Torsion of members is an important topic in the mechanics of elastic bodies. We can calculate shear stresses and the rotation angles created by applied torques. The study of pure torsion in circular bars is much simplified because of the high degree of geometry in the member. The study of pure torsion in rectangular bars is more in depth. From this report I hope to help create a better understanding of torsion in non-circular members.

In circular members, central geometry greatly enhances the understanding of torsion’s effects. Shear stresses are equivalent along circumfrential lines about the center (see Figure 1.1). Studying pure torsion in circular members and their geometry results in equations (1.1) and (1.2).

t = (rT)/Ip Eq(1.1)

Where:

t is shear stress

r is the radius distance from center

T is the applied torque

Ip is the polar moment of inertia

D f = Tl/GIp Eq(1.2)

Where:

D f is the change in angle over the length of the bar

l is the length of the bar

G is the shear modulus

The observations made for torsion of members with circular cross sections do not hold for those with non-circular cross-sections:

Out of plane displacements require solutions of the non-circular torsion problem to use a warping function. The warping function makes the solution of the problem more complex. We will not explore it here, rather show the results from the first proposed solution to the non-circular torsion problem.

St. Venant was the was the first to accurately describe the shear stress distribution on the cross section of a non-circular member using the Theory of Elasticity:

Applicable statements from the theory of elasticity:

• the maximum shear strain and stress occur at the centerline of the long sides of the rectangular cross section
• the shear strain and stress at the corners and center of the rectangular cross section are zero
• the strain and stress variations on the cross section are primarily nonlinear

The figures in 2.1 (a) and (b) show St. Venant’s resulting stress zones from rectangular and square torsion members.

(a)

The theory of elasticity has been applied to find analytical solutions for the torsion of rectangular elastic members. Equations for shear stress and angle of twist are stated in equations (2.1) and (2.2).

Eq(2.1)

Eq(2.2)

b= length of the long side

t = thickness, or width of short side

a ,b = parameters obtained from Table 2.1

The solution to the non-circular torsion problem requires the availability of a warping function. The elastic membrane analogy provides for a much simpler way to find the solution to a this problem. Prandtl, showed that the Laplace equation describing the torsion of an elastic member is identical to that used to describe the deflection of an elastic membrane subjected to a uniform pressure.

The elastic membrane analogy is as follows:

Consider a tube which has the same cross-sectional boundary as the bar. Then a hypothetical membrane is stretched over the tube’s cross-section and internal pressure is applied. The deflected shape of the membrane helps us to understand the stress pattern in the bar under torsion.

The following conclusions are used to help understand the analogy:

In engineering practice most materials are not the ideal, perfect materials we study. In the same way, studying pure torsion in bars of circular cross-section allow understanding of the effects of torque on a member, but many times are exclusive to the situations which arise in the real world. Studying torsion in non-circular structures allows needed calculations to compute the effects of applied torque.