简支饱和多孔弹性梁的非线性弯曲

基于饱和多孔介质理论和弹性梁的大挠度弯曲假设,在多孔弹性梁轴线不可伸长,孔隙流体仅沿轴向方向扩散的限制下,建立了微观不可压饱和多孔弹性梁大挠度拟静态响应的一维非线性数学模型.在此基础上,利用Galerkin截断法,分析了两端可渗透的简支多孔弹性梁在突加横向均布载荷作用下的非线性弯曲,给出了梁弯曲时挠度、弯矩以及孔隙流体压力等效力偶随时间的响应曲线.数值结果表明:当载荷较小时,大挠度非线性与小挠度线性理论的结果相差很小,而当载荷较大时,非线性大挠度理论的结果小于相应线性小挠度理论的结果,并且这种差异随着载荷的增大而增大.同时,在载荷突加于梁上时,多孔弹性梁骨架起初不变形,孔隙流体压力等效力偶由零突增为非零,其值与外载荷保持平衡.随着时间的增加,梁的挠度增加,等效力偶逐渐减小为零,最终多孔梁骨架承担全部的外载荷.     

均布力偶作用下细长梁力学分析

通过铁木辛柯梁理论分析了反向均布表面剪应力——等效均匀分布力偶作用下的等截面均质细长梁挠度和应力分布规律,并与有限元法的计算结果对比发现：当边界条件中剪力不为零时,弯曲挠度和正应力分析必须考虑剪力的影响,即Euler梁理论不能满足分析的要求;若存在剪力为零边界时,可使用Euler梁分析弯曲挠度和正应力;剪应力分布向通常规律一样,仍沿高度方向呈抛物线分布,即使对于剪力为零的横截面也可能存在剪应力,这是由于表面剪应力的影响使得梁的上下表面存在剪应力,并且剪应力在横截面内正负可以发生变化。     

简支饱和多孔弹性梁的非线性动力响应

基于饱和多孔弹性梁大挠度变形的数学模型,利用Galerkin截断法,本文研究了两端可渗透的简支饱和多孔弹性梁分别在突加横向均布常载荷和简谐载荷作用下的动力响应,得到了梁弯曲时挠度、弯矩以及孔隙流体压力等效力偶等随时间的响应,考察了不同载荷下多孔弹性梁弯曲的响应特征.结果表明:随着载荷的增加,在常载荷作用下多孔弹性梁非线性大挠度响应与线性小挠度的差别愈加明显,而在简谐载荷作用下,多孔弹性梁的动力响应呈现较丰富的性态,相图由最初的单一椭圆曲线不断变形,形状随载荷幅值的增加而逐渐复杂,同时,时程曲线也由简单正弦曲线变为具有多峰值特征的一个周期曲线.     

饱和多孔弹性Timoshenko梁的大挠度分析

基于微观不可压饱和多孔介质理论和弹性梁的大挠度变形假设,考虑梁剪切变形效应,在梁轴线不可伸长和孔隙流体仅沿轴向扩散的限定下,建立了饱和多孔弹性Timoshenko梁大挠度弯曲变形的非线性数学模型.在此基础上,利用Galerkin截断法,研究了两端可渗透简支饱和多孔Timoshenko梁在突加均布横向载荷作用下的拟静态弯曲,给出了饱和多孔 Timoshenko梁弯曲变形时固相挠度、弯矩和孔隙流体压力等效力偶等随时间的响应.比较了饱和多孔Timoshenko梁非线性大挠度和线性小挠度理论以及饱和多孔 Euler-Bernoulli梁非线性大挠度理论的结果,揭示了他们间的差异,指出当无量纲载荷参数q＞l0时,应采用饱和多孔Timoshenko梁或Euler-Bernoulli梁的大挠度数学模型进行分析,特别的,当梁长细比λ＜30时,应采用饱和多孔Timoshenko梁大挠度数学模型进行分析.     

轴向扩散下简支饱和多孔弹性梁的大挠度分析

基于多孔介质理论和弹性梁的大挠度理论,并考虑轴向变形,在孔隙流体仅沿轴向扩散的假设下,建立了微观不可压饱和多孔弹性梁大挠度弯曲变形的一维非线性数学模型.在此基础上,忽略饱和多孔弹性梁的轴向应变,并利用Galerkin截断法,研究了两端可渗透的简支饱和多孔弹性梁在突加横向均布载荷作用下的拟静态弯曲,给出了饱和多孔梁弯曲时挠度、弯矩和轴力以及孔隙流体压力等效力偶等沿轴线的分布曲线.揭示了大挠度非线性和小挠度线性模型的结果差异,指出大挠度非线性模型的结果小于相应小挠度线性模型的结果,并且这种差异随着载荷的增大而增大.计算表明:当无量纲载荷参数q>5时,应该采用大挠度非线性数学模型进行研究.     

从一个怪例看细长梁理论的基本假定

分别采用欧拉和铁木辛柯梁理论分析了均匀分布力偶作用下的两端固支等截面匀质细长 梁, 并通过ABAQUS有限元分析了一个实例, 验证了铁木辛柯梁理论分析的结果. 对比证明在 这种载荷及边界条件下即使细长梁, 也必须考虑剪切效应的影响.     

不可压饱和多孔弹性简支梁的动力响应

在杆件弯曲小变形的假定下,考虑杆件的侧向变形因素,根据多孔介质理论,本文首先建立了不可压饱和多孔弹性梁弯曲变形时动力响应的控制方程。其次,基于所建立的控制微分方程,利用变量分离法,研究了两端可渗透的饱和多孔弹性简支梁在梁中间集中载荷作用下的动力响应,得到了不同物性参数下简支梁动态弯曲时挠度和孔隙流体压力等效力偶等随时间的响应曲线。研究发现由于孔隙流体和固相骨架的相互作用,不可压饱和多孔弹性梁挠度的动力响应具有粘性特征,同时,随着时间的增加,饱和多孔弹性梁的挠度、弯矩等最终趋于经典弹性梁的静挠度、弯矩,此时,孔隙流体压力为零,梁的固相骨架承担所有的外载荷。     

基于等效弹簧模型的裂纹Euler-Bernoulli梁弯曲变形分析

考虑裂纹的缝隙效应,研究了开闭裂纹Euler-Bernoulli梁的弯曲变形．首先,将裂纹等效为内部旋转弹簧,利用广义函数,给出了考虑裂纹缝隙影响的Euler-Bernoulli梁的等效抗弯刚度,推导了具有任意数目开闭裂纹梁弯曲变形的显式通解．在此基础上,研究了均布载荷作用下上侧单裂纹简支梁以及裂纹处承受集中力和集中力偶共同作用的固支梁的弯曲变形,分析了梁长细比、裂纹深度和位置以及载荷等对裂纹开闭状态和梁弯曲变形的影响。结果表明：梁挠度分布在裂纹处存在尖点,而转角分布存在跳跃;梁挠度与载荷的响应关系一般为双折线形式,分别对应于裂纹的张开和闭合状态;且裂纹张开时,裂纹梁的柔度随着梁长细比的增加和裂纹深度的减小而减小。这些结果对梁裂纹无损检测具有指导意义．     

基于均布荷载挠度曲率的梁结构损伤识别方法

为运用荷载挠度曲线进行损伤识别,通过力法推导了梁结构在均布荷载作用下的挠度曲率理论公式,提出通过损伤前后的挠度曲率差进行损伤定位,针对多跨连续梁均布荷载下挠度曲率指标存在的损伤识别漏判问题,提出逐跨均布荷载挠度曲率指标以避免其影响,并建立了挠度曲率与损伤程度的理论关系式,可对损伤程度进行较精确的定量描述．通过一简支梁和一三跨连续梁算例,考虑多种损伤工况,分析了指标在不同程度噪声水平下的抗干扰能力,验证了挠度曲率损伤指标应用于实际的可行性．     

不可压饱和多孔弹性梁、杆动力响应的数学模型

基于多孔介质理论,首先建立了饱和多孔弹性杆件弯曲与轴向变形时动力响应的数学模型.其次,基于多孔弹性梁弯曲变形的数学模型,利用Laplace变换,分析了两端可渗透的饱和多孔弹性悬臂梁在自由端受阶梯载荷作用下的动静力响应,给出了梁弯曲时挠度、弯矩以及孔隙流体压力等效力偶等物理量随时间的响应曲线.发现不可压多孔弹性梁的拟静态响应亦存在Mandel-Cryer现象,多孔弹性梁的挠度具有与粘弹性梁挠度类似的蠕变特征,然而,其应力响应不同于粘弹性梁,随着时间的增加,梁拟静态响应的弯矩逐渐增加,并达到一个稳态值.这些结果有助于揭示植物根茎等力学行为的机理.     

超静定梁?柱的解析解研究

本文采用渐进积分法研究了超静定梁?柱的弯曲问题. 首先建立超静定梁?柱的四阶挠度微分方程, 考虑到边界条件和连续光滑条件, 采用连续分段独立一体化积分法求解得到了挠度的精确解析解. 为了满足工程设计需要, 构造了超静定梁?柱的四阶挠度微分迭代方程, 选取无轴向力作用时超静定梁的挠曲线作为梁的初函数, 将初函数代入梁的四阶挠度微分迭代方程进行积分, 利用边界条件和连续光滑条件确定积分常数, 得到下一次迭代挠度函数, 依次进行迭代积分运算. 计算出了最大挠度、最大转角和最大弯矩等用轴向力放大系数表示的多项式解析函数解. 本文选取了两种边界条件下受分布力作用的超静定梁?柱进行分析, 计算结果表明, 当超静定梁?柱所受的轴向力小于欧拉临界力的1/2时, 迭代六次误差就可以控制在1%以内; 不仅梁?柱最大位移和最大内力的大小随轴向力的增大而增大, 而且其位置也随轴向力的增大而发生迁移. 本文的研究对揭示轴向力对超静定梁?柱变形和内力的影响有重要意义, 为超静定梁?柱的实际设计提供了一定的理论基础.      

A micro scale Timoshenko beam model based on strain gradient elasticity theory

A micro scale Timoshenko beam model is developed based on strain gradient elasticity theory. Governing equations, initial conditions and boundary conditions are derived simultaneously by using Hamilton's principle. The new model incorporated with Poisson effect contains three material length scale parameters and can consequently capture the size effect. This model can degenerate into the modified couple stress Timoshenko beam model or even the classical Timoshenko beam model if two or all material length scale parameters are taken to be zero respectively. In addition, the newly developed model recovers the micro scale Bernoulli–Euler beam model when shear deformation is ignored. To illustrate the new model, the static bending and free vibration problems of a simply supported micro scale Timoshenko beam are solved respectively. Numerical results reveal that the differences in the deflection, rotation and natural frequency predicted by the present model and the other two reduced Timoshenko models are large as the beam thickness is comparable to the material length scale parameter. These differences, however, are decreasing or even diminishing with the increase of the beam thickness. In addition, Poisson effect on the beam deflection, rotation and natural frequency possesses an interesting “extreme point” phenomenon, which is quite different from that predicted by the classical Timoshenko beam model.     

A size-dependent Reddy–Levinson beam model based on a strain gradient elasticity theory

A size-dependent Reddy–Levinson beam model is developed based on a strain gradient elasticity theory. Governing equations and boundary conditions are derived by using Hamilton’s principle. The model contains three material length scale parameters, which may effectively capture the size effect in micron or sub-micron. This model can degenerate into the modified couple stress model or even the classical model if two or all material length scale parameters are taken to be zero respectively. In addition, the present model recovers the micro scale Timoshenko and Bernoulli–Euler beam models based on the same strain gradient elasticity theory. To illustrate the new model, the static bending and free vibration problems of a simply supported micro scale Reddy–Levinson beam are solved respectively; the results are compared with the reduced models. Numerical results reveal that the differences in the deflection, rotation and natural frequency predicted by the present model and the other two reduced Reddy–Levinson models are getting larger as the beam thickness is comparable to the material length scale parameters. These differences, however, are decreasing or even diminishing with the increase of the beam thickness. This study may be helpful to characterize the mechanical properties of small scale beam-like structures for a wide range of potential applications.     

Surface and non-local effects for non-linear analysis of Timoshenko beams

In this paper, we present a non-local non-linear finite element formulation for the Timoshenko beam theory. The proposed formulation also takes into consideration the surface stress effects. Eringen׳s non-local differential model has been used to rewrite the non-local stress resultants in terms of non-local displacements. Geometric non-linearities are taken into account by using the Green–Lagrange strain tensor. A C⁰ beam element with three degrees of freedom has been developed. Numerical solutions are obtained by performing a non-linear analysis for bending and free vibration cases. Simply supported and clamped boundary conditions have been considered in the numerical examples. A parametric study has been performed to understand the effect of non-local parameter and surface stresses on deflection and vibration characteristics of the beam. The solutions are compared with the analytical solutions available in the literature. It has been shown that non-local effect does not exist in the nano-cantilever beam (Euler–Bernoulli beam) subjected to concentrated load at the end. However, there is a significant effect of non-local parameter on deflections for other load cases such as uniformly distributed load and sinusoidally distributed load (Cheng et al. (2015) [10]). In this work it has been shown that for a cantilever beam with concentrated load at free end, there is definitely a dependency on non-local parameter when Timoshenko beam theory is used. Also the effect of local and non-local boundary conditions has been demonstrated in this example. The example has also been worked out for other loading cases such as uniformly distributed force and sinusoidally varying force. The effect of the local or non-local boundary conditions on the end deflection in all these cases has also been brought out.     

Euler–Bernoulli beams with multiple singularities in the flexural stiffness

Euler–Bernoulli beams under static loads in presence of discontinuities in the curvature and in the slope functions are the object of this study. Both types of discontinuities are modelled as singularities, superimposed to a uniform flexural stiffness, by making use of distributions such as unit step and Dirac's delta functions. A non-trivial generalisation to multiple different singularities of an integration procedure recently proposed by the authors for a single singularity is presented in this paper. The proposed integration procedure leads to closed form solutions, dependent on boundary conditions only, which do not require enforcement of continuity conditions along the beam span. It is however shown how, from the solution of the clamped-clamped beam, by considering suitable singularities at boundaries in the flexural stiffness model, responses concerning several boundary conditions can be recovered. Furthermore, solutions in terms of deflection of the beam are obtained for imposed displacements at boundaries providing the so called shape functions. The above mentioned shape functions can be adopted to insert beams with singularities as frame elements in a finite element discretisation of a frame structure. Explicit expressions of the element stiffness matrix are provided for beam elements with multiple singularities and the reduction of degrees of freedom with respect to classical finite element procedures is shown. Extension of the proposed procedure to beams with axial displacement and vertical deflection discontinuities is also presented.     

Vibration of beams with general boundary conditions due to a moving random load

Summary  The transverse vibrations of elastic homogeneous isotropic beams with general boundary conditions due to a moving random force with constant mean value are analyzed. The boundary conditions considered are: pinned–pinned, fixed–fixed, pinned–fixed, and fixed–free. Based on the Bernoulli beam theory, the problem is described by means of a partial differential equation. Closed-form solutions for the variance and the coefficient of variation of the beam deflection are obtained and compared for three types of force motion: accelerated, decelerated and uniform. The effects of beam damping and speed of the moving force on the dynamic response of beams are studied in detail. Received 3 December 2001; accepted for publication 30 April 2002     

Analysis of micropolar elastic beams

In this paper, a linear theory for the analysis of beams based on the micropolar continuum mechanics is developed. Power series expansions for the axial displacement and micro-rotation fields are assumed. The governing equations are derived by integrating the momentum and moment of momentum equations in the micropolar continuum theory. Body couples and couple stresses can be supported in this theory. After some simplifications, this theory can be reduced to the well-known Timoshenko and Euler–Bernoulli beam theories. The nature of flexural and longitudinal waves in the infinite length micropolar beam has been investigated. This theory predicts the existence of micro-rotational waves which are not present in any of the known beam theories based on the classical continuum mechanics. Also, the deformation of a cantilever beam with transverse concentrated tip loading has been studied. The pattern of deflection of the beam is similar to the classical beam theories, but couple stress and micro-rotation show an oscillatory behavior along the beam for various loadings.