹簧与导向杆之间的摩擦在低频激励时可能导致隔振失效 (2007, 2021, 2016, 2014) 连杆−弹簧准零刚度机构 运动副精度高、负刚度可设计性强、准零刚度区间大、易于与其他机构集成 传统构型存在狭小低刚度区域和刚度渐硬非线性恢复力, 难以承受高振幅激励; 铰链间隙与摩擦影响精度与寿命 (2014, 2016, 2015, 2016, 2021) 凸轮−滚子准零刚度机构 可设计任意刚度曲线、摩擦损耗低、运动精度高、微幅振动敏感性强、动态响应迅速以及使用寿命长 典型构型存在较大摩擦阻尼; 准零刚度范围受凸轮尺寸限制; 圆形凸轮只能在很小范围内实现低刚度 (2020, 2016, 2017) 屈曲梁/板/环式准零刚度结构 结构紧凑、无活动关节、易于微型化与集成 对加工精度异常敏感; 高度依赖正负刚度的精确参数匹配; 负载适应性差; 转折处应力集中, 存在过早疲劳破坏问题 (2018, 2013,
2020, 2021)磁力准零刚
度机构无接触、无摩擦、响应速度快、刚度可电控调节、无机械疲劳、稳定性强 磁悬浮式结构存在大幅失稳风险; 强非线性导致系统易诱发突跳现象; 热稳定性问题 (2022, 2009, 2013, 2018, 2020, 2019) 仿生准零刚
度机构准零刚度区间大、结构轻量化、适应性强 结构复杂, 制造难度大; 部分构型承载力下降; 易出现刚度硬化和非线性跳跃导致系统失稳 (2021, 2015, 2018, 2018, 2019) 折纸准零刚
度机构可折叠、体积可变、刚度可调范围极大、形状可重构 准零刚度行程较短, 限制了在低频隔振领域的应用推广 (2017, 2021, 2021, 2024, 2025) 表 3 单层、多层与多向准零刚度隔振结构性能对比
比较维度 单层准零刚度隔振结构 多层准零刚度隔振结构 多向准零刚度隔振结构 核心目标 实现单向低频振动隔离, 结构简单、易于实现 提升高频衰减速率, 实现低频
高效隔振实现多自由度或多方向低频振动隔离, 适应复杂激励环境 典型构型 斜弹簧式、连杆−弹簧式、凸轮−滚子式、屈曲梁式、磁
力式、仿生式、折纸式双层/多层弹簧−质量系统、多层屈曲梁堆叠、多层磁力机构
串联、多层X形结构面内多向隔振器、三自由度解耦式、六自由度Stewart平台、Gough-Stewart构型 承载能力 由正刚度元件决定, 可通过弹簧刚度与几何参数设计调控, 可满足轻载至中载需求 由多层叠加结构共同承担, 分布式承载, 适用于重载工况 由空间对称布置的多个准零刚度单元共同支撑, 可实现大承载
(数百公斤至数吨)隔振频带 起始隔振频率低 (可至0.1 ~
5 Hz), 高频段传递率下降率
约为40 dB/decade起始隔振频率与与单层相当 (可低至0.1 ~ 5 Hz), 高频段传递率下降率可达80 dB/decade,
隔振效率显著提升各方向均可实现低频隔振 (起始频率6 ~ 10 Hz), 自由度间耦合
效应需通过构型设计解耦适用场景 基础隔振场景: 精密仪器支撑、车辆座椅悬架、设备隔振安装等 对隔振效率要求较高的场景: 舰船浮筏、航天器敏感载荷、
精密测量平台多源振动耦合场景: 航天器整星隔振、车载设备多维隔振、
船舶动力系统工程实现难度 较低. 构型成熟、元件标准,
便于加工与装配中等. 层间耦合参数匹配复杂,
需精密装配与调试高. 需多向准零刚度匹配与空间布局优化, 对设计、加工及装配精度要求极为苛刻 主要局限性 有效隔振频带相对较窄; 变载荷适应性差; 部分构型准零
刚度行程有限自由度增加引入额外共振峰, 需通过阻尼抑制; 结构复杂度与成本增加; 设计参数增多 构型复杂、体积较大; 多自由度非线性耦合效应难以完全消除; 成本高昂 -
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