General Design Principles for DuPont Engineering Polymers - Module
General Design Principles for DuPont Engineering Polymers - Module
General Design Principles for DuPont Engineering Polymers - Module
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4—Structural <strong>Design</strong><br />
Short Term Loads<br />
If a plastic part is subjected to a load <strong>for</strong> only a short<br />
time (10–20 minutes) and the part is not stressed<br />
beyond its elastic limit, then classical design <strong>for</strong>mulas<br />
found in engineering texts as reprinted here can be<br />
used with sufficient accuracy. These <strong>for</strong>mulas are<br />
based on Hooke’s Law which states that in the elastic<br />
region the part will recover to its original shape after<br />
stressing, and that stress is proportional to strain.<br />
Tensile Stress—Short Term<br />
Hooke’s law is expressed as:<br />
s = E ε<br />
where:<br />
s = tensile stress (Kg/cm 2 ) (psi)<br />
E = modulus of elasticity (Kg/cm 2 ) (psi)<br />
ε = elongation or strain (mm/mm) (in/in)<br />
The tensile stress is defined as:<br />
s = F<br />
A<br />
where:<br />
F = total <strong>for</strong>ce (Kg) (lb)<br />
A = total area (cm 2 ) (in 2 )<br />
Bending Stress<br />
In bending, the maximum stress is calculated from:<br />
sb =<br />
My<br />
=<br />
M<br />
I Z<br />
where:<br />
s = bending stress (Kg/cm2 ) (psi)<br />
M = bending moment (Kg/cm) (lb·in)<br />
I = moment of inertia (cm4 ) (in4 )<br />
y = distance from neutral axis to extreme outer<br />
fiber (cm) (in)<br />
Z = I = section modulus (cm3 ) (in3 )<br />
y<br />
The I and y values <strong>for</strong> some typical cross-sections are<br />
shown in Table 4.01.<br />
Beams<br />
Various beam loading conditions can be found in the<br />
Roark’s <strong>for</strong>mulas <strong>for</strong> stress and strain.<br />
Beams in Torsion<br />
When a plastic part is subjected to a twisting moment,<br />
it is considered to have failed when the shear strength<br />
of the part is exceeded.<br />
15<br />
The basic <strong>for</strong>mula <strong>for</strong> torsional stress is: Ss = Tr<br />
K<br />
where:<br />
Ss = Shear stress (psi)<br />
T = Twisting Moment (in·lb)<br />
r = Radius (in)<br />
K = Torsional Constant (in4 )<br />
Formulas <strong>for</strong> sections in torsion are given in Table<br />
4.02.<br />
To determine θ, angle of twist of the part whose<br />
length is , the equation shown below is used:<br />
θ = T<br />
KG<br />
where:<br />
θ = angle of twist (radians)<br />
K = Torsional Constant (in4 )<br />
= length of member (in)<br />
G = modulus in shear (psi)<br />
To approximate G, the shear modulus, use the<br />
equation,<br />
G= E<br />
2 (1+η)<br />
where:<br />
η = Poisson’s Ratio<br />
E = Modulus (psi) (mPa)<br />
Formulas <strong>for</strong> torsional de<strong>for</strong>mation and stress <strong>for</strong><br />
commonly used sections are shown in Table 4.02.<br />
Tubing and Pressure Vessels<br />
Internal pressure in a tube, pipe or pressure vessel<br />
creates three (3) types of stresses in the part: Hoop,<br />
meridional and radial. See Table 4.03.<br />
Buckling of Columns, Rings and<br />
Arches<br />
The stress level of a short column in compression is<br />
calculated from the equation,<br />
Sc = F<br />
A<br />
The mode of failure in short columns is compressive<br />
failure by crushing. As the length of the column<br />
increases, however, this simple equation becomes<br />
invalid as the column approaches a buckling mode of<br />
failure. To determine if buckling will be a factor,<br />
consider a thin column of length , having frictionless<br />
rounded ends and loaded by <strong>for</strong>ce F. As F increases,<br />
the column will shorten in accordance with Hooke’s<br />
Law. F can be increased until a critical value of P CR is<br />
reached. Any load above P CR will cause the column to<br />
buckle.