![]() ![]() Integrating curvatures over beam length, the deflection, at some point along x-axis, should also be reversely proportional to I. Therefore, it can be seen from the former equation, that when a certain bending moment M is applied to a beam cross-section, the developed curvature is reversely proportional to the moment of inertia I. Where Ixy is the product of inertia, relative to centroidal axes x,y (=0 for the I/H section, due to symmetry), and Ixy' is the product of inertia, relative to axes that are parallel to centroidal x,y ones, having offsets from them d_. ![]() Where I' is the moment of inertia in respect to an arbitrary axis, I the moment of inertia in respect to a centroidal axis, parallel to the first one, d the distance between the two parallel axes and A the area of the shape, equal to 2b t_f + (h-2t_f)t_w, in the case of a I/H section with equal flanges.įor the product of inertia Ixy, the parallel axes theorem takes a similar form: RESULTS DATA I x - Area moment of inertia about centroidal axis X I y - Area moment of inertia about centroidal axis Y A - Cross section area - Bending stress in cross section (on edge s). The so-called Parallel Axes Theorem is given by the following equation: INITIAL DATA H - T-beam height B - T-beam width t - Shelf thickness s - Wall thickness M x - Bending moment in cross section in the direction of X axis. The moment of inertia of any shape, in respect to an arbitrary, non centroidal axis, can be found if its moment of inertia in respect to a centroidal axis, parallel to the first one, is known. ![]()
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