薛纭
* , 2) , 陈立群
, ? , 3) *
上海应用技术大学 机械工程学院,上海201418 ?
哈尔滨工业大学(深圳) 理学院力学系, 深圳 518055 GENERALIZATION OF KIRCHHOFF KINETIC ANALOGY TO THIN ELASTIC SHELLS 1) Xue Yun
* , 2) , Chen Liqun
, ? , 3) *
School of Mechanical Engineering, Shanghai Institute of Technology, Shanghai 201418, China ?
School of Science, Harbin Institute of Technology, Shenzhen 518055, China 通讯作者: 3)陈立群, 教授, 主要研究方向: 非线性动力学和振动控制. E-mail:
chenliqun@hit.edu.cn 收稿日期: 2020-08-2
接受日期: 2020-10-15
网络出版日期: 2020-12-31
基金资助: 1)国家自然科学基金资助项目 .11872159 国家自然科学基金资助项目 .11372195
Received: 2020-08-2
Accepted: 2020-10-15
Online: 2020-12-31
作者简介 About authors
2)薛纭,教授.主要研究方向:分析力学,弹性细杆力学和弹性薄壳力学等.E-mail:
xy@sit.edu.cn 摘要 将弹性细杆的"Kirchhoff动力学比拟"方法推广到弹性薄壳,使弹性薄壳的变形在物理概念上和刚体的运动对应, 在数学表述上等同,从而可以用刚体动力学的理论和方法研究弹性薄壳的变形,为连续的弹性薄壳提供新的离散化方法. 在直法线假设下,在弹性中面上构筑空间正交轴系, 此轴系沿坐标线"运动"的角速度构成两自变量的弯扭度. 沿两个坐标线的弯扭度表达了弹性薄壳的变形和位形,证明了弯扭度之间以及弯扭度与中面切矢间的相容关系. 用Euler角和Lam$\acute{e}$系数表达了非完整约束和中面位形的微分方程,用弯扭度和Lam$\acute{e}$系数表达了应变和应力以及内力及其本构方程.导出了用分布内力集度表达的弹性薄壳在变形后位形上的平衡偏微分方程组,方程的形式与刚体动力学的Euler方程和弹性细杆的Kirchhoff方程具有相似性,实现了Kirchhoff动力学比拟对弹性薄壳的推广.总结了弹性薄壳静力学和刚体动力学以及弹性细杆静力学在概念上的比拟关系.最后给出了一个算例. 为研究弹性薄壳的变形和运动提供新的建模方法和研究思路.也可进一步推广到弹性薄壳动力学.
关键词： Kirchhoff动力学比拟 ;
弹性薄壳静力学 ;
刚体动力学 ;
弯扭度 Abstract The Kirchhoff kinetic analogy is generalized from thin elastic rods to thin elastic shells. The generalization makes thin shell deformations physically correspond and mathematically equivalent to rigid body motions. Hence theories and methods of rigid body dynamics can be applied to investigate deformations of thin elastic shell, and also provide a novel discretization for continuous thin elastic shells. An orthogonal spatial axis system is established along the coordinate lines of the middle surface under the straight normal assumption. The moving of the axis system along the coordinate lines in unit velocity forms its "angular velocity", which is the curvature-twist vector with two independent variables. The curvature-twist vector along two coordinate lines expresses the deformation and the configuration of a thin elastic shell. It is demonstrated that curvature-twist vectors are compatible, and curvature-twist vectors and tangential vectors of middle surface are compatible. Nonholonomic constraints and differential equations of middle surfaces are established in the Euler angles and the Lam$\acute{e}$ coefficient form. The strain, the stress and the internal forces are formulated in the curvature-twist vectors and the Lam$\acute{e}$ coefficients. The equilibrium partial differential equations are presented with distributed internal forces intensity of thin elastic shells. The forms of the equations are similar to the Euler equations of rigid body dynamics and Kirchhoff equations of thin elastic rods. The fact means that the Kirchhoff kinetic analogy of thin elastic rods is generalized to thin elastic shells. The analogy relations between thin elastic shells and dynamics of rigid body or thin elastic rods are concluded. Finally, an example is given to show the application of this method. The proposed analogy leads to novel views and approaches to model and to analyze deformation of thin elastic shells. It is possible to generalize further the analogy for dynamics of thin elastic shells.
Keywords： Kirchhoff kinetic analogy ;
statics of thin elastic shell ;
rigid body dynamics ;
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Bibtex 收藏本文 本文引用格式 薛纭, 陈立群. Kirchhoff动力学比拟对弹性薄壳的推广
1) .
力学学报 [J], 2020, 53(1): 234-247 DOI:
10.6052/0459-1879-20-266 Xue Yun, Chen Liqun.
GENERALIZATION OF KIRCHHOFF KINETIC ANALOGY TO THIN ELASTIC SHELLS 1) .
Chinese Journal of Theoretical and Applied Mechanics [J], 2020, 53(1): 234-247 DOI:
10.6052/0459-1879-20-266 引言 弹性细杆的平衡与刚体的定点转动是两类完全不同的经典力学问题. 1859年Kirchhoff等
[1 -2 ] 在平面截面假定下建立的弹性细杆静力学理论,依据其平衡的Kirchhoff方程与刚体动力学的Euler方程在数学形式上的相似性,提出了Kirchhoff动力学比拟方法.1927年, Love
[3 ] 在其弹性力学著作中详细叙述Kirchhoff理论,明确了两者在物理概念上的对应和在数学表达上的等同关系. 对此,刘延柱
[4 ] 作了更明确的叙述, 如中心线弧长坐标-时间;截面的姿态-定点转动刚体的姿态;截面的弯扭度-刚体的角速度;截面的抗弯抗扭刚度- 刚体对主轴的转动惯量等.
促使弹性细杆力学近代发展的是分子生物学.作为脱氧核糖核酸(DNA)双螺旋结构的力学模型,弹性细杆的Kirchhoff动力学比拟方法成为描述DNA双螺旋复杂位形的有力工具
[5 ] .Coleman和Swigon
[6 ] 于2004年由Kirchhoff方程得到有结和无结质粒超螺旋的精确解. 从力学的角度看,动力学比拟也为连续弹性细杆提供新的离散化方法, 从而成为3自由度系统,弹性细杆的位形是截面沿中心线的弧坐标历程. 位形、曲率和挠率等几何概念都可用弯扭度和Euler角表达
[4 ] ,开辟了用刚体动力学的理论和方法研究弹性细杆静力学的新思路,成为求解弹性细杆小应变大位移问题的有效方法.同时还极大地丰富了弹性细杆力学理论. 分析力学方法
[7 ] 、非完整约束
[8 -9 ] 、对称性和守恒量
[10 ] 、Lyapunov稳定性
[11 ] ,甚至混沌
[12 ] 等动力学概念和理论都可移植或应用到弹性细杆静力学,并赋予新的含义.同时Kirchhoff动力学比拟也为刚体动力学的运动历程提供几何直观图像.
弹性细杆中心线的二维扩展形成弹性薄壳的中面.自然希望将弹性细杆的Kirchhoff动力学比拟方法推广到弹性薄壳.
随着工程技术的发展,大型柔性航天器动力学和多柔体系统动力学应用日益广泛
[13 ] . 文献[
14 ]简要回顾了多柔体系统动力学建模的3类方法:浮动坐标方法、几何精确方法和绝对节点坐标方法. 对于大变形柔性梁,文献[
15 ]在浮动坐标系下使用柔性梁参数方程形式的精确曲率公式来计算柔性梁的弯曲变形能,建立了基于浮动坐标系的考虑曲率纵向变形效应的刚耦合动力学模型.
对于几何非线性问题的建模与数值计算的主要方法有初应力法
[16 ] 、几何大变形约束法
[17 ] 、大变形耦合方法等
[18 ] .
在大变形情况下, 文献[
19 ]提出了用绝对节点坐标法建模,解决了用混合坐标法建模计算效率较低的问题,文献[
20 ]进一步用大变形实验验证了绝对节点坐标法的正确性.文献[
21 ]不使用微分几何中的矩阵及其退化概念,在弹性中面的原始位形和当前位形之外, 定义了平面参考位形,在这3个位形上定义正交坐标系,通过映射表达他们间的关系.用Cartesian坐标表达应变.
文献[
22 ]指出, "显然, 研究薄壳大变形大位移比研究刚体的一般空间运动更复杂,后者的自由度为6, 而对可变形物体却有无穷多个自由度. "将Kirchhoff动力学比拟方法应用到弹性薄壳, 有望将弹性薄壳化作离散力学系统,从而经典动力学理论和方法可以用到弹性薄壳力学,为弹性薄壳静力学注入新的概念和方法.
经典的弹性细杆和弹性薄壳的现代研究在对象, 以及研究内容和研究方法上都赋予了全新的内涵
[23 ] . 将弹性细杆Kirchhoff动力学比拟的思想, 推广到弹性薄壳是很有意义的工作. 在弹性中面上建立正交轴系并定义姿态坐标和弯扭度. 用Lam$\acute{e}$系数、弯扭度和姿态坐标表达中面偏微分方程、一点的应变和应力状态、截面的内力,以及平衡方程等. 此外, 弯扭度和Lam$\acute{e}$系数还可表达曲面微分几何的基本概念和公式, 这将另文讨论.
本文在直法线假设下
[24 -26 ] , 基于Kirchhoff动力学比拟方法和刚体动力学的观念,用Euler角、弯扭度和Lam$\acute{e}$系数讨论弹性薄壳的静力学建模.
文中指标取值$i,j=1,2;k=1,2,3$.
1 弹性薄壳中面的轴系 设$O-\xi \eta \zeta $为惯性参照系, 沿坐标轴方向的单位基矢量为${e}_{\xi}, {e}_{\eta }, {e}_{\zeta}$. 变形前弹性中面上的任意点$p$变形后为 $P$, 中面方程分别为
(1) $\begin{eqnarray} {r=r}\left( {q_{1} ,q_{2} } \right), \\ {R=R}\left( {q_{1} ,q_{2} } \right) \end{eqnarray}$其中$q_{1} ,q_{2} $为广义弧坐标. 设${r}$和${R}$具有所需要的各阶连续偏导数
(2) $\begin{eqnarray} \label{eq2} \overrightarrow{pP} ={u}={R}-{r} \end{eqnarray}$为位移函数, 如
图1 所示.
图1 新窗口打开 |
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生成PPT 图1变形前和变形后中面上点的矢径和位移矢量 Fig.1The position vector and displacement vector of the point on the mid-surface before and after deformation 变形后中面上沿坐标线的切矢量、单位切矢量和弧长微分依次为
(3) $\begin{eqnarray} {T}_{i} =\dfrac{\partial {R}}{\partial q_{i} }, \\ {T}_{i}^{0} =\dfrac{{T}_{i} }{T_{i} }, \\ {d}S_{i} =T_{i} {d}q_{i} \end{eqnarray}$其中Lam$\acute{e}$系数$T_{i} =\left| {{T}_{i} } \right|$. 在中面上一点$P$建立两个轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0}} \right)$,
其中
(4) $\begin{eqnarray} \label{eq4} {N}^{0}=\dfrac{{T}_{1}^{0} \times {T}_{2}^{0} }{\sin \phi }, \\ {B}_{i}^{0} ={N}^{0}\times {T}_{i}^{0} \end{eqnarray}$式中, ${N}^{0}$为变形后中面的单位法矢量, $\sin \phi =\left| {{T}_{1}^{0} \times {T}_{2}^{0} } \right|$, 物理上要求$\left| {{T}_{1}^{0} \times {T}_{2}^{0} } \right|\ne 0$, 如
图2 所示. 文献上称$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0}} \right)$为点$P$的轴系,或Cosserat方向子或活动标架. ${B}_{i}^{0} $可以用${T}_{1}^{0} ,{T}_{2}^{0} $线性表为
(5) $\begin{eqnarray} \label{eq5} \left.\begin{array}{l} {B}_{1}^{0} =-\cot \phi {T}_{1}^{0} +\dfrac{1}{\sin \phi }{ T}_{2}^{0} \\ {B}_{2}^{0} =-\dfrac{1}{\sin \phi }{T}_{1}^{0} +\cot \phi { T}_{2}^{0} \\ \end{array}\right\} \end{eqnarray}$图2 新窗口打开 |
下载原图ZIP |
生成PPT 图2弹性中面上两轴系的相对位置 Fig.2The position relation between two frames on the elastic mid-surface 对中面的任意曲线$q_{i} =q_{i} \left( q \right)$的单位切矢量
(6) $\begin{eqnarray} \label{eq6} {T}_{q}^{0} ={T}_{1}^{0} \cos \alpha +{B}_{1}^{0} \sin \alpha \end{eqnarray}$和其$q$坐标线的弧长微分${d}S$, 将式(5)第1式代入式(6), 化作
(7) $\begin{eqnarray} \label{eq7} {T}_{q}^{0} =\dfrac{\sin \left( {\phi -\alpha } \right)}{\sin \phi }{ T}_{1}^{0} +\dfrac{\sin \alpha }{\sin \phi }{T}_{2}^{0} \end{eqnarray}$得到其弧长微分关系为
(8) $\begin{eqnarray} \label{eq8} {d}S_{1} =\dfrac{\sin \left( {\phi -\alpha } \right)}{\sin \phi }{d}S, \\ {d}S_{2} =\dfrac{\sin \alpha }{\sin \phi }{d}S \end{eqnarray}$当$\alpha ={\pi}/{2}$时, 得到以${T}_{1}^{0},{T}_{2}^{0},{B}_{1}^{0} $为切线方向的弧长微分之间的关系
(9) $\begin{eqnarray} \label{eq9} {d}S_{1} =-\cot \phi {d}S_{3} , \\ {d}S_{2} =\dfrac{1}{\sin \phi }{d}S_{3} \end{eqnarray}$其中${d}S_{3} $是${B}_{1}^{0} $方向的弧长微分.
两个轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0}}
\right)$存在如下关系
(10) $\begin{eqnarray} \label{eq10} \left( {{\begin{array}{*{20}c} {{T}_{2}^{0} } \hfill \\ {{B}_{2}^{0} } \hfill \\ {{N}^{0}} \hfill \\ \end{array} }} \right)={\varPhi }\left( {{\begin{array}{*{20}c} {{T}_{1}^{0} } \hfill \\ {{B}_{1}^{0} } \hfill \\ {{N}^{0}} \hfill \\ \end{array} }} \right), \\ {\varPhi }=\left( {{\begin{array}{*{20}c} {\cos \phi } \hfill & {\sin \phi } \hfill & 0 \hfill \\ {-\sin \phi } \hfill & {\cos \phi } \hfill & 0 \hfill \\ 0 \hfill & 0 \hfill & 1 \hfill \\ \end{array} }} \right) \end{eqnarray}$同理, 上述概念可以在变形前的弹性中面上定义, 并用下标0表示
(11) $\begin{eqnarray} \label{eq11} &&{T}_{i0} =\dfrac{\partial {r}}{\partial q_{i} },T_{i0} =\left| {{T}_{i0} } \right|,{T}_{i0}^{0} =\dfrac{{T}_{i0} }{T_{i0} },{d}s_{i} =T_{i0} {d}q_{i} \end{eqnarray}$(12) $\begin{eqnarray} {N}_{0} =\dfrac{{T}_{10}^{0} \times {T}_{20}^{0} }{\sin \phi_{0} },\\ {B}_{i0}^{0} ={N}_{0} \times {T}_{i0}^{0} \end{eqnarray}$(13) $\begin{eqnarray} \left.\begin{array}{l} {B}_{10}^{0} =-\cot \phi_{0} {T}_{10}^{0} +\dfrac{1}{\sin \phi_{0} }{T}_{20}^{0} \\ {B}_{20}^{0} =-{T}_{10}^{0} \sin \phi_{0} +{B}_{10}^{0} \cos \phi_{0} \\ \end{array}\right\} \end{eqnarray}$式中${d}s_{i} $为变形前中面坐标线的弧长微分.
2 弹性薄壳的弯扭度及其相容方程 2.1 弯扭度的定义 用轴系$(T_{i}^{0},{B}_{i}^{0}, {N}^{0})$表达变形后中面的弯扭度
[4 ,27 ] . 记${e}_{i1} ={T}_{i}^{0} ,{e}_{i2} ={B}_{i}^{0} , {e}_{i3} ={N}^{0}$. 轴系沿坐标线$q_{j} $的弯扭度${\omega }_{ij} $定义为
(14) $\begin{eqnarray} \label{eq14} \dfrac{\partial {e}_{ik} }{\partial q_{j} }={\omega }_{ij} \times {e}_{ik} \end{eqnarray}$或
(15) $\begin{eqnarray} \label{eq15} {\omega }_{ij} =\dfrac{1}{2}\sum\limits_{k=1}^3 {\left( {{e}_{ik} \times \dfrac{\partial {e}_{ik} }{\partial q_{j} }} \right)} \end{eqnarray}$以变形前或变形后中面坐标线弧长微分为基准, 即定义式中偏导分别对变形前和变形后的坐标线弧长进行, 弯扭度分别记为${\omega }_{ij}^{s} $和${\omega }_{ij}^{S} $, 三者的关系为
(16) $\begin{eqnarray} \label{eq16} {\omega }_{ij} =T_{j0} {\omega }_{ij}^{s} =T_{j} {\omega }_{ij}^{S} \end{eqnarray}$弯扭度${\omega }_{ij}^{S} $的几何意义是$P$点以单位速度沿$q_{j}$坐标线"运动"时轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0} } \right)$的角速度.
弯扭度的分量形式记为
(17) $\begin{eqnarray} \label{eq17} {\omega }_{ij} =\omega_{ij}^{1} {T}_{i}^{0} +\omega_{ij}^{2} {B}_{i}^{0} +\omega_{ij}^{3} {N}^{0} \end{eqnarray}$由式(15), 弯扭度的投影$\omega_{ij}^{k} ={\omega }_{ij} \cdot {e}_{ik} $可表为
(18) $\begin{eqnarray} \label{eq18} \left.\begin{array}{l} \omega_{ij}^{1} =-{e}_{i2} \cdot \dfrac{\partial {e}_{i3} }{\partial q_{j} }={e}_{i3} \cdot \dfrac{\partial {e}_{i2} }{\partial q_{j} }\\ \omega_{ij}^{2} =-{e}_{i3} \cdot \dfrac{\partial {e}_{i1} }{\partial q_{j} }={e}_{i1} \cdot \dfrac{\partial {e}_{i3} }{\partial q_{j} }\\ \omega_{ij}^{3} =-{e}_{i1} \cdot \dfrac{\partial {e}_{i2} }{\partial q_{j} }={e}_{i2} \cdot \dfrac{\partial {e}_{i1} }{\partial q_{j} } \end{array}\right\} \end{eqnarray}$后面, 弯扭度分量$\omega_{ij}^{k} $的$l$次方用$\left( {\omega_{ij}^{k} } \right)^{l}$表示.
若矢量${V}$写作${V}=V{V}^{0}$, 其中${V}^{0}$为单位矢量.
其偏导数用弯扭度表为
(19) $\begin{eqnarray} \label{eq19} \dfrac{\partial {V}}{\partial q_{j} }=\dfrac{\partial V}{\partial q_{j} }{V}^{0}+V\dfrac{\tilde{{\partial }}{V}^{0}}{\partial q_{j} }+{\omega }_{ij} \times {V} \end{eqnarray}$其中顶标波浪号表示相对于轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0} } \right)$的导数.
以变形前广义弧坐标微分${d}q$为基准, 沿任意方向${T}_{q}^{0} ={T}_{1}^{0} \cos \alpha +{B}_{1}^{0} \sin \alpha $的弯扭度定义为
(20) $\begin{eqnarray} \label{eq20} {\omega }_{i\alpha } =\dfrac{1}{2}\sum\limits_{k=1}^3 {{e}_{ik} } \times \dfrac{{d}{e}_{ik} }{{d}q} \end{eqnarray}$其中沿中面上曲线$q_{i} =q_{i} \left( q \right)$的单位切矢量为${T}_{q}^{0} $. 用沿坐标线的基于变形后弧长的弯扭度表为
(21) $\begin{eqnarray} \label{eq21} {\omega }_{i\alpha }^{S} =\dfrac{1}{\mbox{sin}\phi }\left[ {-{\omega }_{i1}^{S} \mbox{sin}\left( {\alpha -\phi } \right)+{\omega }_{i2}^{S} \mbox{sin}\alpha } \right] \end{eqnarray}$利用弯扭度的定义式(15), 平面的弯扭度特征是
(22) $\begin{eqnarray} \label{eq22} \omega_{ij}^{1} =\omega_{ij}^{2} =0 \end{eqnarray}$在曲面微分几何中, Rodrigues方程指出了曲面主方向和主曲率的几何特征
[28 ] .当曲面的坐标线为曲率线时,有
(23) $\begin{eqnarray} \label{eq23} \left.\begin{array}{l} \omega_{11}^{1} =0,\\ \omega_{11}^{2} =-T_{1} \kappa _{n1} \\ \omega_{12}^{1} =T_{2} \kappa_{n2} ,\omega_{12}^{2} =0\\ \end{array}\right\} \end{eqnarray}$式中$\kappa_{{n}i} $为两个主曲率. 这也是Rodrigues方程的弯扭度表达.它指出了主方向的弯扭度特征,进一步明确了弯扭度的几何意义.
2.2 等距面上的Lam$\acute{e}$系数和坐标线夹角 板壳中与中面等距离的面称为等距面.在直法线假设下,变形前和变形后等距面方程分别为
(24) $\begin{eqnarray} \label{eq24} {r}^{z} ={r}\left( {q_{1} ,q_{2} } \right)+{u}_{{r}0} , \\ {u}_{{r}0} =z{N}_{0} \end{eqnarray}$和
(25) $\begin{eqnarray} \label{eq25} {R}^{z}={R}+{u}_{{r}} , \\ {u}_{{r}} =z{N}^{0} \end{eqnarray}$或
(26) $\begin{eqnarray} \label{eq26} {R}^{z}={r}^{z}{+u}^{z}, \\ {u}^{z}={u}+{u}_{{r}} -{u}_{{r}0} \end{eqnarray}$其中$h$为弹性薄壳的厚度, $z$为厚度坐标$(-{h}/{2}≤ z≤ {h}/{2})$, ${N}_{0} $为${N}^{0}$的原始值.
计算变形后等距面坐标线的夹角.等距面上沿坐标线的切矢量为
(27) $\begin{eqnarray} \label{eq27} {T}_{i}^{z} ={T}_{i} +z\left( {\omega_{ii}^{2} {T}_{i}^{0} -\omega_{ii}^{1} {B}_{i}^{0} } \right) \end{eqnarray}$略去高阶微量, Lam$\acute{e}$系数和弧长微分为
(28) $\begin{eqnarray} \label{eq28} T_{i}^{z} =\sqrt {{T}_{i}^{z} \cdot {T}_{i}^{z} } =T_{i} +z\omega _{ii}^{2} , \quad {d}S_{i}^{z} =T_{i}^{z} {d}q_{i} \end{eqnarray}$其中用到了对$z$的一阶近似. 单位切向量为
(29) $\begin{eqnarray} \label{eq29} {T}_{i}^{z0} =\dfrac{1}{T_{i}^{z} }\left[ {{T}_{i} +z\left( {\omega_{ij}^{2} {T}_{i}^{0} -\omega_{ij}^{1} {B}_{i}^{0} } \right)} \right] \end{eqnarray}$等距面上坐标线夹角$\phi^{z} $由下式给出
(30) $\begin{eqnarray} \label{eq30} \cos \phi^{z} ={T}_{1}^{z0} \cdot {T}_{2}^{z0} \end{eqnarray}$在略去高阶微量后化作
(31) $\begin{eqnarray} \label{eq31} \phi^{z} =\phi \end{eqnarray}$同理, 变形前沿坐标线的切矢量和单位切矢量有类似形式, 这里不再赘述.
2.3 弯扭度的相容性 定义的弯扭度${\omega }_{ij} $不是互相独立的, 存在相容协调关系.设弹性中面不可撕裂或折叠, 这要求弯扭度是关于广义弧坐标的连续可微函数,并满足相容协调关系.
2.3.1 弯扭度${\omega }_{1j} ,{\omega }_{2j} $的相容性
弹性中面上两个轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0}} \right)$沿同一坐标线的弯扭度${\omega }_{1j} ,{\omega }_{2j}
$的相容协调关系为
(32) $\begin{eqnarray} \label{eq32} {\omega }_{2j} -{\omega }_{1j} =\dfrac{\partial \phi }{\partial q_{j} }{N}^{0} \end{eqnarray}$其在轴系$\left( {{e}_{21} , {e}_{22} , {e}_{23} } \right)$上投影的矩阵式为
(33) $\begin{eqnarray} \label{eq33} \left( {{\begin{array}{*{20}c} {\omega_{2j}^{1} } \\ {\omega_{2j}^{2} } \\ {\omega_{2j}^{3} } \\ \end{array} }} \right)={\varPhi }\left( {{\begin{array}{*{20}c} {\omega_{1j}^{1} } \\ {\omega_{1j}^{2} } \\ {\omega_{1j}^{3} +\dfrac{\partial \phi }{\partial q_{j} }} \\ \end{array} }} \right) \end{eqnarray}$其中$\omega_{ij}^{k} ={\omega }_{ij} \cdot {e}_{ik} $, 矩阵${\varPhi }$由式(10)定义.
证明: 对轴系$\left( {{e}_{11}, {e}_{12}, {e}_{13} }\right)$和矩阵${\varPhi }$, 容易验证如下关系
(34) $\begin{eqnarray} \label{eq34} \left( {{\begin{array}{*{20}c} {{e}_{11} } & {{e}_{12} } & {{e}_{13} } \\ \end{array} }} \right)\left( {{\varPhi }^{\mbox{T}}\cdot \dfrac{\partial {\varPhi }}{\partial q_{j} }} \right)\times \left( {{\begin{array}{*{20}c} {{e}_{11} } \\ {{e}_{12} } \\ {{e}_{13} } \\ \end{array} }} \right)=2\left( {\dfrac{\partial \phi }{\partial q_{j} }} \right){N}^{0} \end{eqnarray}$将式(10)代入式(15), 即可导出式(32). 再将${\omega }_{ij} $向轴系$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$投影, 并注意到式(10), 即得到式(33).
值得说明的是, 式(32)对任意方向的弯扭度也成立, 即
(35) $\begin{eqnarray} \label{eq35} {\omega }_{2\alpha } -{\omega }_{1\alpha } =\dfrac{\partial \phi }{\partial q}{N}^{0} \end{eqnarray}$其中${\omega }_{i\alpha } $由式(20)定义.
2.3.2 弯扭度${\omega }_{i1} ,{\omega }_{i2} $的相容性
弹性中面上同一个轴系沿不同坐标线方向弯扭度${\omega }_{i1} ,{\omega }_{i2} $的相容协调关系有下面四种等价形式
(36) $\begin{eqnarray} \label{eq36} &&\dfrac{\partial {\omega }_{i1} }{\partial q_{2} }-\dfrac{\partial {\omega }_{i2} }{\partial q_{1} }+{\omega }_{i1} \times {\omega }_{i2} =0 \end{eqnarray}$(37) $\begin{eqnarray} \dfrac{\tilde{{\partial }}{\omega }_{i1} }{\partial q_{2} }=\dfrac{\partial {\omega }_{i2} }{\partial q_{1} } \end{eqnarray}$$\begin{eqnarray} \dfrac{\partial {\omega }_{i1} }{\partial q_{2} }=\dfrac{\tilde{{\partial }}{\omega }_{i2} }{\partial q_{1} } \end{eqnarray}$$(38) (39) $\begin{eqnarray} \dfrac{\tilde{{\partial }}{\omega }_{i1} }{\partial q_{2} }-\dfrac{\tilde{{\partial }}{\omega }_{i2} }{\partial q_{1} }+{\omega }_{i2} \times {\omega }_{i1} =0 \end{eqnarray}$其中波浪号表示相对轴系$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3}} \right)$的偏导数.
证明: 设${a}$为给定轴系$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$中的固定常矢量, 由式(19)依次对$q_{1} ,q_{2}$求混合偏导数.由求偏导次序的可交换性, 以及三重矢积恒等式, 得到
(40) $\begin{eqnarray} \label{eq40} \left( {\dfrac{\partial {\omega }_{i1} }{\partial q_{2} }-\dfrac{\partial {\omega }_{i2} }{\partial q_{1} }+{\omega }_{i1} \times {\omega }_{i2} } \right)\times {a}=0 \end{eqnarray}$因${a}$为任意的固定矢量, 于是就导出式(36). 再由式(19),从式(36)导出式(37). 同理可导出式(38)和式(39).
值得指出, 以实际弧长为基准的弯扭度${\omega }_{ij}^{s} ,{\omega}_{ij}^{S} $对不同下标$j$的相容协调关系一般不具有式(36)的形式.
2.3.3 弯扭度相容方程的独立性
可以证明式(36)给出的两个式子可以互相推导, 即
(41) $\begin{eqnarray} \label{eq41} && \dfrac{\partial {\omega }_{21} }{\partial q_{2} }-\dfrac{\partial {\omega }_{22} }{\partial q_{1} }+{\omega }_{21} \times {\omega }_{22} = \dfrac{\partial {\omega }_{11} }{\partial q_{2} }-\dfrac{\partial {\omega }_{12} }{\partial q_{1} }+{\omega }_{11} \times {\omega }_{12} \end{eqnarray}$将式(32)代入式(41)等号左边即可推出等号右边.
2.3.4 中面上弯扭度与切矢量的相容性
弹性中面上弯扭度与一点的切矢量也必须是相容的.切矢量满足如下关系
(42) $\begin{eqnarray} \label{eq42} \dfrac{\partial {T}_{1} }{\partial q_{2} }=\dfrac{\partial {T}_{2} }{\partial q_{1} } \end{eqnarray}$这既是曲线积分
(43) $\begin{eqnarray} \label{eq43} {R}=\displaystyle\int {{T}_{1} } {d}q_{1} +{T}_{2} {d}q_{2} \end{eqnarray}$与路径无关的条件, 保证变形后的弹性中面无裂缝;也是两沿坐标线切矢量的相容协调关系.
注意到${T}_{i} =T_{i} {T}_{i}^{0} $, 式(42)写作
(44) $\begin{eqnarray} \label{eq44} \dfrac{\partial T_{1} }{\partial q_{2} }{T}_{1}^{0} +T_{1} {\omega }_{12} \times {T}_{1}^{0} =\dfrac{\partial T_{2} }{\partial q_{1} }{ T}_{2}^{0} +T_{2} {\omega }_{21} \times {T}_{2}^{0} \end{eqnarray}$其分量形式为
(45) $\begin{eqnarray} \label{eq45} \left.\begin{array}{l} \dfrac{\partial T_{1} }{\partial q_{2} }=\dfrac{\partial T_{2} }{\partial q_{1} }\cos \phi -T_{2} \omega_{21}^{3} \sin \phi \\ T_{1} \omega_{12}^{3} =\dfrac{\partial T_{2} }{\partial q_{1} }\sin \phi +T_{2} \omega_{21}^{3} \cos \phi \\ T_{1} \omega_{12}^{2} =T_{2} \omega_{21}^{2} \\ \end{array}\right\} \end{eqnarray}这是关于弯扭度和Lam$\acute{e}$系数的约束方程. 由式(33), 式(45)右端的弯扭度可用${\omega }_{1i} $表达, 化作
(46) $\begin{eqnarray} \label{eq46} \left.\begin{array}{l} \dfrac{\partial T_{1} }{\partial q_{2} }=\dfrac{\partial T_{2} }{\partial q_{1} }\cos \phi -T_{2} \left( {\omega_{11}^{3} +\dfrac{\partial \phi }{\partial q_{1} }} \right)\sin \phi \\ T_{1} \omega_{12}^{3} =\dfrac{\partial T_{2} }{\partial q_{1} }\sin \phi +T_{2} \left( {\omega_{11}^{3} +\dfrac{\partial \phi }{\partial q_{1} }} \right)\cos \phi \\ T_{1} \omega_{12}^{2} =T_{2} \left( {-\omega_{11}^{1} \sin \phi +\omega _{11}^{2} \cos \phi } \right) \\ \end{array}\right\} \end{eqnarray}$式(32)和式(36)及其等阶形式, 以及约束方程(46), 在弯扭度用Euler角及其偏导数表示时再作进一步讨论.
3 轴系姿态和弯扭度 中面偏微分方程 3.1 轴系姿态的Euler 建立惯性参照系$O-\xi \eta \zeta $.借助Euler角将轴系$\left( {{e}_{i1}, {e}_{i2} , {e}_{i3} } \right)$用惯性参照系的基矢量$\left( {{e}_{\xi } ,{e}_{\eta } ,{e}_{\zeta } } \right)$表达. 为此将$O-\xi \eta \zeta $平移到弹性中面的$P$点, 绕轴的如下三次转动到达轴系$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$的位置$P-xyz$ ,如
图3 所示
[4 ,29 ] $\begin{eqnarray*} P-\xi \eta \zeta \mathrel{\mathop{\kern0pt\longrightarrow}\limits_{\psi_{i} }^\zeta } P-x_{1} y_{1} z_{1} \mathrel{\mathop{\kern0pt\longrightarrow}\limits_{\theta _{i} }^{x_{1} }} P-x_{2} y_{2} z_{2} \mathrel{\mathop{\kern0pt\longrightarrow}\limits_{\varphi_{i} }^{z_{2} }} P{-}xyz \end{eqnarray*}$
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下载原图ZIP |
生成PPT 图3轴系$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} }\right)$ 姿态的Euler角 Fig.3Euler angles of attitude of the frame $\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$ 基的变换关系用矩阵表为
(47) $\begin{eqnarray} \label{eq47} \left( {{\begin{array}{*{20}c} {{e}_{i1} } \\ {{e}_{i2} } \\ {{e}_{i3} } \\ \end{array} }} \right)={Q}_{i} \left( {{\begin{array}{*{20}c} {{e}_{\xi } } \\ {{e}_{\eta } } \\ {{e}_{\zeta } } \\ \end{array} }} \right) \end{eqnarray}$其中${Q}_{i} $为方向余弦矩阵
(48) $\begin{eqnarray} {Q}_{i} = \left( {{\begin{array}{*{20}c} {\mbox{c}\psi \mbox{c}\varphi_{i} -\mbox{c}\theta \mbox{s}\psi \mbox{s}\varphi_{i} } & {\mbox{c}\varphi_{i} \mbox{s}\psi +\mbox{c}\psi \mbox{c}\theta \mbox{s}\varphi_{i} } & {\mbox{s}\theta \mbox{s}\varphi_{i} } \\ {-\mbox{c}\psi \mbox{s}\varphi_{i} -\mbox{c}\theta \mbox{s}\psi \mbox{c}\varphi_{i} } & {-\mbox{s}\varphi_{i} \mbox{s}\psi +\mbox{c}\psi \mbox{c}\theta \mbox{c}\varphi_{i} } & {\mbox{s}\theta \mbox{c}\varphi_{i} } \\ {\mbox{s}\psi \mbox{s}\theta } & {-\mbox{c}\psi \mbox{s}\theta } & {\mbox{c}\theta } \\ \end{array} }} \right) \end{eqnarray}$由
图2 知, $\psi_{2} =\psi_{1} ,\theta_{2} =\theta_{1} ,\varphi_{2}=\varphi_{1} +\phi $, 可略去$\psi ,\theta $的下标; $\psi =\psi \left({q_{1} ,q_{2} } \right)$, $\theta =\theta \left( {q_{1} ,q_{2} } \right)$,$\varphi_{i} =\varphi_{i} \left( {q_{1} ,q_{2} } \right)$ 为轴系$\left({{e}_{i1} , {e}_{i2} , {e}_{i3} }\right)$相对于惯性系的Euler角; 字母$\mbox{s},\mbox{c}$分别表示$\sin ,\cos $.
两方向余弦矩阵${Q}_{i} $之间有如下关系
(49) $\begin{eqnarray} \label{eq49} {Q}_{2} ={\varPhi Q}_{1} \end{eqnarray}$式中${\varPhi }$由式(10)定义.
当给定矩阵${Q}_{i} $, 可以通过式(48)从对应元素相等解出相应的Euler角
[4 ,29 ] . 表达轴系$\left({{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$在惯性参照系$O-\xi \eta \zeta $中的姿态还可以用Cardano角或Euler参数等, 这里不再赘述.
3.2 弯扭度的Euler角表示 由刚体动力学知, 用Euler角表达的弯扭度${\omega }_{ij} $在基$\left( {{e}_{i1} , {e}_{i2} , {e}_{i3} } \right)$下的矩阵式为
[4 ,29 ] (50) $\left.\begin{array}{l} {\omega }_{ij} ={\varTheta }_{i} \dfrac{\partial }{\partial q_{j} }\left( {{\begin{array}{*{20}c} \psi \hfill \\ \theta \hfill \\ {\varphi_{i} } \hfill \\ \end{array} }} \right)\\ {\varTheta }_{i} =\left( {{\begin{array}{*{20}c} {\sin \theta \sin \varphi_{i} } \hfill & {\cos \varphi_{i} } \hfill & 0 \hfill \\ {\sin \theta \cos \varphi_{i} } \hfill & {-\sin \varphi_{i} } \hfill & 0 \hfill \\ {\cos \theta } \hfill & 0 \hfill & 1 \hfill \\ \end{array} }} \right) \end{array}\right\}$将此弯扭度的Euler角表达式代入弯扭度的相容方程(32)和方程(36)$\sim$(39),都成为恒等式.表明弯扭度的相容方程对Euler角不构成约束.弯扭度的Euler角表达式将使式(45)和式(46)转化为对Euler角和Lam$\acute{e}$系数及其偏导数的约束方程.
3.3 中面偏微分方程 在惯性参照系$O-\xi \eta \zeta $中, 变形后弹性中面上一点$P$的直角坐标为
(51) $\begin{eqnarray} \label{eq51} \xi =\xi \left( {q_{1} ,q_{2} } \right),\eta =\eta \left( {q_{1} ,q_{2} } \right),\zeta =\zeta \left( {q_{1} ,q_{2} } \right) \end{eqnarray}$式(3)给出中面的偏微分方程的矢量形式
(52) $\begin{eqnarray}\dfrac{\partial {R}}{\partial q_{i} }=T_{i} {T}_{i}^{0} \end{eqnarray}$将${T}_{i}^{0} $用Euler角表示并投影到惯性参照系的基矢量$\left( {{e}_{\xi } ,{e}_{\eta } ,{e}_{\zeta } } \right)$.方向余弦矩阵式(48)第一行为单位切矢量${T}_{i}^{0}$在惯性基投影的Euler角表示, 导出中面偏微分方程的投影式
(53) $\begin{eqnarray} \left.\begin{array}{l} \dfrac{\partial \xi }{\partial q_{i} }=T_{i} \left( {\mbox{cos}\psi \mbox{cos}\varphi_{i} -\mbox{cos}\theta \mbox{sin}\psi \mbox{sin}\varphi_{i} } \right)\\ \dfrac{\partial \eta }{\partial q_{i} }=T_{i} \left( {\mbox{sin}\psi \mbox{cos}\varphi_{i} +\mbox{cos}\psi \mbox{cos}\theta \mbox{sin}\varphi_{i} } \right)\\ \dfrac{\partial \zeta }{\partial q_{i} }=T_{i} \mbox{sin}\theta \mbox{sin}\varphi_{i} \end{array}\right\} \end{eqnarray}$当已知Euler角和Lam$\acute{e}$系数$\psi ,\theta ,\varphi ,\phi ;T_{1},T_{2} $随广义弧坐标$q_{i} $的变化规律, 且满足约束方程(46),式中弯扭度由式(50)给出, 即
(54) $\begin{eqnarray} \left.\begin{array}{l} \omega_{12}^{2} =\sin \theta \cos \varphi_{1} \dfrac{\partial \psi }{\partial q_{2} }-\sin \varphi_{1} \dfrac{\partial \theta }{\partial q_{2}}\\ \omega_{12}^{3} =\cos \theta \dfrac{\partial \psi }{\partial q_{2} }+\dfrac{\partial \varphi_{1} }{\partial q_{2} }\\ \omega_{21}^{2} =\sin \theta \cos \varphi_{2} \dfrac{\partial \psi }{\partial q_{1} }-\sin \varphi_{2} \dfrac{\partial \theta }{\partial q_{1}}\\ \omega_{21}^{3} =\cos \theta \dfrac{\partial \psi }{\partial q_{1} }+\dfrac{\partial \varphi_{2} }{\partial q_{1} }\\ \varphi_{2} =\varphi_{1} +\phi \end{array}\right\} \end{eqnarray}$并且已知边界条件, 如
(55) $\begin{eqnarray} \left.\begin{array}{l} \left( {\xi ,\eta ,\zeta } \right)_{q_{0} } =\left( {\xi_{q_{0} } ,\eta _{q_{0} } ,\zeta_{q_{0} } } \right) \\ \left. {T_{i} } \right|_{q_{j} =q_{j0} } =g_{i} \left( {q_{i} } \right) \\ \left( {i\ne j} \right) \\ \left( {\psi ,\theta ,\varphi } \right)_{q_{0} } =\left( {\psi_{q_{0} } ,\theta_{q_{0} } ,\varphi_{q_{0} } } \right) \\ \left. \phi \right|_{q_{1} =q_{10} } =\phi_{q_{1} } \left( {q_{2} } \right) \\ \end{array}\right\} \end{eqnarray}$就可以求得弹性中面的位形.
特殊地, 当仅有$i=1$时, 式(53)即为弹性细杆的轴线微分方程, 此时${R}$为弹性细杆中心线的矢径, ${T}_{i}^{0} $为其单位切矢量.可见这是弹性细杆轴线微分方程向弹性薄壳中面的推广.
4 应变和应力及其弯扭度表达 一点沿任意$q$坐标线方向的线应变定义为
[30 ] (56) $\begin{eqnarray} \label{eq56} \varepsilon =\dfrac{{d}S-{d}s}{{d}s}=\dfrac{T}{T_{0} }-1 \end{eqnarray}$式中${d}S$是微分弧段${d}s$在变形后的长度,$T={{{d}S}/{{d}q}}$, $T_{0}={{{d}s}/{{d}q}}$为相应的Lam$\acute{e}$系数.可近似表为
[30 ] (57) $\begin{eqnarray} \label{eq57} \varepsilon =\dfrac{{d}{r}}{{d}s}\cdot \dfrac{{d}{ u}}{{d}s}+\dfrac{1}{2}\dfrac{{d}{u}}{{d}s}\cdot \dfrac{{d}{u}}{{d}s} \end{eqnarray}$4.1 等距面上一点的线应变合成定理 等距面上一点的线应变合成定理:弹性薄壳变形后等距面上一点$P^{z}$沿坐标线$q_{i} $的线应变$\varepsilon_{i}^{z} $等于中面上点$P$沿该坐标线的线应变$\varepsilon_{{e}i}$和点$P^{z}$相对于点$P$的线应变$\varepsilon_{{r}i} $,以及原始相对应变负值$-\varepsilon_{{r}i0} $的代数和, 表示为
(58) $\begin{eqnarray} \label{eq58} \varepsilon_{i}^{z} =\varepsilon_{{e}i} +\varepsilon _{{r}i} -\varepsilon_{{r}i0} \end{eqnarray}$其中
(59) $\begin{eqnarray} \label{eq59} \varepsilon_{{e}i} =\dfrac{{d}S_{i} -{d}s_{i} }{{d}s_{i} }=\dfrac{T_{i} }{T_{i0} }-1 \end{eqnarray}$或
(60) $\begin{eqnarray} &&\varepsilon_{{e}i} =\dfrac{1}{\left( {T_{i0} } \right)^{2}}\left( {{T}_{i0} \cdot \dfrac{\partial {u}}{\partial q_{i} }+\dfrac{1}{2}\dfrac{\partial {u}}{\partial q_{i} }\cdot \dfrac{\partial {u}}{\partial q_{i} }} \right) \end{eqnarray}$(61) $\begin{eqnarray} \varepsilon_{{r}i} =\dfrac{1}{\left( {T_{i0} } \right)^{2}}\left( {{T}_{i} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{i} }} \right) \end{eqnarray}$(62) $\begin{eqnarray} \varepsilon_{{r}i0} =\dfrac{1}{T_{i0} }\left( {{T}_{i0}^{0} \cdot \dfrac{\partial {u}_{\mbox{r0}} }{\partial q_{i} }} \right) \end{eqnarray}$其中${u}_{{r}} $由式(25)定义, ${u}_{\mbox{r0}}$为其原始值由式(24)定义.
若变形前弹性中面为曲面, ${\partial {N}{ }_{0} }/{\partial q_{i}}\ne 0$. 将式(24)代入式(57), 此时式中$\varepsilon $为$\varepsilon_{i}^{z}$, 略去二阶以上小量便得到式(58).
下面用弯扭度表达$\varepsilon_{{r}i} ,\varepsilon_{{r}i0}$. 由式(25), 得
(63) $\begin{eqnarray} \label{eq63} \dfrac{\partial {u}_{{r}} }{\partial q_{i} }=z\dfrac{\partial { N}^{0}}{\partial q_{i} }=z\left( {{\omega }_{ji} \times {N}^{0}} \right)=z\left( {\omega_{ji}^{2} {T}_{j}^{0} -\omega_{ji}^{1} { B}_{j}^{0} } \right) \end{eqnarray}$代入式(61), 取$j=i$, 相对线应变$\varepsilon_{{r}i}$用弯扭度表达为
(64) $\begin{eqnarray} \label{eq64} \varepsilon_{{r}i} =\dfrac{1}{\left( {T_{i0} } \right)^{2}}\left( {{T}_{i} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{i} }} \right)=\dfrac{T_{i} }{\left( {T_{i0} } \right)^{2}}z\omega_{ii}^{2} \end{eqnarray}$即
(65) $\begin{eqnarray} \label{eq65} \left.\begin{array}{l} \varepsilon_{r_1} =\dfrac{T_{1} }{\left( {T_{10} } \right)^{2}}z\omega_{11}^{2} \\ \varepsilon_{r_2} =\dfrac{T_{2} }{\left( {T_{20} } \right)^{2}}z\omega_{22}^{2}=\\ \qquad \dfrac{T_{2} }{\left( {T_{20} } \right)^{2}}z\left( {\omega _{12}^{2} \cos \phi -\omega_{12}^{1} \sin \phi } \right) \\ \end{array}\right\} \end{eqnarray}$在应变的一次近似下, 式中可取$\cos \phi =0,\sin \phi =1$, ${T_{i}}/{T_{i0} }=1$, 写作
(66) $\begin{eqnarray} \label{eq66} \varepsilon_{r_1} =\dfrac{1}{T_{10} }z\omega_{11}^{2} ,\quad \varepsilon_{r_2} =\dfrac{1}{T_{20} }z\omega_{22}^{2} =-\dfrac{1}{T_{20} }z\omega_{12}^{1} \end{eqnarray}$同理, 可得
(67) $\begin{eqnarray} \label{eq67} \varepsilon_{r_{10}} =\dfrac{1}{T_{10} }z\omega_{11}^{02} , \quad \varepsilon_{r_{20}} =\dfrac{1}{T_{20} }z\omega_{22}^{02} =-\dfrac{1}{T_{20} }z\omega_{12}^{01}\quad \end{eqnarray}$其中${\omega }_{22}^{0} ,{\omega }_{12}^{0} $为原始弯扭度.
4.2 等距面上一点的剪应变 等距面上一点的剪应变合成定理: 变形后弹性等距面上一点$P^{z}$的剪应变$\gamma_{xy}^{z} $在一次近似下等于弹性中面上一点$P$的剪应变$\gamma_{{e}xy}$和点$P^{z}$相对于点$P$的剪应变$\gamma_{{r}xy} $,以及变形前点$p^{z}$的"剪应变"负值$-\gamma_{xy0}^{z} =-\left( {\gamma_{{e}xy0} +\gamma_{{r}xy0} } \right)$的代数和. 表示为
(68) $\begin{eqnarray} \label{eq68} \gamma_{xy}^{z}=\gamma_{{e}xy} +\gamma_{{r}xy} -\left( {\gamma_{{e}xy0} +\gamma_{{r}xy0} } \right) \end{eqnarray}$式中
(69) $\begin{eqnarray} \label{eq69} &&\hspace{-6mm}\gamma_{{e}xy} ={T}_{1}^{0} \cdot {T}_{2}^{0} =\cos \phi , \gamma_{{e}xy0} ={T}_{10}^{0} \cdot {T}_{20}^{0} =\cos \phi _{0} \end{eqnarray}$(70) $\begin{eqnarray} \gamma_{{r}xy}^{z} =\dfrac{1}{T_{1} }{T}_{2}^{0} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{1} }+\dfrac{1}{T_{2} }{T}_{1}^{0} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{2} } \end{eqnarray}$或
(71) $\begin{eqnarray} \label{eq71} &&\gamma_{{r}xy}^{z} =\dfrac{1}{T_{10} }{T}_{2}^{0} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{1} }+\dfrac{1}{T_{20} }{T}_{1}^{0} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{2} } \end{eqnarray}$(72) $\begin{eqnarray} \gamma_{rxy0} =\dfrac{1}{T_{20} }{T}_{10}^{0} \cdot \dfrac{\partial {u}_{{r}0} }{\partial q_{2} }+\dfrac{1}{T_{10} }{T}_{20}^{0} \dfrac{\partial {u}_{{r}0} }{\partial q_{1} } \end{eqnarray}$推导如下: 变形前弹性薄壳等距面坐标线一般不是正交的. 因此, 按照剪应变的定义,在小应变下有
$(73) $\begin{eqnarray} \label{eq73} && \gamma_{xy}^{z} =\dfrac{\pi }{2}-\phi^{z}-\left( {\dfrac{\pi }{2}-\phi_{0}^{z} } \right)=\cos \phi^{z}-\cos \phi_{0}^{z} = {T}_{1}^{z0} \cdot {T}_{2}^{z0} -{T}_{10}^{z0} \cdot {T}_{20}^{z0} \end{eqnarray}$其中
(74) $\begin{eqnarray} && \cos \phi^{z}={T}_{1}^{z0} \cdot {T}_{2}^{z0} ={T}_{1}^{0} \cdot {T}_{2}^{0} +\dfrac{1}{T_{2} }\left( {{T}_{1}^{0} \cdot \dfrac{\partial {u}_{{r}} }{\partial q_{2} }} \right)+ \dfrac{1}{T_{1} }\left( {{T}_{2}^{0} \cdot \dfrac{\partial { u}_{{r}} }{\partial q_{1} }} \right) \end{eqnarray}$(75) $\begin{eqnarray} && \cos \phi_{0}^{z} ={T}_{10}^{z0} \cdot {T}_{20}^{z0}={T}_{10}^{0} \cdot {T}_{20}^{0} +z\left( \dfrac{1}{T_{10} }{T}_{20}^{0} \cdot \dfrac{\partial {N}_{0} }{\partial q_{1} }+\right. \left.\dfrac{1}{T_{20} }{T}_{10}^{0} \cdot \dfrac{\partial {N}_{0} }{\partial q_{2} } \right) \end{eqnarray}$这就得到了式(68).
用弯扭度表达相对剪应变. 由式(70)得
(76) $\begin{eqnarray} &&\gamma_{{r}xy} =\dfrac{z}{T_{1} }{\omega }_{21} \cdot \left( {{N}^{0}\times {T}_{2}^{0} } \right)+\dfrac{z}{T_{2} }{\omega }_{12} \cdot \left( {{N}^{0}\times {T}_{1}^{0} } \right)=z\left( {\dfrac{1}{T_{1} }\omega_{21}^{2} +\dfrac{1}{T_{2} }\omega _{12}^{2} } \right) \end{eqnarray}$或
(77) $\begin{eqnarray} \gamma_{{r}xy} =z\left[ {\dfrac{1}{T_{1} }\left( {\omega_{11}^{2} \cos \phi -\omega_{11}^{1} \sin \phi } \right)+\dfrac{1}{T_{2} }\omega _{12}^{2} } \right] \end{eqnarray}$同理得
(78) $\begin{eqnarray} \gamma_{{r}xy0} =\dfrac{z}{T_{10} }\omega_{21}^{02} +\dfrac{z}{T_{20} }\omega_{12}^{02} \end{eqnarray}$或
(79) $\begin{eqnarray} \gamma_{{r}xy0} =\dfrac{z}{T_{10} }\left( {\omega_{11}^{02} \cos \phi_{0} -\omega_{11}^{01} \sin \phi_{0} } \right)+\dfrac{z}{T_{20} }\omega_{12}^{02} \end{eqnarray}$在应变的一次近似下, 取${T_{20} }/{T_{2} }={T_{10} }/{T_{1} }=1$,式(77)和式(79)化作
(80) $\begin{eqnarray} &&\gamma_{{r}xy} =z\left( {-\dfrac{1}{T_{10} }\omega_{11}^{1} +\dfrac{1}{T_{20} }\omega_{12}^{2} } \right) \end{eqnarray}$(81) $\begin{eqnarray} \gamma_{{r}xy0} =z\left( {-\dfrac{1}{T_{10} }\omega_{11}^{01} +\dfrac{1}{T_{20} }\omega_{12}^{02} } \right) \end{eqnarray}$4.3 等距面上一点沿任意方向的线应变 等距面上一点沿任意方向${T}_{q}^{0} $的应变$\varepsilon_{q}^{z} $, 在一阶近似下可以用沿坐标线的应变$\varepsilon_{i}^{z} ,\gamma_{xy}^{z}$表为
(82) $\begin{eqnarray} \label{eq82} && \varepsilon_{q}^{z} =\dfrac{1}{\sin^{2}\phi }\left[ {\varepsilon_{1}^{z} \sin^{2}\left( {\phi -\alpha } \right)+\varepsilon_{2}^{z} \sin^{2}\alpha } +\right. \left. {\gamma_{xy}^{z} \sin \alpha \sin \left( {\phi -\alpha } \right)} \right] \end{eqnarray}$当$\alpha ={\pi }/{2}$时为${B}_{1}^{0} $方向, 应变及其一次近似记为$\varepsilon_{3}^{z} $, 分别为
(83) $\begin{eqnarray} \label{eq83} \left. {\varepsilon_{3}^{z} =\varepsilon_{q}^{z} } \right|_{\alpha ={\pi}/{2}} =\dfrac{1}{\sin^{2}\phi }\left( {\varepsilon_{1}^{z} \cos ^{2}\phi +\varepsilon_{2}^{z} -\gamma_{xy}^{z} \cos \phi } \right)\quad \end{eqnarray}$和
(84) $\begin{eqnarray} \label{eq84} \left. {\varepsilon_{3}^{z} =\varepsilon_{q}^{z} } \right|_{\alpha ={\pi }/{2}} =\varepsilon_{2}^{z} \end{eqnarray}$沿${T}_{1}^{0} ,{T}_{2}^{0} $方向的应变为
(85) $\begin{eqnarray} \label{eq85} \left. {\varepsilon_{q}^{z} } \right|_{\alpha =0} =\varepsilon_{1}^{z} , \quad \left. {\varepsilon_{q}^{z} } \right|_{\alpha =\phi } =\varepsilon_{2}^{z} \end{eqnarray}$这结果是显然的.
可以验证, 薄板的经典大挠度理论是上述结果的特例.
4.4 应力及其弯扭度表达 等距面上$P^{z}$点垂直于坐标轴基矢量${T}_{1}^{0}$, ${B}_{1}^{0}$, ${N}^{0}$且外法线与坐标轴一致的截面依次记为$S_{1}^{+}$, $S_{13}^{+}$, $z^{+}$, 微分单元截面上沿轴系$(T_{1}^{0}, {B}_{1}^{0}, {N}^{0})$基矢量方向的正应力和剪应力分别记为$(\sigma_{x}^{z}, \sigma_{y}^{z}, \sigma_{z}^{z})$和$(\tau_{xy}^{z}, \tau_{yz}^{z}, \tau_{zx}^{z})$,正应变和剪应变分别记为$(\varepsilon_{x}^{z}, \varepsilon_{y}^{z}, \varepsilon_{z}^{z})$和$(\gamma_{xy}^{z}, \gamma_{yz}^{z}, \gamma_{zx}^{z})$. 在直法线假设下, 不计应力分量$\sigma_{z}^{z}$和剪应变分量$\gamma_{yz}^{z}$, $\gamma_{zx}^{z}$, 但计及相应的剪应力$\tau_{yz}^{z}$, $\tau_{zx}^{z}$. 微分单元上计及的应变所对应的应力分量如
图4 所示.
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生成PPT 图4直法线假设下计及的应变所对应的应力 Fig.4The stress corresponding to the strain considered under the straight normal assumption 设材料是线弹性的. 由广义Hooke定律知
(86) $\begin{eqnarray} \left.\begin{array}{l} \sigma_{x}^{z} =\dfrac{E}{1-\mu^{2}}\left( {\varepsilon_{x}^{z} +\mu \varepsilon_{y}^{z} } \right)\\ \sigma_{y}^{z} =\dfrac{E}{1-\mu^{2}}\left( {\varepsilon_{y}^{z} +\mu \varepsilon_{x}^{z} } \right)\\ \tau_{xy}^{z} =G\gamma_{xy}^{z} \end{array}\right\} \end{eqnarray}$式中, $E$, $G$, $\mu$分别为材料的拉压弹性模量、剪切弹性模量和Poisson比,三者满足关系$G=E/2(1+\mu)$.
注意到式(84), 将应变式(58)和式(68)代入式(86), 式中应变分量由弯扭度和Lam$\acute{e}$系数表达, 得
(87) $\begin{eqnarray} \left.\begin{array}{l} \sigma_{x}^{z} =\sigma_{{e}x} +\sigma_{{r}x} -\sigma_{{r}x0} \\\sigma_{y}^{z} =\sigma_{{e}y} +\sigma_{{r}y} -\sigma _{{r}y0}\\ \tau_{xy}^{z} =\tau_{{e}xy} +\tau_{{r}xy} -\left( {\tau _{{e}xy0} +\tau_{{r}xy0} } \right) \end{array}\right\} \end{eqnarray}$其中
(88) $\begin{eqnarray} \label{eq88} &&\left.\begin{array}{l} \sigma_{{e}x} =\dfrac{E}{1-\mu^{2}}\left[ {\left( {\dfrac{T_{1} }{T_{10} }-1} \right)+\mu \left( {\dfrac{T_{2} }{T_{20} }-1} \right)} \right]\\ \sigma_{{e}y} =\dfrac{E}{1-\mu^{2}}\left[ {\left( {\dfrac{T_{2} }{T_{20} }-1} \right)+\mu \left( {\dfrac{T_{1} }{T_{10} }-1} \right)} \right]\\ \end{array}\right\} \end{eqnarray}$(89) $\begin{eqnarray} \left.\begin{array}{l} \sigma_{{r}x} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{T_{1} }{\left( {T_{10} } \right)^{2}}\omega_{11}^{2} +\mu \dfrac{T_{2} }{\left( {T_{20} } \right)^{2}}\omega_{22}^{2} } \right) \\ \sigma_{{r}y} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{T_{2} }{\left( {T_{20} } \right)^{2}}\omega_{22}^{2} +\mu \dfrac{T_{1} }{\left( {T_{10} } \right)^{2}}\omega_{11}^{2} } \right) \\ \end{array}\right\} \end{eqnarray}$(90) $\begin{eqnarray} \left.\begin{array}{l} \sigma_{{r}x0} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{1}{T_{10} }\omega_{11}^{02} +\dfrac{\mu }{T_{20} }\omega_{22}^{02} } \right) \\ \sigma_{{r}y0} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{1}{T_{20} }\omega_{22}^{02} +\dfrac{\mu }{T_{10} }\omega_{11}^{02} } \right) \\ \end{array}\right\} \end{eqnarray}$或由式(66)和式(67), 式(89)和式(90)化为
(91) $\begin{eqnarray} &&\left.\begin{array}{l} \sigma_{{r}x} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{1}{T_{10} }\omega_{11}^{2} -\dfrac{\mu }{T_{20} }\omega_{12}^{1} } \right) \\ \sigma_{{r}y} =\dfrac{Ez}{1-\mu^{2}}\left( {-\dfrac{1}{T_{20} }\omega_{12}^{1} +\dfrac{\mu }{T_{10} }\omega_{11}^{2} } \right) \\ \end{array}\right\} \end{eqnarray}$(92) $\begin{eqnarray} \left.\begin{array}{l} \sigma_{{r}x0} =\dfrac{Ez}{1-\mu^{2}}\left( {\dfrac{1}{T_{10} }\omega_{11}^{02} -\dfrac{\mu }{T_{20} }\omega_{12}^{01} } \right) \\ \sigma_{{r}y0} =\dfrac{Ez}{1-\mu^{2}}\left( {-\dfrac{1}{T_{20} }\omega_{12}^{01} +\dfrac{\mu }{T_{10} }\omega_{11}^{02} } \right) \\ \end{array}\right\} \end{eqnarray}$截面在中线处的剪应力为
(93) $\begin{eqnarray} \label{eq93} \tau_{{e}xy} =G\cos \phi ,\tau_{{e}xy0} =G\cos \phi_{0} \end{eqnarray}$相对剪应力为
(94) $\begin{eqnarray} \left.\begin{array}{l} \tau_{{r}xy} =Gz\left( {-\dfrac{1}{T_{1} }\omega_{11}^{1} +\dfrac{1}{T_{2} }\omega_{12}^{2} } \right) \\ \tau_{{r}xy0} =Gz\left( {-\dfrac{1}{T_{10} }\omega_{11}^{01} +\dfrac{1}{T_{20} }\omega_{12}^{02} } \right) \\ \end{array}\right\} \end{eqnarray}$按照剪应力互等定理, 有
(95) $\begin{eqnarray} \label{eq95} &&\tau_{xy}^{z} =\tau_{yx}^{z} , \tau_{{e}xy} =\tau_{{e}yx} , \tau_{{r}xy} =\tau_{{r}yx} \end{eqnarray}$(96) $\begin{eqnarray} \tau_{{e}xy0} =\tau_{{e}yx0} ,\tau_{{r}xy0} =\tau_{{r}yx0} \end{eqnarray}$式中, $\sigma_{{e}x} ,\sigma_{{e}y} ,\tau_{{e}xy}$为薄膜应力, $\sigma_{{r}x} ,\sigma_{{r}y} $为弯曲应力,$\tau_{{r}xy} $为扭转剪应力, 而$\sigma_{{e}x0} ,\sigma _{{e}y0} ,\sigma_{{r}x0} ,\sigma_{{r}y0} ,\tau_{{r}xy0} $不具有应力的意义.
5 弹性薄壳截面上的分布内力和本构方程 5.1 弹性薄壳截面上内力的简化 变形后弹性薄壳的微分单元如
图5 所示, 其中应力$\sigma_{x}^{z} ,\sigma_{y}^{z} ,\tau_{xy}^{z} ,\tau_{yz}^{z}
$由式(87)给出. 弹性中面和$z$等距面上坐标线的弧长微分分别由式(3)和式(28)给出.$_{ }$由式(9)可得${B}_{1}^{0} $方向的弧长微分为
(97) $\begin{eqnarray} \left.\begin{array}{l} {d}S_{3} =B_{1} {d}q_{3} =\sin \phi {d}S_{2}\\ {d}S_{3}^{z} =B_{1}^{z} {d}q_{3} =\sin \phi^{z}{d}S_{2}^{z} \end{array}\right\} \end{eqnarray}$微分单元截面上应力向中线简化的结果为一分布主矩和分布主矢, 如
图6 所示.
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生成PPT 图5微分单元及其计及应变的应力状态 Fig.5Differential unit and its stress state considering strain 图6 新窗口打开 |
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生成PPT 图6微分单元及其内力: 分布主矩和分布主矢 Fig.6Differential unit and its internal force: Distributed principal moment and distributed principal vector 在微分单元的$S_{1}^{+} $和$S_{3}^{+} $截面上, 分布主矩和分布主矢为
(98) $\begin{eqnarray} \label{eq98} &&\left.\begin{array}{l} {M}_{1} =M_{1x} {T}_{1}^{0} +M_{1y} {B}_{1}^{0} \\ {F}_{1} =F_{1x} {T}_{1}^{0} +F_{1y} {B}_{1}^{0} +F_{1z} {N}^{0} \\ \end{array}\right\} \end{eqnarray}$(99) $\begin{eqnarray} \left.\begin{array}{l} {M}_{3} =M_{3x} {T}_{1}^{0} +M_{3y} {B}_{1}^{0} \\ {F}_{3} =F_{3x} {T}_{1}^{0} +F_{3y} {B}_{1}^{0} +F_{3z} {N}^{0} \\ \end{array}\right\} \end{eqnarray}$其中, $M_{1x} ,M_{3y} $为分布扭矩, $M_{1y} ,M_{3x} $为分布弯矩, $F_{1x} ,F_{3y} $为法向分布力, $F_{1y} ,F_{1z} ,F_{3x} ,F_{3z}$为切向分布力. 具体表达如下
(100) $\begin{eqnarray} && M_{1x} =-\dfrac{1}{{d}S_{3} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\tau _{xy}^{z} {d}S_{3}^{z} {d}z} = -\dfrac{1}{T_{2} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\tau_{xy}^{z} \left( {T_{2} +z\omega_{22}^{2} } \right){d}z} \end{eqnarray}$以下直接写为
(101) $\begin{eqnarray} &&M_{1y} =\dfrac{1}{T_{2} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\sigma _{x}^{z} \left( {T_{2} +z\omega_{22}^{2} } \right){d}z} \end{eqnarray}$(102) $\begin{eqnarray} \left.\begin{array}{l} F_{1x} =\dfrac{1}{T_{2} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\sigma_{x}^{z} \left( {T_{2} +z\omega_{22}^{2} } \right){d}z} \\ F_{1y} =\dfrac{1}{T_{2} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\tau_{xy}^{z} \left( {T_{2} +z\omega_{22}^{2} } \right){d}z} \\ F_{1z} =\dfrac{1}{T_{2} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\tau_{xz}^{z} \left( {T_{2} +z\omega_{22}^{2} } \right){d}z} \end{array}\right\} \end{eqnarray}$其中$\omega_{22}^{2} =-\sin \phi \omega_{12}^{1} +\cos \phi \omega_{12}^{2} $, 在一阶近似下可取$\omega_{22}^{2} =-\omega_{12}^{1} $,还用到了式(31).
(103) $\begin{eqnarray} && M_{3x} =-\dfrac{1}{{d}S_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\sigma_{y}^{z} {d}S_{1}^{z} {d}z}= -\dfrac{1}{T_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\sigma_{y}^{z} \left( {T_{1} +z\omega_{11}^{2} } \right){d}z} \end{eqnarray}$以下直接写为
(104) $\begin{eqnarray} \label{eq104} &&M_{3y} =\dfrac{1}{T_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {z\tau_{yx}^{z} \left( {T_{1} +z\omega_{11}^{2} } \right){d}z} \end{eqnarray}$(105) $\begin{eqnarray} \left.\begin{array}{l} F_{3x} =\dfrac{1}{T_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\tau_{yx}^{z} \left( {T_{1} +z\omega_{11}^{2} } \right){d}z}\\ F_{3y} =\dfrac{1}{T_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\sigma_{y}^{z} \left( {T_{1} +z\omega_{11}^{2} } \right){d}z} \\ F_{3z} =\dfrac{1}{T_{1} }\displaystyle\int_{-{h}/{2}}^{{h}/{2}} {\tau_{yz}^{z} \left( {T_{1} +z\omega_{11}^{2} } \right){d}z} \end{array}\right\} \end{eqnarray}$可以验证, 内力主矩和主矢表达式与经典的表达是一致的
[24 -26 ] .
5.2 本构方程 由式(100) ~式(105), 得到本构方程
(106) $\begin{eqnarray} && M_{1x} =\dfrac{\omega_{22}^{2} }{T_{2} }I_{y} \tau_{{e}xy} +\dfrac{\left( {1-\mu } \right)}{2}D\cdot \left[ {\left( {\dfrac{\omega_{11}^{1} }{T_{1} }-\dfrac{\omega_{11}^{01} }{T_{10} }} \right)} \right.-\left. {\left({\dfrac{\omega_{12}^{2} }{T_{2} }-\dfrac{\omega_{12}^{02} }{T_{20} }} \right)} \right]\\ \end{eqnarray}$(107) $\begin{eqnarray} && M_{1y} =\dfrac{\omega_{22}^{2} }{T_{2} }I_{y} \sigma_{{e}x} + D \left[ \dfrac{1}{T_{10}}\left( \dfrac{T_{1} }{T_{10} }\omega_{11}^{2} -\omega_{11}^{02} \right)+\right. \frac{\mu }{T_{20}}\left( {\dfrac{T_{2} }{T_{20} }\omega_{22}^{2} -\omega_{22}^{02} } \right]\\ \end{eqnarray}$(108a) $\begin{eqnarray} \label{eq108} &&F_{1x} =h\sigma_{{e}x} -D\dfrac{\omega_{22}^{2} }{T_{2} }\left[\dfrac{1}{T_{10} }\left( {\dfrac{T_{1} }{T_{10} }\omega_{11}^{2} -\omega_{11}^{02} } \right)+ \right. \left.\dfrac{\mu }{T_{20} }\left({\dfrac{T_{2} }{T_{20} }\omega_{22}^{2} -\omega_{22}^{02} } \right)\right]\\ \end{eqnarray}$(108b) $\begin{eqnarray} &&F_{1y} =h\tau_{{e}xy} -\dfrac{\left( {1-\mu } \right)}{2}D\dfrac{\omega_{22}^{2} }{T_{2} }\cdot \left[ {-\left( {\dfrac{\omega_{11}^{1} }{T_{1} }-\dfrac{\omega_{11}^{01} }{T_{10} }} \right)+\left( {\dfrac{\omega _{12}^{2} }{T_{2} }-\dfrac{\omega_{12}^{02} }{T_{20} }} \right)} \right] \end{eqnarray}$$(109) $\begin{eqnarray} \label{eq109} &&M_{3x} =-\dfrac{\omega_{11}^{2}}{T_{1}}I_{x} \sigma_{{e}y} -D\left[\dfrac{1}{T_{20}}\left( \dfrac{T_{2}}{T_{20}}\omega_{22}^{2} -\omega_{22}^{02} \right) + \right. \left.\dfrac{\mu}{T_{10}}\left(\dfrac{T_{1}}{T_{10}}\omega_{11}^{2} -\omega_{11}^{02} \right) \right]\\ \end{eqnarray}$(110) $\begin{eqnarray} &&M_{3y}=\dfrac{\omega_{11}^{2}}{T_{1}}I_{x} \tau_{{e}yx} -\dfrac{\left( {1-\mu } \right)}{2}D\cdot \left[ \left(\dfrac{\omega_{11}^{1} }{T_{1} }-\dfrac{\omega_{11}^{01} }{T_{10} } \right)-\left( \dfrac{\omega_{12}^{2} }{T_{2} }-\dfrac{\omega_{12}^{02} }{T_{20}} \right) \right] \\ \end{eqnarray}(111) $\begin{eqnarray} &&\left.\begin{array}{l} F_{3x} =h\tau_{{e}yx} -\dfrac{\left( {1-\mu } \right)}{2}D\dfrac{\omega_{11}^{2} }{T_{1} }\cdot \\ \qquad \left[ {\left( {\dfrac{\omega_{11}^{1} }{T_{1} }-\dfrac{\omega _{11}^{01} }{T_{10} }} \right)-\left( {\dfrac{\omega_{12}^{2} }{T_{2} }-\dfrac{\omega_{12}^{02} }{T_{20} }} \right)} \right] \\ F_{3y} =h\sigma_{{e}y} +D\dfrac{\omega_{11}^{2} }{T_{1} }\left[{\dfrac{1}{T_{20} }\left( {\dfrac{T_{2} }{T_{20} }\omega_{22}^{2} -\omega_{22}^{02} } \right)} \cdot \right. \\ \qquad \left. \dfrac{\mu }{T_{10} }\left( {\dfrac{T_{1} }{T_{10} }\omega_{11}^{2} -\omega_{11}^{02} } \right) \right] \end{array}\right\} \end{eqnarray}$式中
(112) $\begin{eqnarray} \label{eq106} I_{x} =I_{y} =\dfrac{h^{3}}{12}, \quad D=\dfrac{Eh^{3}}{12\left( {1-\mu^{2}} \right)} \end{eqnarray}$其中$D$为抗弯刚度.
根据直法线假定, $F_{1z} ,F_{3z} $是独立变量.本构方程也可以在应变的一次近似下表达, 这里从略.
6 平衡方程和动力学比拟 6.1 平衡方程 设沿弹性薄壳中面作用有随体或固定的分布载荷
(113) $\begin{eqnarray} {f}={f}\left( {q_{1} ,q{ }_{2}} \right) \end{eqnarray}$列出变形后微分单元的平衡方程并整理得
(114) $\begin{eqnarray} \label{eq114} &&\dfrac{\partial \left( {{F}_{1} {d}S_{3} } \right)}{\partial q_{1} }{d}q_{1} +\dfrac{\partial \left( {{F}_{3} {d}S_{1} } \right)}{\partial q_{3} }{d}q_{3} +{f}{d}S_{1} {d}S_{3} ={\bf0}\qquad \end{eqnarray}$(115) $\begin{eqnarray} && \dfrac{\partial \left( {{M}_{1} {d}S_{3} } \right)}{\partial q_{1} }{d}q_{1} +\dfrac{\partial \left( {{M}_{3} {d}S_{1} } \right)}{\partial q_{3} }{d}q_{3} + \left( {{T}_{1}^{0} \times {F}_{1} +{B}_{1}^{0} \times {F}_{3} } \right){d}S_{1} {d}S_{3} ={\bf0} \end{eqnarray}$将式(3)、式(9)和式(97)代入, 化作
(116) $\begin{eqnarray} && \dfrac{\partial \left( {{F}_{1} T_{2} \sin \phi } \right)}{\partial q_{1} }+\dfrac{T_{2} \sin \phi }{B_{1} }\dfrac{\partial \left( {{F}_{3} T_{1} } \right)}{\partial q_{3} } + T_{1} T_{2} \sin \phi {f}={\bf0} \end{eqnarray}$(117) $\begin{eqnarray} && \dfrac{\partial \left( {{M}_{1} T_{2} \sin \phi } \right)}{\partial q_{1} }+\dfrac{T_{2} \sin \phi }{B_{1} }\dfrac{\partial \left( {{M}_{3} T_{1} } \right)}{\partial q_{3} }+ \left( {{T}_{1}^{0} \times {F}_{1} +{B}_{1}^{0} \times {F}_{3} } \right)T_{1} T_{2} \sin \phi ={\bf0} \end{eqnarray}$这形式上与Kirchhoff方程和Euler方程相似,但多了一个自变量.与经典薄壳平衡微分方程也是一致的
[24 -26 ] .
值得指出式(117)的${N}^{0} $轴投影式不是独立的.不失一般性,当坐标线$q_{i} $是曲率线时, $\phi ={\pi /2}$, ${T}_{2}^{0} ={B}_{1}^{0} $, 且有式(\ref{eq23})知, $\omega_{11}^{1} =\omega_{12}^{2} =0$,可以证明式(117)沿${N}^{0} $的投影式是恒等式.需要注意的是,变形后的中面位形是待求的.
静力方程式(116)和式(117)是2自变量的偏微分方程组, 与约束方程(46)联立,方程数位8, 所含的未知量是$\psi ,\theta ,\varphi_{1} ,\phi ,F_{1z} ,F_{3z},T_{1} ,T_{2} $, 个数相等.因此, 方程组封闭.值得一提的是,这里的约束方程是运算和变形规则要求, 因而无需对应的约束力,文献上称此类约束为内约束.
由复合函数的求导规则和式(9), 有
(118) $\begin{eqnarray} \dfrac{1}{B_{1} }\dfrac{\partial }{\partial q_{3} }=-\dfrac{1}{T_{1} }\cot \phi \dfrac{\partial }{\partial q_{1} }+\dfrac{1}{T_{2} }\dfrac{1}{\sin \phi }\dfrac{\partial }{\partial q_{2} } \end{eqnarray}$据此, 可将对$q_{3}$的偏导数化作对$q_{i} $的偏导数.
借助式(118), 并用相对轴系$\left( {{T}_{1}^{0} ,{B}_{1}^{0} ,{N}^{0}} \right)$的导数, 写作
(119) $\begin{eqnarray} && \dfrac{1}{T_{2} }\dfrac{\tilde{{\partial }}\left( {{F}_{1} \sin \phi T_{2} } \right)}{\partial q_{1} }-\dfrac{\cos \phi }{T_{1} }\dfrac{\tilde{{\partial }}\left( {{F}_{3} T_{1} } \right)}{\partial q_{1} } +\dfrac{1}{T_{2} }\dfrac{\tilde{{\partial }}\left( {{F}_{3} T_{1} } \right)}{\partial q_{2} }+ {\omega }_{11} \times \left( {{F}_{1} \sin \phi -{F}_{3} \cos \phi } \right) +\dfrac{T_{1} }{T_{2} }\left( {{\omega }_{12} \times {F}_{3} } \right)+ T_{1} \sin \phi {f}={\bf0} \end{eqnarray}$(120) $\begin{eqnarray} &&\dfrac{1}{T_{2} }\dfrac{\tilde{{\partial }}\left( {{M}_{1} T_{2} \sin \phi } \right)}{\partial q_{1} }-\dfrac{\cos \phi }{T_{1} }\dfrac{\tilde{{\partial }}\left( {{M}_{3} T_{1} } \right)}{\partial q_{1} }+\dfrac{1}{T_{2} }\dfrac{\tilde{{\partial }}\left( {{M}_{3} T_{1} } \right)}{\partial q_{2} } + {\omega }_{11} \times \left( {{M}_{1} \sin \phi -{M}_{3} \cos \phi } \right)+\dfrac{T_{1} }{T_{2} }\left( {{\omega }_{12} \times {M}_{3} } \right) + \left( {{T}_{1}^{0} \times {F}_{1} +{B}_{1}^{0} \times {F}_{3} } \right)T_{1} \sin \phi ={\bf0} \end{eqnarray}$其中顶标波浪号表示相对轴系$\left( {{T}_{1}^{0} ,{B}_{1}^{0} ,{N}^{0}} \right)$的导数.
6.2 弹性薄壳的Kirchhoff动力学比拟 式(115)与定点转动刚体的Euler方程和弹性细杆Kirchhoff方程有一定相似性.按照Kirchhoff动力学比拟,弹性薄壳静力学与刚体动力学有很好的对应关系, 主要有: 时间坐标 $t$ -中面广义弧坐标$q_{i}$,Euler角$\psi$, $\theta$, $\varphi$ -- Euler角$\psi$, $\theta$, $\varphi_{i}$, 角速度${\varOmega}$ -弯扭度${\omega }_{ij} $; 刚体的运动过程-弹性薄壳的位形, 动量矩-内力主矩等. 弹性薄壳可以取刚体的姿态坐标和Lam$\acute{e}$系数以及厚度方向的切向分布力为未知函数,按照求解刚体运动的思路求解弹性薄壳的位形.
7 算例 设薄板宽度为$b$, 长度为$l$, 厚度为$h$, 不计自重. 在板两端作用分布力偶
(121) $\begin{eqnarray} \left. {{m}} \right|_{q_{2} =0} =-m{e}_{\xi } , \left. {{m}} \right|_{q_{2} =l} =m{e}_{\xi } \end{eqnarray}$如
图7 所示.变形前弹性中面的矢径为
(122) $\begin{eqnarray} {r}=q_{1} {e}_{\xi } +q_{2} {e}_{\eta } \end{eqnarray}$Lam$\acute{e}$系数$T_{i0} =1$,轴系基矢量为
(123) $$\begin{eqnarray} {T}_{10}^{0} ={e}_{\xi } ,\\ {B}_{0}^{0} ={T}_{20}^{0} ={e}_{\eta } ,\\ {N}_{0} ={e}_{\zeta } \end{eqnarray}$弯扭度${\omega }_{ij}^{0} =0$.
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生成PPT 图7变形前后的弹性薄板 Fig.7Thin elastic plate before and after deformation 变形后中面轴系$\left( {{T}_{i}^{0} ,{B}_{i}^{0} ,{N}^{0} } \right)$姿态的Euler角为$\psi ,\theta ,\varphi $,坐标线夹角为$\phi $.计算薄板满足
(124) $\begin{eqnarray} \psi =\varphi_{1} =0, \phi =\dfrac{\pi }{2}, T_{1} =T_{2} =1 \end{eqnarray}$的一个解. 将式(124)代入式(120)在${T}_{1}^{0} ,{B}_{1}^{0} $方向投影式,
得到
(125) $\begin{eqnarray} F_{1z} =F_{3z} =0 \end{eqnarray}$${N}^{0} $方向的投影式为恒等式. 再将式(124)和式(125)代入式(119), 解得
(126) $\begin{eqnarray} \left.\begin{array}{l} \dfrac{\partial \theta }{\partial q_{2} }\dfrac{\partial^{2}\theta }{\partial q_{1} \partial q_{2} }=0 \\ \dfrac{\partial \theta }{\partial q_{1} }\dfrac{\partial^{2}\theta }{\partial q_{1} \partial q_{2} }+\dfrac{\partial \theta }{\partial q_{2} }\dfrac{\partial^{2}\theta }{\partial q_{1}^{2} }=0 \\ \dfrac{\partial \theta }{\partial q_{1} }\dfrac{\partial \theta }{\partial q_{2} }=0 \end{array}\right\} \end{eqnarray}$考虑到约束方程式(46), 解为
(127) $\begin{eqnarray} \dfrac{\partial \theta }{\partial q_{1} }=0 \end{eqnarray}$积分得
(128) $\begin{eqnarray} \theta =\theta \left( {q_{2} } \right) \end{eqnarray}$此时的弯扭度和中面的应力为
(129) $\begin{eqnarray} &&\left.\begin{array}{l} {\omega }_{11} =0,{\omega }_{12} =\dfrac{\partial \theta }{\partial q_{2} }{T}_{1}^{0} \\ {\omega }_{21} =0,{\omega }_{22} =-\dfrac{\partial \theta }{\partial q_{2} }{B}_{2}^{0} \\ \end{array}\right\} \end{eqnarray}$(130) $\begin{eqnarray} &&\sigma_{{e}x} =\sigma_{ey} =\tau_{{e}xy} =0 \end{eqnarray}$由式(47)知, 此时${T}_{1}^{0} ={e}_{\xi } $, 内力边界条件表为
(131) $\begin{eqnarray} \left.\begin{array}{l} \left. {M_{1y} } \right|_{q_{1} =0} =\left. {M_{1y} } \right|_{q_{1} =b} =0 \\ \left. {M_{3x} } \right|_{q_{2} =0} =\left. {M_{3x} } \right|_{q_{2} =l} =m \\ \end{array}\right\} \end{eqnarray}$由式(107)得到
(132) $\begin{eqnarray} \omega_{11}^{2} +\mu \omega_{22}^{2} =0 \end{eqnarray}$注意到$\phi = {\pi }/{2}$和式(129), 式(109)化作
(133) $\begin{eqnarray} -D\left( {\omega_{22}^{2} +\mu \omega_{11}^{2} } \right)=D\left( {1-\mu ^{2}} \right)\dfrac{\partial \theta }{\partial q_{2} }=m \end{eqnarray}$解得
(134) $\begin{eqnarray} \dfrac{\partial \theta }{\partial q_{2} }=\dfrac{m}{D\left( {1-\mu^{2}} \right)}=12\dfrac{m}{Eh^{3}} \end{eqnarray}$积分得
(135) $\begin{eqnarray} \theta =12\dfrac{m}{Eh^{3}}q_{2} +C \end{eqnarray}$其中$C$为积分常数.设$\left. \theta \right|_{q_{2} ={l}/{2}} =0$,导出$C=-{6ml}/({Eh^{3}})$.
(136) $\begin{eqnarray} \theta =12\dfrac{m}{Eh^{3}}\left( {q_{2} -\dfrac{l}{2}} \right) \end{eqnarray}$由式(53)得到变形后的中面偏微分方程
(137) $\begin{eqnarray} \left.\begin{array}{l} \dfrac{\partial \xi }{\partial q_{1} }=1, \dfrac{\partial \eta }{\partial q_{1} }=0, \dfrac{\partial \zeta }{\partial q_{1} }=0 \\ \dfrac{\partial \xi }{\partial q_{2} }=0, \dfrac{\partial \eta }{\partial q_{2} }=\mbox{cos}\theta , \dfrac{\partial \zeta }{\partial q_{2} }=\mbox{sin}\theta \end{array}\right\} \end{eqnarray}$在边界条件$\left. \xi \right|_{q_{1} =0} =0,\left. \eta \right|_{q_{2}={l}/{2}} =\dfrac{l}{2},\left. \zeta \right|_{q_{2} ={l}/{2}}=0$下的解为
(138) $\begin{eqnarray} \left.\begin{array}{l} \xi =q_{1}\\ \eta =\dfrac{1}{K}\sin K\left( {q_{2} -\dfrac{l}{2}} \right)+\dfrac{l}{2} \\ \zeta =\dfrac{1}{K}\left[ {1-\cos K\left( {q_{2} -\dfrac{l}{2}} \right)}\right]\ \end{array}\right\} \end{eqnarray}$其中, $K=12{m}/({Eh^{3}})$. 这就是薄板在两边分布力偶作用下的中面方程.是一圆弧面,圆心轴为平行于$\xi $轴的直线段$\left( {q_{1} ,{l}/{2},{1}/{K}}\right)$, 半径为${1}/{K}$. 这结论是熟知的,如
图8 所示.
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生成PPT 图8弹性中面的位形 Fig.8Configuration of elastic mid-splane 结论 用中面轴系的姿态坐标和弯扭度, 以及Lam$\acute{e}$系数表达了弹性薄壳中面的位形、一点的应变状态和应力状态、以及截面上的分布主矩和分布主矢, 得到的平衡偏微分方程与定点转动刚体的Euler方程和弹性细杆Kirchhoff方程有一定的相似性.使中面位形成为广义弧坐标历程.将弹性杆的Kirchhoff动力学比拟方法推广到弹性薄壳.
在Kirchhoff动力学比拟下, 弹性薄壳的位形空间是是一个6维空间, 因为双自变量,且存在3个非完整约束, 因此自由度为9.可以引入完整和非完整约束的概念,并形成弹性薄壳的分析力学方法.
[1] Kirchhoff G Journal F$\ddot{u}$r Die Reine Und Angewandte Mathematic , 1859 , 56: 285 -313 [本文引用: 1] [2] Kirchhoff G Vorlesung $\ddot{u}$eber mathematische Physik, Mechanik Leipzig , 1874 [本文引用: 1] [3] Love AEH New York: Dover , 1927 [本文引用: 1] [4] 刘延柱 . 弹性细杆的非线性力学——DNA力学模型的理论基础 . 北京: 清华大学出版社, 斯普林格出版社, 2006 . [本文引用: 6] (Liu Yanzhu Nonlinear Mechanics of Thin Elastic Rod——Theoritical Basis of Mechanical Model of DNA. Beijing: Tsinghua University Press, Springer, 2006 (in Chinese)) [本文引用: 6] [5] 刘延柱 . 弹性杆基因模型的力学问题力学与实践 , 2003 , 25(1 ): 1 -5 . [本文引用: 1] (Liu Yanzhu Mechanics in Engineenring , 2003 , 25(1 ): 1 -5 (in Chinese)) [本文引用: 1] [6] Coleman B Swigon D Philosophical Transactions Mathematical Physical & Engineering Sciences ,2004 , A362: 1281 -1299 [本文引用: 1] [7] 薛纭 , 刘延柱 , 陈立群 . 超细长弹性杆的分析力学问题力学学报 , 2005 , 37(4 ): 485 -493 . [本文引用: 1] (Xue Yun Liu Yanzhu Chen Liqun Chinese Journal of Theoretical Applied Mecanics , 2005 , 37: 485 -493 (in Chinese)) [本文引用: 1] [8] Xue Y Shang HL Chinese Physics Letters , 2009 , 26(7 ): 074501 -3 [本文引用: 1] [9] 薛纭 , 曲佳乐 , 陈立群 . Cosserat生长弹性杆动力学的Gauss最小拘束原理应用数学和力学 , 2015 , 36(7 ): 700 -709 . [本文引用: 1] (Xue Yun Qu Jiale Chen Liqun Applied Mathematics and Mechanics , 2015 , 36(7 ): 700 -709 (in Chinese)) [本文引用: 1] [10] Wang P Xue Y Liu YL Chinese Physics B , 2013 , 22(10 ): 104503 -6 [本文引用: 1] [11] 薛纭 , 陈立群 , 刘延柱 . Kirchhoff方程的相对常值特解及其Lyapunov稳定性物理学报 , 2004 , 53(12 ): 4029 -4036 . [本文引用: 1] (Xue Yun Chen Liqun Liu Yanzhu Acta Physica Sinica , 2004 , 53(12 ): 4029 -4036 (in Chinese)) [本文引用: 1] [12] Leung AYT Kuang JL Lim CW et al .Spatial chaos of buckled elastica by the Kirchhoff analogy of a gyrostatComputers and Structures , 2005 , 83: 2395 -2413 [本文引用: 1] [13] 曹登庆 , 白坤朝 , 丁虎 等 .大型柔性航天器动力学与振动控制研究进展力学学报 , 2019 , 51(1 ): 1 -13 . [本文引用: 1] (Cao Dengqing Bai Kunchao Ding Hu et al .Advances in dynamics and vibration control of large-scale flexible spacecraftChinese Journal of Theoretical and Applied Mechanics , 2019 , 51(1 ): 1 -13 (in Chinese)) [本文引用: 1] [14] 孙加亮 , 田强 , 胡海岩 . 多柔体系统动力学建模与优化研究进展力学学报 , 2019 , 51(6 ): 1565 -1586 . [本文引用: 1] (Sun Jialiang Tian Qiang Hu Haiyan Chinese Journal of Theoretical and Applied Mechanics , 2019 , 51(6 ): 1565 -1586 (in Chinese)) [本文引用: 1] [15] 章孝顺 , 章定国 , 洪嘉振 . 考虑曲率纵向变形效应的大变形柔性梁刚柔耦合动力学建模与仿真力学学报 , 2016 ,48(3 ): 692 -701 . [本文引用: 1] (Zhang Xiaoshun Zhang Dingguo Hong Jiazhen Chinese Journal of Theoretical and Applied Mechanics , 2016 , 48(3 ): 692 -701 (in Chinese)) [本文引用: 1] [16] Wallrapp O Schwertassek R International Journal for Numerical Methods in Engineering , 1991 , 32: 1833 -1850 [本文引用: 1] [17] Yoo HH Chung J Journal of Sound and Vibration , 2001 , 239(1 ): 123 -137 [本文引用: 1] [18] Zhang DJ Liu CQ Huston RL Mechanics of Structures and Machines , 1995 , 23(3 ): 419 -438 [本文引用: 1] [19] Dmitrochenko ON Pogorelov DY Multibody System Dynamics , 2003 , 10: 17 -43 [本文引用: 1] [20] Yoo WS Kim MS Kim HW et al .Developments of multibody system dynamics: Domputer simulations and experimentsMultibody System Dynamics , 2007 , 18: 35 -58 [本文引用: 1] [21] Pimenta PM Campello EMB International Journal Numerical Methods Engineering , 2009 , 78: 1094 -1112 [本文引用: 1] [22] 陈至达 . 杆、板、壳大变形理论 . 北京: 科学出版社, 1994 : 106. [本文引用: 1] (Chen Zhida Large Deformation Theory of Rods, Plates and Shells . Beijing: Science Press, 1994 : 106(in Chinese)) [本文引用: 1] [23] 胡海岩 . 梁在固有振动中的对偶关系力学学报 , 2020 , 52(1 ): 139 -149 . [本文引用: 1] (Hu Haiyan Chinese Journal of Theoretical and Applied Mechanics , 2020 , 52(1 ): 139 -149 (in Chinese)) [本文引用: 1] [24] 黄克智 . 板壳理论 . 北京: 清华大学出版社, 1987 . [本文引用: 3] (Huang Kezhi Theory of Plates and Shells. Bejing: Tsinghua University Press, 1987 (in Chinese)) [本文引用: 3] [25] 刘鸿文 , 林建兴 , 曹曼玲 . 板壳理论 . 杭州: 浙江大学出版社, 1987 .(Liu Hongwen Lin Jianxing Cao Manlin Theory of Plates and Shells. Hangzhou: Zhejiang University Press, 1987 (in Chinese)) [26] S.铁摩辛柯 , S.沃诺斯基 . 板壳理论.《板壳理论》翻译组译 . 北京: 科学出版社, 1977 . [本文引用: 3] (Timoshenko S Woinowsky-Krieger S McGraw-Hill Book Company Inc , 1959 (in Chinese)) [本文引用: 3] [27] Cao DQ Tucker RW International Journal of Solids and Structure , 2008 , 45(2 ): 460 -477 [本文引用: 1] [28] 吴大任 . 微分几何讲义 . 北京: 高等教育出版社, 1959 . [本文引用: 1] (Wu Daren Lecture Notes on Differential Geometry. Beijing: Higher Education Press, 1959 (in Chinese)) [本文引用: 1] [29] 刘延柱 . 高等动力学(第2版) . 北京: 高等教育出版社, 2016 . [本文引用: 3] (Liu Yanzhu Advanced Dynamics (Second Edition). Beijing: Higher Education Press, 2016 (in Chinese)) [本文引用: 3] [30] 武际可 , 王敏中 , 王炜 . 弹性力学引论(修订版) . 北京: 北京大学出版社, 1981 . [本文引用: 2] (Wu Jike Wang Minzhong Wang Wei Introduction to Elastic Mechanics (Revised Edition). Beijing: Beijing University Press, 1981 (in Chinese)) [本文引用: 2] 
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新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
新窗口打开|下载原图ZIP|生成PPT
