Part 1 of this tale questioned whether the classical mechanics formulas for calculating stresses in torsion springs were correct. In part 1 it was shown that the mandrel diameter influenced torque output using the spring shown in figure 1 fitted with strain gauges.
The torsion springs were made with a gap between the coils, had tangential legs, and used 4mm square spring steel wire. To ensure the test spring was not subject to plastic deformation the maximum deflection was limited to 45 deg/9.3Nm, equating to a theoretical uncorrected stress of 870MPa, or 52 percent of the wire UTS.
The spring was supported during testing on interchangeable mandrels of Ø32, 30, 25mm diameter. The spring legs were loaded using Ø9mm pins at a radius of 40mm from the jig center.
When deflecting to a fixed angle, the torque, and hence stress, was lower when using a smaller mandrel, but the spring visibly sheared producing stresses that were not the same at each of the strain gauge location. The average stress measured with each mandrel was similar, but the difference in maximum and minimum was much greater with the small mandrel. The stress data for a constant torque will now be discussed.
The strain gauge results were used to calculate the stress for an applied torque of 8Nm. The results in table 1 show the average calculated for the loading/unloading stresses measured at the four gauges, and they were measured at both the static and driven end of the spring. In theory the stresses at each end should be the same, and to a first approximation this theory was shown to be true in practice. The theoretical stress at 8Nm is 750N/mm2 uncorrected, and 810 N/mm2 corrected1.
These results show that with the larger Ø32 and Ø30mm mandrels gauge 1 is the highest stressed position, which is to be expected. However, when the mandrel diameter becomes smaller, then the maximum stress position moves to gauge 2 (as would exist for a spring without a mandrel), so that with the Ø25 mandrel, gauges 3 and 4 have a reduction in stresses, indicating that the coil shearing is producing an increase stress at positions 1 and 2 and a reduced stress at position 3 and 4. It can also be seen that as the mandrel diameter reduces, the maximum stress measured increases.
Since the maximum measured stresses are approximately equal to the calculated corrected stress, it is reasonable to continue using this torsion spring formula, but beware that the actual maximum stress will be higher than the calculated when a relatively small mandrel is used. However, this work shows that the current method of correcting the calculated stresses in all design standards around the world are flawed, and while they give approximately the right result (but only with relatively large mandrels), a new torsion spring calculation method would be recommended. A new multi-national research project to produce an internationally acceptable formula for correcting torsion spring operating stresses is required.
The moral of this cautionary tale is that the operating stresses in torsion springs could be significantly different from the values calculated in CAD programs, and this may help explain some problems that are encountered with this type of spring.
1 The practice in Europe is to correct the calculated stress at the OD of a torsion spring by a factor greater than 1. The SMI uses a factor of 1. A.M. Wahl in “Mechanical Springs” and Berry in “An Investigation of Small Helical Torsion Springs” published in 1952 by the Institution of Mechanical Engineers, have shown that the correction factor at the OD is less than one. Their analysis assumes that the coils remain concentric.
Mark Hayes is the senior metallurgist at the Institute of Spring Technology (IST): The International Independent Centre of Excellence for Spring Technology. He manages IST’s spring failure analysis service, and all metallurgical aspects of advice given by the Institute. He also designs and delivers the majority of the spring training courses that the IST offers globally. Readers are encouraged to contact him with comments about this cautionary tale, and with subjects that they would like to be addressed in future tales. Contact Hayes at (011) 44 114 252 7984, fax (011) 44 114 2527997, or e-mail email@example.com.