Virtual work arises in the application of the principle of least action to the study of forces and movement of a mechanical system. The work of a force acting on a particle as it moves along a displacement will be different for different displacements. Among all of the possible displacements that a particle may follow, called virtual displacements, one will minimize the action, and, therefore, is the one followed by the particle by the principle of least action. The work of a force on a particle along a virtual displacement is known as the virtual work.
Historically, virtual work and the associated calculus of variations were formulated to analyze systems of rigid bodies,^{[1]} but they have also been developed for the study of the mechanics of deformable bodies.^{[2]}
Contents

History 1

Overview 2

Introduction 3

Static equilibrium 4

Law of the Lever 5

Gear train 6

Dynamic equilibrium for rigid bodies 7

Generalized inertia forces 7.1

D'Alembert's form of the principle of virtual work 7.2

Virtual work principle for a deformable body 8

Proof of Equivalence between the Principle of Virtual Work and the Equilibrium Equation 8.1

Principle of virtual displacements 8.2

Principle of virtual forces 8.3

Alternative forms 9

See also 10

References 11

Bibliography 12
History
The introduction of virtual work and the principle of least action was guided by the view that the actual movement of a body is the one in a set of "tentative" realities that minimizes a particular quantity. This idea that nature minimizes is a version of the "simplicity hypothesis" that can be traced to Aristotle.^{[3]} Another form of this hypothesis is Occam's razor which states that "it is futile to employ many principles when it is possible to employ fewer." These ideas illustrate a view of physics that nature optimizes in some way.
Gottfried Leibniz formulated Newton's laws of motion in terms of work and kinetic energy, or vis viva (living force), which are minimized as a system moves.^{[1]}^{[3]} Maupertuis adapted Leibniz's ideas as the principle of least action that nature minimizes action. But it was Euler and Lagrange who provided the mathematical foundation of the calculus of variations and applied it to the study of the statics and dynamics of mechanical systems.
Hamilton's reformulation of the principle of least action and Lagrange's equations yielded a theory of dynamics that is the foundation for modern physics and quantum mechanics.
Overview
If a force acts on a particle as it moves from point A to point B, then, for each possible trajectory that the particle may take, it is possible to compute the total work done by the force along the path. The principle of virtual work, which is the form of the principle of least action applied to these systems, states that the path actually followed by the particle is the one for which the difference between the work along this path and other nearby paths is zero (to first order). The formal procedure for computing the difference of functions evaluated on nearby paths is a generalization of the derivative known from differential calculus, and is termed the calculus of variations.
Consider a point particle that moves along a path which is described by a function r(t) from point A, where r(t = t_{0}), to point B, where r(t = t_{1}). It is possible that the particle moves from A to B along a nearby path described by r(t) + δr(t), where δr(t) is called the variation of r(t). The variation δr(t) satisfies the requirement δr(t_{0}) = δr(t_{1}) = 0. The components of the variation, δr_{1}(t), δr_{2}(t) and δr_{3}(t), are called virtual displacements. This can be generalized to an arbitrary mechanical system defined by the generalized coordinates q_{i} , i = 1, ..., n. In which case, the variation of the trajectory q_{i} (t) is defined by the virtual displacements δq_{i} , i = 1, ..., n.
Virtual work is the total work done by the applied forces and the inertial forces of a mechanical system as it moves through a set of virtual displacements. When considering forces applied to a body in static equilibrium, the principle of least action requires the virtual work of these forces to be zero.
Introduction
Consider a particle P that moves from a point A to a point B along a trajectory r(t), while a force F(r(t)) is applied to it. The work done by the force F is given by the integral

W = \int_{\mathbf{r}(t_0)=A}^{\mathbf{r}(t_1)=B}\mathbf{F}\cdot d\mathbf{r} = \int_{t_0}^{t_1}\mathbf{F}\cdot \frac{d\mathbf{r}}{dt}~dt = \int_{t_0}^{t_1}\mathbf{F}\cdot \mathbf{v}~dt,
where dr is the differential element along the curve that is the trajectory of P, and v is its velocity. It is important to notice that the value of the work W depends on the trajectory r(t).
Now consider particle P that moves from point A to point B again, but this time it moves along the nearby trajectory that differs from r(t) by the variation δr(t)=εh(t), where ε is a scaling constant that can be made as small as desired and h(t) is an arbitrary function that satisfies h(t_{0}) = h(t_{1}) = 0. Suppose the force F(r(t)+εh(t)) is the same as F(r(t)). The work done by the force is given by the integral

\bar{W} = \int_{\mathbf{r}(t_0)=A}^{\mathbf{r}(t_1)=B}\mathbf{F}\cdot d(\mathbf{r}+\epsilon \mathbf{h})=\int_{t_0}^{t_1}\mathbf{F}\cdot \frac{d(\mathbf{r}(t)+\epsilon\mathbf{h}(t))}{dt}~dt=\int_{t_0}^{t_1}\mathbf{F}\cdot (\mathbf{v}+\epsilon \dot{\mathbf{h}})~dt .
The variation of the work δW associated with this nearby path, known as the virtual work, can be computed to be

\delta W = \bar{W}W = \int_{t_0}^{t_1}(\mathbf{F}\cdot \epsilon\dot{\mathbf{h}})~dt.
If there is no constraint force, then 6 parameters are needed to completely describe the motion of P. If there are k (k ≤ 6) constraint forces, then n = (6  k) parameters are needed. Hence, we can define n generalized coordinates q_{i} (t) (i = 1, 2, ..., n), and express r(t) and δr=εh(t) in terms of the generalized coordinates. That is,

\mathbf{r}(t) = \mathbf{r}(q_1,q_2,...,q_n;t),

\mathbf{h}(t) = \mathbf{h}(q_1,q_2,...,q_n;t).
Then, the derivative of the variation δr=εh(t) is given by

\frac{d}{dt}\delta \mathbf{r} = \frac{d}{dt}\epsilon\mathbf{h} = \sum_{i=1}^n\frac{\partial \mathbf{h}}{\partial q_i}\epsilon\dot{q}_i,
then we have

\delta W = \int_{t_0}^{t_1}\left(\sum_{i=1}^n \mathbf{F}\cdot\frac{\partial\mathbf{h}}{\partial q_i}\epsilon\dot{q}_i\right)dt = \sum_{i=1}^n\left(\int_{t_0}^{t_1}\mathbf{F}\cdot\frac{\partial\mathbf{h}}{\partial q_i}\epsilon\dot{q}_i ~dt\right).
The requirement that the virtual work be zero for an arbitrary variation δr(t)=εh(t) is equivalent to the set of requirements

Q_i = \mathbf{F}\cdot \frac{\partial \mathbf{h}}{\partial q_i} = 0, \quad i=1, \ldots, n.
The terms Q_{i} are called the generalized forces associated with the virtual displacement δr.
Static equilibrium
Static equilibrium is a state in which the net force and net torque acted upon the system is zero. In other words, both linear momentum and angular momentum of the system are conserved. The principle of virtual work states that the virtual work of the applied forces is zero for all virtual movements of the system from static equilibrium. This principle can be generalised such that three dimensional rotations are included: the virtual work of the applied forces and applied moments is zero for all virtual movements of the system from static equilibrium. That is

\delta W = \sum_{i=1}^m \mathbf{F}_i \cdot \delta\mathbf{r}_i + \sum_{j=1}^n \mathbf{M}_j \cdot \delta\mathbf{\phi}_j = 0 ,
where F_{i} , i = 1, 2, ..., m and M_{j} , j = 1, 2, ..., n are the applied forces and applied moments, respectively, and δr_{i} , i = 1, 2, ..., m and δφ_{j} , j = 1, 2, ..., n are the virtual displacements and virtual rotations, respectively.
Suppose the system consists of N particles, and it has f (f ≤ 6N) degrees of freedom. It is sufficient to use only f coordinates to give a complete description of the motion of the system, so f generalised coordinates q_{k} , k = 1, 2, ..., f are defined such that the virtual movements can be expressed in terms of these generalised coordinates. That is,

\delta\mathbf{r}_i (q_1, q_2, ..., q_f; t), \quad i = 1, 2, ..., m ;

\delta\phi_j (q_1, q_2, ..., q_f; t), \quad j = 1, 2, ..., n .
The virtual work can then be reparametrised by the generalised coordinates:

\delta W = \sum_{k=1}^f \left[ \left( \sum_{i=1}^m \mathbf{F}_i \cdot \frac{\partial \mathbf{r}_i}{\partial q_k} + \sum_{j=1}^n \mathbf{M}_j \cdot \frac{\partial \mathbf{\phi}_j}{\partial q_k} \right) \delta q_k \right] = \sum_{k=1}^f Q_k \delta q_k ,
where the generalised forces Q_{k} are defined as

Q_k = \sum_{i=1}^m \mathbf{F}_i \cdot \frac{\partial \mathbf{r}_i}{\partial q_k} + \sum_{j=1}^n \mathbf{M}_j \cdot \frac{\partial \mathbf{\phi}_j}{\partial q_k} , \quad k = 1, 2, ..., f .
Kane^{[4]} shows that these generalised forces can also be formulated in terms of the ratio of time derivatives. That is,

Q_k = \sum_{i=1}^m \mathbf{F}_i \cdot \frac{\partial \mathbf{v}_i}{\partial \dot{q}_k} + \sum_{j=1}^n \mathbf{M}_j \cdot \frac{\partial \mathbf{\omega}_j}{\partial \dot{q}_k} , \quad k = 1, 2, ..., f .
The principle of virtual work requires that the virtual work done on a system by the forces F_{i} and moments M_{j} vanishes if it is in equilibrium. Therefore, the generalized forces Q_{k} are zero, that is

\delta W=0 \quad \Rightarrow \quad Q_k = 0 \quad k =1, 2, ..., f .
Constraint forces
An important benefit of the principle of virtual work is that only forces that do work as the system moves through a virtual displacement are needed to determine the mechanics of the system. There are many forces in a mechanical system that do no work during a virtual displacement, which means that they need not be considered in this analysis. The two important examples are (i) the internal forces in a rigid body, and (ii) the constraint forces at an ideal joint.
Lanczos^{[1]} presents this as the postulate: "The virtual work of the forces of reaction is always zero for any virtual displacement which is in harmony with the given kinematic constraints." The argument is as follows. The principle of virtual work states that in equilibrium the virtual work of the forces applied to a system is zero. Newton's laws state that at equilibrium the applied forces are equal and opposite to the reaction, or constraint forces. This means the virtual work of the constraint forces must be zero as well.
Law of the Lever
A lever is modeled as a rigid bar connected to a ground frame by a hinged joint called a fulcrum. The lever is operated by applying an input force F_{A} at a point A located by the coordinate vector r_{A} on the bar. The lever then exerts an output force F_{B} at the point B located by r_{B}. The rotation of the lever about the fulcrum P is defined by the rotation angle θ.
This is an engraving from Mechanics Magazine published in London in 1824.
Let the coordinate vector of the point P that defines the fulcrum be r_{P}, and introduce the lengths

a = \mathbf{r}_A  \mathbf{r}_P, \quad b = \mathbf{r}_B  \mathbf{r}_P,
which are the distances from the fulcrum to the input point A and to the output point B, respectively.
Now introduce the unit vectors e_{A} and e_{B} from the fulcrum to the point A and B, so

\mathbf{r}_A  \mathbf{r}_P = a\mathbf{e}_A, \quad \mathbf{r}_B  \mathbf{r}_P = b\mathbf{e}_B.
This notation allows us to define the velocity of the points A and B as

\mathbf{v}_A = \dot{\theta} a \mathbf{e}_A^\perp, \quad \mathbf{v}_B = \dot{\theta} b \mathbf{e}_B^\perp,
where e_{A}^{⊥} and e_{B}^{⊥} are unit vectors perpendicular to e_{A} and e_{B}, respectively.
The angle θ is the generalized coordinate that defines the configuration of the lever, therefore using the formula above for forces applied to a one degreeoffreedom mechanism, the generalized force is given by

Q = \mathbf{F}_A \cdot \frac{\partial\mathbf{v}_A}{\partial\dot{\theta}}  \mathbf{F}_B \cdot \frac{\partial\mathbf{v}_B}{\partial\dot{\theta}}= a(\mathbf{F}_A \cdot \mathbf{e}_A^\perp)  b(\mathbf{F}_B \cdot \mathbf{e}_B^\perp).
Now, denote as F_{A} and F_{B} the components of the forces that are perpendicular to the radial segments PA and PB. These forces are given by

F_A = \mathbf{F}_A \cdot \mathbf{e}_A^\perp, \quad F_B = \mathbf{F}_B \cdot \mathbf{e}_B^\perp.
This notation and the principle of virtual work yield the formula for the generalized force as

Q = a F_A  b F_B = 0. \,\!
The ratio of the output force F_{B} to the input force F_{A} is the mechanical advantage of the lever, and is obtained from the principle of virtual work as

MA = \frac{F_B}{F_A} = \frac{a}{b}.
This equation shows that if the distance a from the fulcrum to the point A where the input force is applied is greater than the distance b from fulcrum to the point B where the output force is applied, then the lever amplifies the input force. If the opposite is true that the distance from the fulcrum to the input point A is less than from the fulcrum to the output point B, then the lever reduces the magnitude of the input force.
This is the law of the lever, which was proven by Archimedes using geometric reasoning.^{[5]}
Gear train
A gear train is formed by mounting gears on a frame so that the teeth of the gears engage. Gear teeth are designed to ensure the pitch circles of engaging gears roll on each other without slipping, this provides a smooth transmission of rotation from one gear to the next. For this analysis, we consider a gear train that has one degreeoffreedom, which means the angular rotation of all the gears in the gear train are defined by the angle of the input gear.
Illustration from Army Service Corps Training on Mechanical Transport, (1911), Fig. 112 Transmission of motion and force by gear wheels, compound train
The size of the gears and the sequence in which they engage define the ratio of the angular velocity ω_{A} of the input gear to the angular velocity ω_{B} of the output gear, known as the speed ratio, or gear ratio, of the gear train. Let R be the speed ratio, then

\frac{\omega_A}{\omega_B} = R.
The input torque T_{A} acting on the input gear G_{A} is transformed by the gear train into the output torque T_{B} exerted by the output gear G_{B}. If we assume, that the gears are rigid and that there are no losses in the engagement of the gear teeth, then the principle of virtual work can be used to analyze the static equilibrium of the gear train.
Let the angle θ of the input gear be the generalized coordinate of the gear train, then the speed ratio R of the gear train defines the angular velocity of the output gear in terms of the input gear, that is

\omega_A = \omega, \quad \omega_B = \omega/R.\!
The formula above for the principle of virtual work with applied torques yields the generalized force

Q = T_A \frac{\partial\omega_A}{\partial\omega}  T_B \frac{\partial \omega_B}{\partial\omega}= T_A  T_B/R = 0.
The mechanical advantage of the gear train is the ratio of the output torque T_{B} to the input torque T_{A}, and the above equation yields

MA = \frac{T_B}{T_A} = R.
Thus, the speed ratio of a gear train also defines its mechanical advantage. This shows that if the input gear rotates faster than the output gear, then the gear train amplifies the input torque. And, if the input gear rotates slower than the output gear, then the gear train reduces the input torque.
Dynamic equilibrium for rigid bodies
If the principle of virtual work for applied forces is used on individual particles of a rigid body, the principle can be generalized for a rigid body: When a rigid body that is in equilibrium is subject to virtual compatible displacements, the total virtual work of all external forces is zero; and conversely, if the total virtual work of all external forces acting on a rigid body is zero then the body is in equilibrium.
If a system is not in static equilibrium, D'Alembert showed that by introducing the acceleration terms of Newton's laws as inertia forces, this approach is generalized to define dynamic equilibrium. The result is D'Alembert's form of the principle of virtual work, which is used to derive the equations of motion for a mechanical system of rigid bodies.
The expression compatible displacements means that the particles remain in contact and displace together so that the work done by pairs of action/reaction interparticle forces cancel out. Various forms of this principle have been credited to Johann (Jean) Bernoulli (1667–1748) and Daniel Bernoulli (1700–1782).
Generalized inertia forces
Let a mechanical system be constructed from n rigid bodies, B_{i}, i=1,...,n, and let the resultant of the applied forces on each body be the forcetorque pairs, F_{i} and T_{i}, i=1,...,n. Notice that these applied forces do not include the reaction forces where the bodies are connected. Finally, assume that the velocity V_{i} and angular velocities ω_{i}, i=,1...,n, for each rigid body, are defined by a single generalized coordinate q. Such a system of rigid bodies is said to have one degree of freedom.
Consider a single rigid body which moves under the action of a resultant for F and torque T, with one degree of freedom defined by the generalized coordinate q. Assume the reference point for the resultant force and torque is the center of mass of the body, then the generalized inertia force Q* associated with the generalized coordinate q is given by

Q^* = (M\mathbf{A})\cdot \frac{\partial \mathbf{V}}{\partial \dot{q}}  ([I_R]\alpha+ \omega\times[I_R]\omega)\cdot \frac{\partial \vec{\omega}}{\partial \dot{q}}.
This inertia force can be computed from the kinetic energy of the rigid body,

T = \frac{1}{2}M\mathbf{V}\cdot\mathbf{V} + \frac{1}{2}\vec{\omega}\cdot [I_R]\vec{\omega},
by using the formula

Q^* = \left(\frac{d}{dt} \frac{\partial T}{\partial \dot{q}} \frac{\partial T}{\partial q}\right).
A system of n rigid bodies with m generalized coordinates has the kinetic energy

T = \sum_{i=1}^n(\frac{1}{2}M\mathbf{V}_i\cdot\mathbf{V}_i + \frac{1}{2}\vec{\omega}_i\cdot [I_R]\vec{\omega}_i),
which can be used to calculate the m generalized inertia forces^{[6]}

Q^*_j = \left(\frac{d}{dt} \frac{\partial T}{\partial \dot{q}_j} \frac{\partial T}{\partial q_j}\right),\quad j=1, \ldots, m.
D'Alembert's form of the principle of virtual work
D'Alembert's form of the principle of virtual work states that a system of rigid bodies is in dynamic equilibrium when the virtual work of the sum of the applied forces and the inertial forces is zero for any virtual displacement of the system. Thus, dynamic equilibrium of a system of n rigid bodies with m generalized coordinates requires that

\delta W = (F_1 + Q^*_1)\delta q_1 + \ldots + (F_m + Q^*_m)\delta q_m = 0,
for any set of virtual displacements δq_{j}. This condition yields m equations,

F_j + Q^*_j = 0, \quad j=1, \ldots, m,
which can also be written as

\frac{d}{dt} \frac{\partial T}{\partial \dot{q}_j} \frac{\partial T}{\partial q_j} = Q_j, \quad j=1,\ldots,m.
The result is a set of m equations of motion that define the dynamics of the rigid body system.
If the generalized forces Q_{j} are derivable from a potential energy V(q_{1},...,q_{m}), then these equations of motion take the form

\frac{d}{dt} \frac{\partial T}{\partial \dot{q}_j} \frac{\partial T}{\partial q_j} = \frac{\partial V}{\partial q_j}, \quad j=1,\ldots,m.
In this case, introduce the Lagrangian, L=TV, so these equations of motion become

\frac{d}{dt} \frac{\partial L}{\partial \dot{q}_j} \frac{\partial L}{\partial q_j} =0 \quad j=1,\ldots,m.
These are known as Lagrange's equations of motion.
Virtual work principle for a deformable body
Consider now the free body diagram of a deformable body, which is composed of an infinite number of differential cubes. Let's define two unrelated states for the body:

The \boldsymbol{\sigma} State (Fig.a): This shows external surface forces T, body forces f, and internal stresses \boldsymbol{\sigma} in equilibrium.

The \boldsymbol{\epsilon} State (Fig.b): This shows continuous displacements \mathbf {u}^* and consistent strains \boldsymbol{\epsilon}^* .
The superscript * emphasizes that the two states are unrelated. Other than the above stated conditions, there is no need to specify if any of the states are real or virtual.
Imagine now that the forces and stresses in the \boldsymbol{\sigma} State undergo the displacements and deformations in the \boldsymbol{\epsilon} State: We can compute the total virtual (imaginary) work done by all forces acting on the faces of all cubes in two different ways:

First, by summing the work done by forces such as F_A which act on individual common faces (Fig.c): Since the material experiences compatible displacements, such work cancels out, leaving only the virtual work done by the surface forces T (which are equal to stresses on the cubes' faces, by equilibrium).

Second, by computing the net work done by stresses or forces such as F_A , F_B which act on an individual cube, e.g. for the onedimensional case in Fig.(c):

F_B \big ( u^* + \frac{ \partial u^*}{\partial x} dx \big )  F_A u^* \approx \frac{ \partial u^* }{\partial x} \sigma dV + u^* \frac{ \partial \sigma }{\partial x} dV = \epsilon^* \sigma dV  u^* f dV

where the equilibrium relation \frac{ \partial \sigma }{\partial x}+f=0 has been used and the second order term has been neglected.

Integrating over the whole body gives:

\int_{V} \boldsymbol{\epsilon}^{*T} \boldsymbol{\sigma} \, dV – Work done by the body forces f.
Equating the two results leads to the principle of virtual work for a deformable body:

\mbox{Total external virtual work} = \int_{V} \boldsymbol{\epsilon}^{*T} \boldsymbol{\sigma} dV \qquad \mathrm{(d)}
where the total external virtual work is done by T and f. Thus,

\int_{S} \mathbf{u}^{*T} \mathbf{T} dS + \int_{V} \mathbf{u}^{*T} \mathbf{f} dV = \int_{V} \boldsymbol{\epsilon}^{*T} \boldsymbol{\sigma} dV \qquad \mathrm{(e)}
The righthandside of (d,e) is often called the internal virtual work. The principle of virtual work then states: External virtual work is equal to internal virtual work when equilibrated forces and stresses undergo unrelated but consistent displacements and strains. It includes the principle of virtual work for rigid bodies as a special case where the internal virtual work is zero.
Proof of Equivalence between the Principle of Virtual Work and the Equilibrium Equation
We start by looking at the total work done by surface traction on the body going through the specified deformation:

\int_{S} \mathbf{u \cdot T} dS = \int_{S} \mathbf{u \cdot \boldsymbol {\sigma} \cdot n} dS
Applying divergence theorem to the right hand side yields:

\int_{S} \mathbf{u \cdot \boldsymbol \sigma \cdot n} dS = \int_V \nabla \cdot \left( \mathbf{u} \cdot \boldsymbol {\sigma} \right) dV
Now switch to indicial notation for the ease of derivation.

\begin{align} \int_V \nabla \cdot \left( \mathbf{u} \cdot \boldsymbol {\sigma} \right) dV &= \int_V \frac{\partial}{\partial x_j} \left( u_i \sigma_{ij} \right) dV \\ &= \int_V \frac{\partial u_i}{\partial x_j} \sigma_{ij} + u_i \frac{\partial \sigma_{ij}}{\partial x_j} dV \end{align}
To continue our derivation, we substitute in the equilibrium equation \frac{\partial \sigma_{ij}}{\partial x_j} + f_i = 0 . Then

\int_V \frac{\partial u_i}{\partial x_j} \sigma_{ij} + u_i \frac{\partial \sigma_{ij}}{\partial x_j} dV = \int_V \frac{\partial u_i}{\partial x_j} \sigma_{ij}  u_i f_i dV
The first term on the right hand side needs to be broken into a symmetric part and a skew part as follows:

\begin{align} \int_V \frac{\partial u_i}{\partial x_j} \sigma_{ij}  u_i f_i dV &= \int_V \frac12 \left[ \left( \frac{\partial u_i}{\partial x_j} + \frac{\partial u_j}{\partial x_i} \right) + \left( \frac{\partial u_i}{\partial x_j}  \frac{\partial u_j}{\partial x_i} \right) \right] \sigma_{ij}  u_i f_i dV \\ &= \int_V \left[ \epsilon_{ij} + \frac12 \left( \frac{\partial u_i}{\partial x_j}  \frac{\partial u_j}{\partial x_i} \right) \right] \sigma_{ij}  u_i f_i dV \\ &= \int_V \epsilon_{ij} \sigma_{ij}  u_i f_i dV\\ &= \int_V \boldsymbol\epsilon : \boldsymbol\sigma  \mathbf u \cdot \mathbf f dV \end{align}
where \boldsymbol\epsilon is the strain that is consistent with the specified displacement field. The 2nd to last equality comes from the fact that the stress matrix is symmetric and that the product of a skew matrix and a symmetric matrix is zero.
Now recap. We have shown through the above derivation that

\int_{S} \mathbf{u \cdot T} dS = \int_V \boldsymbol\epsilon : \boldsymbol\sigma dV  \int_V \mathbf u \cdot \mathbf f dV
Move the 2nd term on the right hand side of the equation to the left:

\int_{S} \mathbf{u \cdot T} dS + \int_V \mathbf u \cdot \mathbf f dV = \int_V \boldsymbol\epsilon : \boldsymbol\sigma dV
The physical interpretation of the above equation is, the External virtual work is equal to internal virtual work when equilibrated forces and stresses undergo unrelated but consistent displacements and strains.
For practical applications:

In order to impose equilibrium on real stresses and forces, we use consistent virtual displacements and strains in the virtual work equation.

In order to impose consistent displacements and strains, we use equilibriated virtual stresses and forces in the virtual work equation.
These two general scenarios give rise to two often stated variational principles. They are valid irrespective of material behaviour.
Principle of virtual displacements
Depending on the purpose, we may specialize the virtual work equation. For example, to derive the principle of virtual displacements in variational notations for supported bodies, we specify:

Virtual displacements and strains as variations of the real displacements and strains using variational notation such as \delta\ \mathbf {u} \equiv \mathbf{u}^* and \delta\ \boldsymbol {\epsilon} \equiv \boldsymbol {\epsilon}^*

Virtual displacements be zero on the part of the surface that has prescribed displacements, and thus the work done by the reactions is zero. There remains only external surface forces on the part S_t that do work.
The virtual work equation then becomes the principle of virtual displacements:

\int_{S_t} \delta\ \mathbf{u}^T \mathbf{T} dS + \int_{V} \delta\ \mathbf{u}^T \mathbf{f} dV = \int_{V}\delta\boldsymbol{\epsilon}^T \boldsymbol{\sigma} dV \qquad \mathrm{(f)}
This relation is equivalent to the set of equilibrium equations written for a differential element in the deformable body as well as of the stress boundary conditions on the part S_t of the surface. Conversely, (f) can be reached, albeit in a nontrivial manner, by starting with the differential equilibrium equations and the stress boundary conditions on S_t , and proceeding in the manner similar to (a) and (b).
Since virtual displacements are automatically compatible when they are expressed in terms of continuous, singlevalued functions, we often mention only the need for consistency between strains and displacements. The virtual work principle is also valid for large real displacements; however, Eq.(f) would then be written using more complex measures of stresses and strains.
Principle of virtual forces
Here, we specify:

Virtual forces and stresses as variations of the real forces and stresses.

Virtual forces be zero on the part S_t of the surface that has prescribed forces, and thus only surface (reaction) forces on S_u (where displacements are prescribed) would do work.
The virtual work equation becomes the principle of virtual forces:

\int_{S_u} \mathbf{u}^T \delta\ \mathbf{T} dS + \int_{V} \mathbf{u}^T \delta\ \mathbf{f} dV = \int_{V} \boldsymbol{\epsilon}^T \delta \boldsymbol{\sigma} dV \qquad \mathrm{(g)}
This relation is equivalent to the set of straincompatibility equations as well as of the displacement boundary conditions on the part S_u . It has another name: the principle of complementary virtual work.
Alternative forms
A specialization of the principle of virtual forces is the unit dummy force method, which is very useful for computing displacements in structural systems. According to D'Alembert's principle, inclusion of inertial forces as additional body forces will give the virtual work equation applicable to dynamical systems. More generalized principles can be derived by:

allowing variations of all quantities.

using Lagrange multipliers to impose boundary conditions and/or to relax the conditions specified in the two states.
These are described in some of the references.
Among the many energy principles in structural mechanics, the virtual work principle deserves a special place due to its generality that leads to powerful applications in structural analysis, solid mechanics, and finite element method in structural mechanics.
See also
References

^ ^{a} ^{b} ^{c} C. Lánczos, The Variational Principles of Mechanics, 4th Ed., General Publishing Co., Canada, 1970

^ Dym, C. L. and I. H. Shames, Solid Mechanics: A Variational Approach, McGrawHill, 1973.

^ ^{a} ^{b} W. Yourgrau and S. Mandelstam, Variational Principles in Dynamics and Quantum Theory, 3rd Ed., General Publishing Co., Canada, 1968

^ T. R. Kane and D. A. Levinson, Dynamics: theory and applications, McGrawHill, New York, 1985

^

^ T. R. Kane and D. A. Levinson, Dynamics, Theory and Applications, McGrawHill, NY, 2005.
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