The vibration of plates is a special case of the more general problem of mechanical vibrations. The equations governing the motion of plates are simpler than those for general three-dimensional objects because one of the dimensions of a plate is much smaller than the other two. This suggests that a two-dimensional plate theory will give an excellent approximation to the actual three-dimensional motion of a plate-like object, and indeed that is found to be true.
There are several theories that have been developed to describe the motion of plates. The most commonly used are the Kirchhoff-Love theory and the Uflyand-Mindlin. The latter theory is discussed in detail by Elishakoff. Solutions to the governing equations predicted by these theories can give us insight into the behavior of plate-like objects both under free and forced conditions. This includes
the propagation of waves and the study of standing waves and vibration modes in plates. The topic of plate vibrations is treated in books by Leissa, Gontkevich, Rao, Soedel, Yu, Gorman and Rao.
The governing equations for the dynamics of a Kirchhoff-Love plate are
where are the in-plane displacements of the mid-surface of the plate, is the transverse (out-of-plane) displacement of the mid-surface of the plate, is an applied transverse load, and the resultant forces and moments are defined as
Note that the thickness of the plate is and that the resultants are defined as weighted averages of the in-plane stresses . The derivatives in the governing equations are defined as
where the Latin indices go from 1 to 3 while the Greek indices go from 1 to 2. Summation over repeated indices is implied. The coordinates is out-of-plane while the coordinates and are in plane.
For a uniformly thick plate of thickness and homogeneous mass density
For an isotropic and homogeneous plate, the stress-strain relations are
where are the in-plane strains. The strain-displacement relations
for Kirchhoff-Love plates are
Therefore, the resultant moments corresponding to these stresses are
If we ignore the in-plane displacements , the governing equations reduce to
where is the bending stiffness of the plate. For a uniform plate of thickness ,
The above equation can also be written in an alternative notation:
In solid mechanics, a plate is often modeled as a two-dimensional elastic body whose potential energy depends on how it is bent from a planar configuration, rather than how it is stretched (which is the instead the case for a membrane such as a drumhead). In such situations, a vibrating plate can be modeled in a manner analogous to a vibrating drum. However, the resulting partial differential equation for the vertical displacement w of a plate from its equilibrium position is fourth order, involving the square of the Laplacian of w, rather than second order, and its qualitative behavior is fundamentally different from that of the circular membrane drum.
For free vibrations, the external force q is zero, and the governing equation of an isotropic plate reduces to
This relation can be derived in an alternative manner by considering the curvature of the plate. The potential energy density of a plate depends how the plate is deformed, and so on the mean curvature and Gaussian curvature of the plate. For small deformations, the mean curvature is expressed in terms of w, the vertical displacement of the plate from kinetic equilibrium, as Δw, the Laplacian of w, and the Gaussian curvature is the Monge–Ampère operatorwxxwyy−w2 xy. The total potential energy of a plate Ω therefore has the form
apart from an overall inessential normalization constant. Here μ is a constant depending on the properties of the material.
The kinetic energy is given by an integral of the form
Hamilton's principle asserts that w is a stationary point with respect to variations of the total energy T+U. The resulting partial differential equation is
Plugging this assumed solution into the governing equation gives us
where is a constant and . The solution of the right hand equation is
The left hand side equation can be written as
where . The general solution of this eigenvalue problem that is
appropriate for plates has the form
where is the order 0 Bessel function of the first kind and is the order 0 modified Bessel function of the first kind. The constants and are determined from the boundary conditions. For a plate of radius with a clamped circumference, the boundary conditions are
From these boundary conditions we find that
We can solve this equation for (and there are an infinite number of roots) and from that find the modal frequencies . We can also express the displacement in the form
For a given frequency the first term inside the sum in the above equation gives the mode shape. We can find the value
of using the appropriate boundary condition at and the coefficients and from the initial conditions by taking advantage of the orthogonality of Fourier components.