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The capstan equation [1] or belt friction equation, also known as Euler–Eytelwein formula [2] (after Leonhard Euler and Johann Albert Eytelwein), [3] relates the hold-force to the load-force if a flexible line is wound around a cylinder (a bollard, a winch or a capstan).
Overloading occurs when operating forces of the application produce loads that exceed the clamp load, causing the joint to loosen over time or fail catastrophically. Over-torquing Under-torquing can cause failures by allowing a joint to come loose, and it may also allow the joint to flex and thus fail under fatigue.
A simple support (pin or roller) is equivalent to a point force on the beam which is adjusted in such a way as to fix the position of the beam at that point. A fixed support or clamp, is equivalent to the combination of a point force and a point torque which is adjusted in such a way as to fix both the position and slope of the beam at that point.
The force and torque vectors that arise in applying Newton's laws to a rigid body can be assembled into a screw called a wrench. A force has a point of application and a line of action, therefore it defines the Plücker coordinates of a line in space and has zero pitch. A torque, on the other hand, is a pure moment that is not bound to a line ...
The parameters (,,,) obtained from a test result can be used with these formulas to calculate the equivalent true stress ´ at failure. Specimen shape effect The graph of specimen shape effect shows how the ratio of true stress to engineering stress (σ´/σ e ) varies with the aspect ratio of the test specimen ( d o / l o {\textstyle d_{o}/l ...
The Marman clamp was first produced by Herbert Marx, better known by his stage name Zeppo Marx; [2] [7] it was manufactured by his company, Marman Products from the 1930s. [8] At the time it was designed to secure cargo during transport. The U.S. Military used Marman clamps to transport the atomic bombs used at the end of the Second World War. [9]
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For the thin-walled assumption to be valid, the vessel must have a wall thickness of no more than about one-tenth (often cited as Diameter / t > 20) of its radius. [4] This allows for treating the wall as a surface, and subsequently using the Young–Laplace equation for estimating the hoop stress created by an internal pressure on a thin-walled cylindrical pressure vessel: