SPRING 2011
Distributor's Link Magazine Spring Issue 2011 / VOL 34 / NO.2
Distributor's Link Magazine Spring Issue 2011 / VOL 34 / NO.2
Create successful ePaper yourself
Turn your PDF publications into a flip-book with our unique Google optimized e-Paper software.
170 THE DISTRIBUTOR’S LINK<br />
FASTENER STRENGTH - REAL OR NOT? continued from page 8<br />
“plated”, some call out “dry” or “oiled”. Some others<br />
refer to a “torque coefficient” (actually the K-factor or<br />
nut-factor) of 0.20 for plain fasteners or 0.15 (!) for<br />
plated. This is not good enough information and can be<br />
down-right dangerous if applied to a critical joint.<br />
A proper calculation of a tightening torque (taught in<br />
my classes) must be based on a K-factor taking into<br />
account thread friction, bearing surface friction (also<br />
area), thread pitch and the nominal fastener size. The<br />
biggest problem is to determine friction data, since there<br />
are not just one standard type of lubricant (like oil) but<br />
also very effective coatings, waxes, molybdenum<br />
disulfide, PTFE, graphite and others that will have much<br />
lower (and more consistent) coefficients of friction than<br />
oils and greases. Also, a “dry” fastener may be<br />
tightened against a “dry” surface, but be threaded in to<br />
a tapped hole with some residual tapping oil present.<br />
That condition would not match up with the simplified<br />
approach in a typical torque chart.<br />
If we do a reasonably good job creating a K-factor<br />
based on reality, we could with confidence use the well<br />
known “short formula” to find a torque value to get it right;<br />
T=K x d x Fp<br />
where<br />
T = Torque or moment of force (Nm, lbfft, etc.)<br />
K = see above<br />
d = nominal diameter of fastener (mm, inch)<br />
Fp= target mean preload force (N, lbf, etc.)<br />
Please note that some (most) torque charts neglect<br />
the desired preload level.<br />
Friction coefficients<br />
There is, unfortunately, no easy way to determine<br />
friction coefficients. The German design guide line VDI<br />
2230 (the best available in the world) lists various<br />
friction classes based on material surfaces and types of<br />
lubricants or no lubricants. The guide line suggests that<br />
we try to be in friction class B meaning coefficients 0.08<br />
– 0.16. The lower range means that we use very effective<br />
lubricants like MoS2, graphite, PTFE and similar, the<br />
upper range being less effective lubricants like oils and<br />
greases.<br />
wrench (dial or clicker) will typically give a tension scatter<br />
around +/-20 %, even if the wrench itself is calibrated to<br />
have an accuracy of +/- 2 % or better. The worst<br />
performer is the noisy impact wrench that will give<br />
tension scatters around +/- 60! Don’t let your service<br />
station tighten the lug nuts on your car with these<br />
horrible tools, it is always better to keep the wheels on<br />
your car instead of out in the woods. If a joint is designed<br />
to be tightened with a calibrated torque wrench and<br />
someone uses an impact wrench, the scatter will either<br />
break the fastener at the upper scatter or not produce<br />
enough load at the lower end.<br />
Torsional stresses<br />
How does torsion (twisting) affect the loading<br />
capacity of a bolt/screw? I mentioned earlier the data in<br />
our various standards showing proofing loads and<br />
tensile load levels. Those numbers are valid only for<br />
testing with a straight pull in a tensile testing apparatus.<br />
When we tighten (avoid the term torquing, we may<br />
tighten by means of torque) a fastener (nut on a bolt or<br />
a screw in a blind hole) typically 90 % of the<br />
moment/torque is wasted by overcoming friction. About<br />
40 % of the torque value is for the friction between the<br />
internal and external threads. With this resistance, the<br />
bolt/screw will actually experience a twisting motion with<br />
torsional stresses being introduced in the fastener. The<br />
fastener is, in fact, a “glorified” rubber band. This<br />
twisting could substantially lower the capacity of the<br />
fastener to carry an axial load.<br />
This is why we should never use the table values in<br />
the standards as they are listed, but instead modify<br />
them with the influence of the torsional “wind-up”.<br />
Factoring in torsion we will establish a new proofing load<br />
level that properly reflects the actual fastener strength<br />
as tightened. The way to predict the influence of torsion<br />
is described in figure 2.<br />
Tightening<br />
All tightening equipment will produce some scatter in<br />
the resulting tension in the joint. A well calibrated torque<br />
please turn to page 172