Balance Equations: Momentum Balance
Newton and Euler Laws of Motion
Newton’s second law of motions states that the rate of change with respect to the time of the linear momentum of an object is equal to the net force acting on that object. If is the force vector acting on an object with mass moving with a velocity vector , then, by denoting the momentum by , we have:
If the mass is constant then:
where is the acceleration vector of the object.
Euler extended Newton’s second law of motion to a continuum object and introduced two laws. The first law is the balance of linear momentum while the second is the balance of angular momentum of a continuum object. These are as follows:
Euler’s Law of the Balance of Linear Momentum
The first equation is a direct extension of Newton’s first law to an arbitrary volume of a continuum body. Given an arbitrary volume of a continuum body represented by the set , then the net force acting on the arbitrary volume is equal to the rate of change of the linear momentum of that volume. The net force is the resultant of the traction vectors acting on the boundary and the body forces acting on the continuum points. Thus, according to Euler’s Law:
where, is time, is the mass density distribution, is the velocity vector distribution, is the body force distribution, is the traction vector distribution acting on the surface of , and and are the differential volume and surface elements of the arbitrary volume .
Euler’s Law of the Balance of Angular Momentum
Euler’s law of angular momentum preservation states that the rate of change of the angular momentum of an arbitrary volume of a continuum body around a fixed origin is equal to the torque (measured around the same fixed point) applied by the traction vectors on the boundary and the body forces acting on the continuum points. Thus, according to Euler’s Law:
where, is the position vector relative to the fixed origin.
It should be noted that the fixed origin can be arbitrary. If is the position vector relative to another fixed point such that , then, by replacing with and using the fact that is a fixed vector:
By using Euler’s law of the balance of linear momentum we reach to the same statement of the balance of angular momentum with replacing :
The Differential Equation of Equilibrium: Derivation using a Differential Volume
Balance of Linear Momentum
Newton’s laws of motion were originally formulated for systems of rigid particles mechanically interacting with each other. Newton’s laws can be extended to a continuum by considering a differential volume and the stresses acting on it. Let be a set representing a deformed configuration. Consider a differential cube of mass inside the body with dimensions and whose mass density is . The differential volume of the cube is given by . Let be the resultant force acting on the cube which is due to a body forces vector per unit mass acting on the cube and the stresses on the different faces of the cube. To write the differential form of the equilibrium equations, the stresses are assumed to be continuous functions. Such assumption allows the use of the first component in the Taylor expansion for the stresses. Thus, the resultant force component acting on the cube in the direction of the first basis vector can be evaluated as follows:
Similarly,
If is the acceleration vector of the differential cube, then the statement of Newton’s second law dictates that the resultant force is related to the acceleration via:
Thus, in component form, the equilibrium equations can be written as:
(1)
The above equations are usually written in the following compact form with :
If the divergence operator is used, the equations of equilibrium can be written in the following vector form:
Balance of Angular Momentum
The three angular momentum balance equations can be used to derive the symmetry of the stress tensor. Consider a differential rectangular volume oriented with the coordinate system with volume . Let the stresses on the sides with the negative normals have stresses and the stresses on the sides with positive normals have stresses . The first two equations for the balance of linear momentum dictate the following:
The moment of the external forces (stresses on the boundary and body forces) acting on the rectangular volume around the axis have the following form:
The rate of change of angular momentum around the axis is denoted and has the form:
By equating , using the equilibrium equations, and neglecting the smaller terms we get:
Therefore, . By repeating the procedure for the moment around other axes we reach:
The Differential Equation of Equilibrium: Derivation using Integrals over Arbitrary Volumes
The same differential equations of motion can be obtained using an equivalent but simpler derivation technique that relies on the integration over an arbitrary volume .
Balance of Linear Momentum
Using Euler’s law of the balance of linear momentum we have:
The differential operator on the left hand side cannot be interchanged with the integration operator unless the volume of integration is independent of time. Therefore, we can replace the differential volume with where is the determinant of the deformation gradient and is the corresponding differential volume in the reference configuration, which is independent of time. We will also utilize the relationship between the traction vector and the stress tensor: , and the divergence theorem which lead to:
The mass balance equations can be used to simplify the left hand side:
Since the integration domain is arbitrary, then the integrand is equal to zero. Therefore, the linear momentum balance equation is:
Balance of Angular Momentum
Using Euler’s law of the balance of angular momentum we have:
The differential operator on the left hand side cannot be interchanged with the integration operator unless the volume of integration is independent of time. Therefore, we can replace the differential volume with where is the determinant of the deformation gradient and is the corresponding differential volume in the reference configuration, which is independent of time. We also utilize the mass balance equations:
Therefore, we have:
Using the balance of linear momentum equation and replacing with we get:
The last equation can be written in component form to show the symmetry of the stress matrix. The component of the above vector equation can be written as:
Using the divergence theorem, the right hand side can be converted into a volume integral as follows:
The right hand side can be further simplified as follows:
Therefore, the integrand is equal to zero. Setting and , the three components of the above vector equation have the form:
Therefore:
It should be noted that the book by P. Chadwick has another proof showing the same result without relying on the component form of the vector equation.
Solution of the Equilibrium Equations in Static Problems
A continuum problem is solved if a stress field (the stress at every point inside the body) and an acceleration field are found such that the three equations of force equilibrium (conservation of linear momentum equations) are satisfied at every point. On the other hand, the restriction that ensures the conservation of angular momentum and no additional information can be obtained from considering the three equations of moment equilibrium. The unknown stress and velocity fields are required to also satisfy certain boundary conditions, which are traditionally given as either displacements or external traction forces on the exterior of the body and initial conditions for velocities. In static equilibrium, which is the purpose of many engineering applications, the acceleration vector is assumed to be zero and, thus, the equilibrium equation is simplified and the stress field becomes the only unknown. In that case, the equations become:
(2)
and . The problem is mathematically formulated as follows:
Let be a set representing a reference configuration of a continuum body. Given a constant or variable body forces vector , find the distribution of the stresses inside the continuum body that would satisfy the equations of equilibrium (Eq. 2) above. The boundary conditions for the equations of equilibrium are given on two parts of the boundary of . On the first part, , the external traction vectors are known so we have the boundary conditions for since . On the second part, , the displacement of the continuum is given. The boundary of is .
Difficulties Associated with Obtaining a Solution to the Equilibrium Equations
There are two difficulties associated with solving Eq. 2. First, these are three equations of static equilibrium. However, there are six unknowns (six stress variables). Thus, in their current form, many solutions could possibly satisfy the equilibrium equations! The second issue is that some of the boundary conditions contain expressions of displacements, while the equations themselves in this form do not have displacements as variables! These two major issues impel replacing the six unknown stress variables in the above equations with three unknown variables (usually the three displacements , , and . This can be performed by using a “constitutive equation” that describes the relationship between the stress and the strains inside the material. By replacing the stresses with the strains, and by using the relationship between the strains and the displacements described in the strain measures section, the problem becomes well posed, i.e., a solution can be obtained. The following few problems illustrate the applications and the solutions of the equilibrium equations given simplified assumptions allowing such solutions to exist.
Examples and Problems
Example 1
A stress field over a body that is in static equilibrium has the following form:
where , , and are the coordinates inside the body. Find the body forces vector field that is in equilibrium with this stress field.
Solution
Since the given stress matrix is symmetric, it automatically satisfies the angular momentum balance equations. Using Eq. 2 above, the body forces vector field has the following form:
View Mathematica Code
x={x1,x2,x3}; s={{5*x1^2+3x2+x3,x2*x1,0},{x2*x1,5x2,0},{0,0,9x3^2}}; rhob1=Sum[D[s[[i,1]],x[[i]]],{i,1,3}] rhob2=Sum[D[s[[i,2]],x[[i]]],{i,1,3}] rhob3=Sum[D[s[[i,3]],x[[i]]],{i,1,3}]
Example 2
The shown vertical beam has a varying circular cross sectional area with a radius metres at the top varying linearly to metres at the bottom. The beam is used to carry a concentrated load of , has a density , and is subjected to a gravity field with . Assuming that (a) the only nonzero stress component is , (b) is constant on every cross section perpendicular to , and (c) the undeformed and deformed coordinates coincide, find the distribution of the stress component along the length of the beam.
Solution
The radius and the area vary with according to the equations:
A horizontal slice of the beam can be analyzed to find the equilibrium equation as follows:
Equating the sum of the vertical forces acting on the slice to zero yields:
Simplifying and rearranging:
A boundary condition for the stress is given at the free end as follows:
Even with the very simplified assumption that is the only nonzero component of the stress matrix, the differential equation is relatively complicated. The command “DSolve” in Mathematica can be used to solve differential equations and was used to find the following distribution of the stress:
View Mathematica Code
Clear[s,x,L,g] A=Pi*(2x/L)^2; a=FullSimplify[DSolve[{s'[x]*A+D[A,x]*s[x]+ro*g*A==0,(s[L]==P/A/.x>L)},s[x],x]] ss=s[x]/.a[[1]] N[ss/.{L>5,ro>20,g>10,P>50}]
Example 3
The shown horizontal beam has a density and is under a constant horizontal body force component . Assuming that (a) is the only nonzero stress component, (b) is only a function of , and (c) the undeformed and deformed coordinates coincide, find the distribution of along the beam.
Solution
It should be noted that the first two assumptions are very strong. For example, closer to the fixed boundary, there could be other nonzero stress components which would cause stress concentrations. Additionally, could be higher in the middle and lower closer to the boundaries. However, to easily achieve a closed form solution to the equilibrium equations, such assumptions are required. Otherwise, a numerical solution (for example, using finite element analysis) would be required to find all the components of the stress.
The equation of equilibrium in the horizontal direction is given by:
Assuming that is a function of only then:
Integrating the above equation yields:
where is a constant that can be obtained from the boundary condition given for the stress:
Therefore, the stress distribution is:
Notice that if the end of the beam metres was also fixed, then the given boundary conditions would not be sufficient to solve the differential equation of equilibrium and a constitutive law would be required to replace the stresses with expressions of the displacement in the differential equation of equilibrium.
Example 4
The following is the stress field inside a body in static equilibrium
If the body is subjected to the following body forces vector:
then, find the values of , , , and such that static equilibrium is achieved.
Solution
The first step is to check that the stress matrix is symmetric to satisfy balance of angular momentum. Indeed, the given stress matrix is symmetric.
The equations of static equilibrium are given as:
Rearranging:
These equations have to be satisfied at every point inside the object, i.e., they have to be satisfied for all possible values of , , and . Therefore , , , and .
View Mathematica Codex= {x1, x2, x3}; s = {{alpha*x1^2 + delta*x1 + 3*x2 + x3, beta*x2*x1, 0}, {beta*x2*x1, 5 x2^2, 0}, {0, 0, gamma*x3^2}}; pb = {10 x1, 10 x2, 10 x3}; Print["Equilibrium Equations:"] Eq1 = Sum[D[s[[i, 1]], x[[i]]], {i, 1, 3}] + pb[[1]] == 0 Eq2 = Sum[D[s[[i, 2]], x[[i]]], {i, 1, 3}] + pb[[2]] == 0 Eq3 = Sum[D[s[[i, 3]], x[[i]]], {i, 1, 3}] + pb[[3]] == 0 Print["Solving Equations:"] ss1 = ForAll[{x1, x2, x3}, Eq1 && Eq2 && Eq3] Solve[Resolve[ss1], {alpha, beta, delta, gamma}]
Problems

A stress field inside a continuum has the following form:
The body forces vector applied is given by:
If the stress field is in equilibrium for all and , determine the values of .

A stress field inside a continuum has the following form:
The body forces vector applied is given by:
Show that the values of the constants , and so that the stress field is in equilibrium with the body forces vector field are 5, 10, 10, and 0, respectively.

A stress field inside a continuum has the following form:
If the stress field is in equilibrium with a zero body forces vector field and the values of is equal to 5 when , show that the values of the constants , and are 0, 0, and 5, respectively.

A two dimensional stress field on a rectangular plate of dimensions 1 and 5 units and 0.01 units of thickness has the following form:
Find the equilibrium body forces vector and the constants and given that for , units and units. Then, drawn the contour plot of the von Mises stress on the plate and identify the critical location (maximum von Mises stress) if the bottom left corner of the rectangular plate has coordinates .
 A stress field inside a continuum has the following form:
Assume the mass density of the continuum to be 2units and that the body forces vector per unit mass is given by:
Is the continuum in equilibrium? If not, what is the acceleration vector?
 The shown horizontal beam has a varying rectangular cross section with a constant thickness of 1m. The height of the beam changes linearly from 1m. at the left end to 2m. at the right end. The beam has a density of and is used to carry a concentrated of 100N. at the right end. The beam is subjected to a distributed load of . Assuming that (a) the only nonzero stress component is , (b) is constant on every cross section perpendicular to , and (c) the undeformed and deformed coordinates coincide, find the distribution of the stress component along the length of the beam.
The Differential Equation of Equilibrium: Lagrangian Formulation
In sections 6.3.2 and 6.3.3, the Eulerian form of the differential equation of equilibrium was derived. In the Eulerian form, the independent variables are the spatial position coordinates in the deformed configuration . One difficulty arises from the fact that the set representing the embedding of the a deforming object is in itself unknown. It is, therefore, desirable to have the differential equations written written in terms of the referential position coordinates represented by the set . In the following two subsections, I will present the derivation of these equations using two approaches, a component form, and a vector form approaches.
Component Form Approach
In the interest of brevity of the derivation, I will be utilizing Einstein Summation Convention. The Eulerian form of the differential equation is given above as:
My intention now is to replace the variables with the variables . For the acceleration and the body forces vectors, that only means a simply change of the argument with the capital letters used for the mappings of the referential coordinates:
I will recall the density equation that relates the density in the reference configuration with the spatial density:
I will also recall the equation that relates the First PiolaKirchhoff stress tensor with the Cauchy stress tensor:
Substituting the above equations in the Eulerian form of the differential equation yields:
I will decompose the first term, replace the derivation with respect to the components of with the derivation with respect to the components of , and will utilize the fourth statement in the matrix calculus section:
Therefore, the Lagrangian form of the equilibrium equation can be written in terms of the First PiolaKirchhoff stress tensor as follows:
The balance of angular moment imposes the following restriction on the components of :
Vector Form Approach
Euler’s law of the balance of linear moment that I showed above is repeated here:
By a simple change of variables, can be replaced by and the derivative operator is used instead of to indicate the Lagrangian formulation (material time derivatives with respect to the reference position comoponents):
I will use the mass balance equations to simplify the first expression and will use the First PiolaKirchhoff stress tensor and the reference area vector for the traction vector:
Considering that can be chosen arbitrarily, the vector form of the differential equation has the form:
The balance of angular moment imposes the following restriction on :