再论压杆失稳与Lyapunov稳定性

进一步分析了弹性杆平衡的Euler稳定性和Lyapunov稳定性的概念和意义，指出了两的异同，表明不能用Euler稳定性的概念去理解弹性杆平衡的Lyapunov稳定性，并用例子予以说明。     

关于相平面法讨论压杆稳定性问题的答复

《力学与实践》2005年第2期发表的陈占清等“从非线性动力学视角认识细长压杆的稳定性”一文,中对笔者发表于2002年第4期的“压杆失稳与Liapunov稳定性”一文中用相平面法讨论压杆稳定性提出异议,对此作以下答复：     

压杆稳定性问题浅议

对于压杆稳定问题,很容易误认为,只有当轴向压力等于临界载荷及其若干整数倍时,杆件才有曲线平衡解,才会失稳;当轴向压力介于临界载荷整数倍之间时,杆件不存在曲线平衡解,不会失稳,这与实际情况不符。利用曲率的精确公式,探讨了造成这一问题的原因,说明了拉杆不会失稳的原因,描述了随着压力增大压杆挠曲线的变化情况。     

考虑压杆稳定性时二杆桁架的优化设计

从材料力学中一个简单桁架结构的优化设计问题入手,讨论了考虑压杆稳定时二杆桁架的优化设计问题.     

非圆截面弹性细杆的螺旋线平衡及稳定性

本文研究端部受力和力矩作用，且存在初曲率和初扭率的非圆截面弹性细杆的螺旋线平衡及其稳定性。描述弹性细杆平衡状态的Kirchhoff方程存在与杆的螺旋线平衡状态相对应的特解。直杆和圆环杆为螺旋线状态的两种特例。文中分析了螺旋线的几何特性与作用力和力矩之间的相互关系，并导出螺旋线平衡的一次近似解析形式稳定性判据。分析表明，松弛状态下弹性杆可处于螺旋线状态，直杆只有在轴向压力的作用下才能保持螺旋线平衡。无初曲率和初扭率弹性杆的螺旋线平衡稳定性必要条件是杆截面绕副法线轴的抗弯刚度大于或等于绕法线轴的抗弯刚度。此条件也适用于带初扭率的圆环杆及更普遍情形。无初曲率和初扭率的圆截面杆的螺旋线平衡恒稳定。     

含刚性段复合压杆的稳定性分析

压杆稳定性实验是材料力学中一个重要实验内容.然而,压杆稳定性实验中压杆两端的约束往往需要附加刚性的夹持件来实现.为了讨论压杆端部夹持件对测试结果的影响,本文基于弹性系统的稳定性理论,采用欧拉方法,分析了两端包含刚性段的复合压杆的稳定性,并通过数值求解讨论了刚性段不同占比情形下压杆的临界载荷.同时,采用有限元数值模拟方法...     

弹性细杆螺旋线平衡的动态稳定性

本文从动力学观点讨论具有初扭率的非圆截面弹性细杆的螺旋线平衡稳定性。弹性杆平衡的动态稳定性建立在以弧坐标s和时间坐标t为双自变量的离散系统的Lyapunov稳定性概念基础上。对于两端约束状况固定不变的弹性杆,若静态稳定性条件已满足,其与弧坐标对应的本征值可根据端部约束条件确定。则螺旋线平衡的动态稳定性由时间域的本征值判断。在缓慢受扰运动条件下,引入尺度缩小的时间变量T=εt,可将动力学过程视为对平衡状态的摄动。证明在ε^2计算精度范围内,当螺旋线平衡的一次近似静态稳定性条件得到满足时,考虑动力学因素的稳定性条件必也同时满足。     

细长压杆的失稳点及临界压力的确定方法研究

为了分析压杆失稳的临界力与失稳后杆件屈服形态的关系,在理论推导和试验研究的基础上,提出了通过捕捉细长压杆失稳时的失稳点来确定压杆临界力的分析方法,通过测量细长压杆失稳时微弯状态下杆端的纵向位移,求得临界压力的大小. 文中将该方法的实验结果与直接用欧拉公式计算的临界压力进行了比较,结果表明,考虑细长压杆微弯状态时杆端的纵向位移所得到的失稳的临界压力值大于利用欧拉公式计算的临界压力值.     

大柔度型钢压杆的稳定性设计计算公式

对大柔度型钢压杆稳定性设计,本文导出一个简便计算公式,从而能够直接选定型钢型号....     

压杆的动态稳定性

在动力学范畴内讨论压杆稳定性问题. 证明压杆的一次近似动态Lyapunov稳定性要求静态Lyapunov稳定性与欧拉稳定性条件同时得到满足.     

Buckling of a twisted and compressed rod

We consider the problem of determining the stability boundary for an elastic rod under thrust and torsion. The constitutive equations of the rod are such that both shear of the cross-section and compressibility of the rod axis are considered. The stability boundary is determined from the bifurcation points of a single nonlinear second order differential equation that is obtained by using the first integrals of the equilibrium equations. The type of bifurcation is determined for parameter values. It is shown that the bifurcating branch is the branch with minimal energy. Finally, by using the first integral, the solution for one specific dependent variable is expressed in terms of elliptic integrals. The solution pertaining to the complete set of equilibrium equations is obtained by numerical integration.     

Buckling of an elastoplastic bar

Buckling of a bar of an elastoplastic material is studied. It is shown that for any (σ-?) diagram of the bar material, the limit load (the longitudinal external force) in dimensionless variables that the bar can withstand does not exceed the current bending stiffness of the most loaded (in terms of the bending moment) section.     

Buckling of a bar on an elastic base

Novosibirsk. Translated from Prikladnaya Mekhanika i Tekhnicheskaya Fizika, No. 5, pp. 106–112, September–October, 1994.     

Buckling of a twisted and compressed rod supported by Cardan joints

We consider the problem of determining the stability boundary of an elastic rod supported by Cardan joints at both ends. The rod is loaded by a compressive force and a couple. The constitutive equations of the rod take into account the compressibility of the rod axis. The stability boundary is determined by the bifurcation points of a system of eight nonlinear first order differential equations obtained by using suitable dependent variables. The type of bifurcation is examined depending on the compressibility. By numerical integration of a system of ten nonlinear first order differential equations the post-critical shape of the rod is determined.     

Buckling modes of a compressed plate on an elastic substrate

The buckling modes of a homogeneously compressed elastic plate on a soft elastic substrate are studied. The critical compression is uniquely determined by the bifurcation equation, but this compression is associated with a wide set of buckling modes. It was proved that any solution of the Helmholtz equation satisfies the bifurcation equation. At the same time, in microelectronics, it is required to know which buckling mode is realized. Experimental and theoretical investigations show that the chessboard-like buckling mode should be expected. In what follows, this problem is discussed theoretically. The expected buckling mode can be found by analyzing the energy of the initial postcritical deformation, and the desired mode is determined from the condition of its minimum. The analytic expression of this energy is obtained. Its minimization results in the chessboard-like buckling mode.