The Kirchhoff–Love theory of plates is a two-dimensional mathematical model that is used to determine the stresses and deformations in thin plates subjected to forces and moments. This theory is an extension of Euler-Bernoulli beam theory and was developed in 1888 by Love using assumptions proposed by Kirchhoff. The theory assumes that a mid-surface plane can be used to represent a three-dimensional plate in two-dimensional form. The following kinematic assumptions that are made in this theory:

Assumed displacement field

Let the position vector of a point in the undeformed plate be \mathbf{x}. Then The vectors form a Cartesian basis with origin on the mid-surface of the plate, x_1 and x_2 are the Cartesian coordinates on the mid-surface of the undeformed plate, and x_3 is the coordinate for the thickness direction. Let the displacement of a point in the plate be. Then This displacement can be decomposed into a vector sum of the mid-surface displacement u^0_\alpha and an out-of-plane displacement w^0 in the x_3 direction. We can write the in-plane displacement of the mid-surface as Note that the index \alpha takes the values 1 and 2 but not 3. Then the Kirchhoff hypothesis implies that If are the angles of rotation of the normal to the mid-surface, then in the Kirchhoff-Love theory Note that we can think of the expression for u_\alpha as the first order Taylor series expansion of the displacement around the mid-surface.

Quasistatic Kirchhoff-Love plates

The original theory developed by Love was valid for infinitesimal strains and rotations. The theory was extended by von Kármán to situations where moderate rotations could be expected.

Strain-displacement relations

For the situation where the strains in the plate are infinitesimal and the rotations of the mid-surface normals are less than 10° the strain-displacement relations are where \beta=1, 2 as \alpha. Using the kinematic assumptions we have Therefore, the only non-zero strains are in the in-plane directions.

Equilibrium equations

The equilibrium equations for the plate can be derived from the principle of virtual work. For a thin plate under a quasistatic transverse load q(x) pointing towards positive x_3 direction, these equations are where the thickness of the plate is 2h. In index notation, where are the stresses. !Derivation of equilibrium equations for small rotations where the thickness of the plate is 2h and the stress resultants and stress moment resultants are defined as Integration by parts leads to The symmetry of the stress tensor implies that. Hence, Another integration by parts gives For the case where there are no prescribed external forces, the principle of virtual work implies that \delta U =0. The equilibrium equations for the plate are then given by If the plate is loaded by an external distributed load q(x) that is normal to the mid-surface and directed in the positive x_3 direction, the external virtual work due to the load is The principle of virtual work then leads to the equilibrium equations

Boundary conditions

The boundary conditions that are needed to solve the equilibrium equations of plate theory can be obtained from the boundary terms in the principle of virtual work. In the absence of external forces on the boundary, the boundary conditions are Note that the quantity is an effective shear force.

Constitutive relations

The stress-strain relations for a linear elastic Kirchhoff plate are given by Since and \sigma_{33} do not appear in the equilibrium equations it is implicitly assumed that these quantities do not have any effect on the momentum balance and are neglected. The remaining stress-strain relations, in matrix form, can be written as Then, and The ** extensional stiffnesses** are the quantities The ** bending stiffnesses** (also called flexural rigidity) are the quantities The Kirchhoff-Love constitutive assumptions lead to zero shear forces. As a result, the equilibrium equations for the plate have to be used to determine the shear forces in thin Kirchhoff-Love plates. For isotropic plates, these equations lead to Alternatively, these shear forces can be expressed as where

Small strains and moderate rotations

If the rotations of the normals to the mid-surface are in the range of 10^{\circ} to 15^\circ, the strain-displacement relations can be approximated as Then the kinematic assumptions of Kirchhoff-Love theory lead to the classical plate theory with von Kármán strains This theory is nonlinear because of the quadratic terms in the strain-displacement relations. If the strain-displacement relations take the von Karman form, the equilibrium equations can be expressed as

Isotropic quasistatic Kirchhoff-Love plates

For an isotropic and homogeneous plate, the stress-strain relations are where \nu is Poisson's Ratio and E is Young's Modulus. The moments corresponding to these stresses are In expanded form, where for plates of thickness H = 2h. Using the stress-strain relations for the plates, we can show that the stresses and moments are related by At the top of the plate where, the stresses are

Pure bending

For an isotropic and homogeneous plate under pure bending, the governing equations reduce to Here we have assumed that the in-plane displacements do not vary with x_1 and x_2. In index notation, and in direct notation which is known as the biharmonic equation. The bending moments are given by !Derivation of equilibrium equations for pure bending and the stress-strain relations are Then, and Differentiation gives and Plugging into the governing equations leads to Since the order of differentiation is irrelevant we have, , and. Hence In direct tensor notation, the governing equation of the plate is where we have assumed that the displacements u^0_1,u^0_2 are constant.

Bending under transverse load

If a distributed transverse load q(x) pointing along positive x_3 direction is applied to the plate, the governing equation is. Following the procedure shown in the previous section we get In rectangular Cartesian coordinates, the governing equation is and in cylindrical coordinates it takes the form Solutions of this equation for various geometries and boundary conditions can be found in the article on bending of plates. !Derivation of equilibrium equations for transverse loading where q is a distributed transverse load (per unit area). Substitution of the expressions for the derivatives of into the governing equation gives Noting that the bending stiffness is the quantity we can write the governing equation in the form In cylindrical coordinates , For symmetrically loaded circular plates, w = w(r), and we have

Cylindrical bending

Under certain loading conditions a flat plate can be bent into the shape of the surface of a cylinder. This type of bending is called cylindrical bending and represents the special situation where. In that case and and the governing equations become

Dynamics of Kirchhoff-Love plates

The dynamic theory of thin plates determines the propagation of waves in the plates, and the study of standing waves and vibration modes.

Governing equations

The governing equations for the dynamics of a Kirchhoff-Love plate are where, for a plate with density , and !Derivation of equations governing the dynamics of Kirchhoff-Love plates The total kinetic energy (more precisely, action of kinetic energy) of the plate is given by Therefore, the variation in kinetic energy is We use the following notation in the rest of this section. Then For a Kirchhof-Love plate Hence, Define, for constant \rho through the thickness of the plate, Then Integrating by parts, The variations and \delta w^0 are zero at t = 0 and t = T. Hence, after switching the sequence of integration, we have Integration by parts over the mid-surface gives Again, since the variations are zero at the beginning and the end of the time interval under consideration, we have For the dynamic case, the variation in the internal energy is given by Integration by parts and invoking zero variation at the boundary of the mid-surface gives If there is an external distributed force q(x,t) acting normal to the surface of the plate, the virtual external work done is From the principle of virtual work, or more precisely, Hamilton's principle for a deformable body, we have. Hence the governing balance equations for the plate are Solutions of these equations for some special cases can be found in the article on vibrations of plates. The figures below show some vibrational modes of a circular plate.

Isotropic plates

The governing equations simplify considerably for isotropic and homogeneous plates for which the in-plane deformations can be neglected. In that case we are left with one equation of the following form (in rectangular Cartesian coordinates): where D is the bending stiffness of the plate. For a uniform plate of thickness 2h, In direct notation For free vibrations, the governing equation becomes !Derivation of dynamic governing equations for isotropic Kirchhoff-Love plates 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 The governing equation for an isotropic and homogeneous plate of uniform thickness 2h in the absence of in-plane displacements is Differentiation of the expressions for the moment resultants gives us Plugging into the governing equations leads to Since the order of differentiation is irrelevant we have. Hence If the flexural stiffness of the plate is defined as we have For small deformations, we often neglect the spatial derivatives of the transverse acceleration of the plate and we are left with Then, in direct tensor notation, the governing equation of the plate is