By Jean-Claude Flabel
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Additional resources for Practical Stress Analysis for Design Engineers: Design & Analysis of Aerospace Vehicle Structures
If, however, more than two unknown bar forces exist at a joint, the unknown bar axial forces cannot immediately be found from these two equations. The extra unknown bar force or forces may however be found from the computations of other isolated joints. 500 ~T.. I - 2,500 FIGURE 1-53 Equilibrium of forces acting on the truss framework. JOINT the cross-sectional area of a bar member does not line up with the centroid of its rivet pattern, a twisting of the member will result. From Fig. 1-50, a detail of joint B depicting these eccentricities is shown in Fig.
From the couple-force relationship of moments derived in Appendix B (Pcoup1e =MIH), the direction of these calculated stresses across the entire section can easily be figured out. In other words, inasmuch as a moment can be thought of as a couple, as such, a push (or compression force) must exist on the upper part of the be_am. while_ a pull (or tension force) must exist on the lower part for the moment M md1cated m this figure. The neutral axis, as the name might imply, is an axis of neutrality or a line of zero stress across the cross-sectional area of a beam subjected to bending.
2-2 is applied. The same basic analogy can be shown to exist for the outer plate members. z the applied load P would be used to describe their structural behavior. Note that the bearing stress distribution used to construct the axial diagram of the middle plate is entirely theoretical. The complexity of bearing failures of most ductile metals makes it physically impossible to measure this quantity accurately. For this reason, in most practical applications, it is common practice to conservatively base the theoretical bearing stress distribution of a member on a uniform stress distribution across the centerline of the hole.