A collar beam roof with the selected geometry is compared in terms of its internal forces between the calculation using RFEM 6 and the manual calculation. In total, three load systems are analyzed.
This verification example is based on Verification Example 0122. A single-mass system without damping is subjected to an axial loading force. An ideal elastic-plastic material with characteristics is assumed. Determine the time course of the end-point deflection, velocity, and acceleration.
The verification example describes wind loads in several wind directions on a model of a group of buildings. The model consists of eight cubes. The velocity fields obtained by the RWIND simulation are compared with the measured values from the experiment. The experimental data are measured using a thermistor anemometer in the wind tunnel.
Consider a rigid scaffolding tube, fixed at the bottom using the Scaffolding Nodal Support and loaded by both a moment and a force. Calculate the maximum deflection with consideration of initial slippage.
Determine the maximum deflection and maximum radial moment of a simply supported circular plate subjected to uniform pressure, uniform temperature, and differential temperature.
One layered square orthotropic plate is fully fixed at its middle point and subjected to pressure. Compare the deflections of the plate corners to check the correctness of the transformation.
Consider a rigid scaffolding tube, fixed at the bottom using the Scaffolding Nodal Support and loaded by both a moment and a force. Calculate the maximum radial deflection by exceeding the capacity of the scaffolding support.
Kelvin-Voigt material model consists of the linear spring and viscous damper connected in parallel. In this verification example there is tested the time behaviour of this model during the loading and relaxation in a time interval 24 hours. The constant force Fx is applied for 12 hours and the rest 12 hours is the material model free of load (relaxation). The deformation after 12 and 20 hours is evaluated. Time History Analysis with Linear Implicit Newmark method is used.
Consider a rigid scaffolding tube, fixed at the bottom using the Scaffolding Nodal Support and loaded by both a moment and a force. Self-weight is not considered. Considering an infinitely rigid beam, determine the maximum radial deflection.
A long, thin beam is carrying a concentrated mass and is loaded by a time-dependent force. It is simply supported. The problem is described using the following parameters. Determine the deflections in the given test times.
A single-mass system with clearance and two springs is initially deflected. Determine the natural oscillations of the system - deflection, velocity, and acceleration time course.
Determine the maximum displacement, in-plane stresses, and stress ratios of a simply supported double-pane glass plate with a foil between both glass panes subjected to uniform pressure.
A steel beam with a square cross-section is loaded with an axial force and distributed loading. The image shows the calculation of the maximum bending deflection and critical load factor according to the second-order analysis.
A thick-walled vessel is loaded by an inner pressure such that the vessel reaches an elastic-plastic state. While neglecting self‑weight, the analytical and numerical solutions for the radial position of the plastic zone border (under the Tresca hypothesis) are determined and compared.
Consider an ASTM A992 W 18x50 beam forspan and uniform dead and live loads as shown in Figure 1. The member is limited to a maximum nominal depth of 18 inches. The live load deflection is limited to L/360. The beam is simply supported and continuously braced. Verify the available flexural strength of the selected beam, based on LRFD and ASD.
A steel cable or membrane with pins on both ends is loaded by distributed loading. Neglecting its self-weight, determine the maximum deflection of the structure using the large deformation analysis.
A two-layered, open-ended, thick-walled vessel is loaded by inner and outer pressure; therefore, there is no axial stress. While neglecting self‑weight, the radial deflection of the inner and outer radius, and the pressure (radial stress) in the middle radius is determined.
A cantilever is fully fixed on the left end and loaded by a transverse force and an axial force on the right end. The tensile strength is zero and the behavior in the compression remains elastic.
Verify that a beam of different cross-sections made of Alloy 6061-T6 is adequate for the required load, in accordance with the 2020 Aluminum Design Manual.
Prove that coupling different dimensional elements does not affect the results. A cantilever with a rectangular cross-section is fixed at one end and loaded at the other by concentrated forces. Neglecting its self-weight and assuming only small deformations, determine the cantilever's maximum deflections.
A cantilever of rectangular cross‑section has a mass at the end. Furthermore, it is loaded by an axial force. Calculate the natural frequency of the structure. Neglect the self‑weight of the cantilever and consider the influence of the axial force for the stiffness modification.
Consider an ASTM A992 W 18×50 beam forspan and uniform dead and live loads as shown in Figure 1. The member is limited to a maximum nominal depth of 18 inches. The live load deflection is limited to L/360. The beam is simply supported and continuously braced. Verify the available flexural strength of the selected beam, based on LRFD and ASD.
The verification example describes the steady-state flow around a high-rise building in city blocks (scaled model). The example is given by the Architectural Institute of Japan (AIJ). The chosen results (velocity magnitude) are compared with the measured values.
Determine the maximum deflections of the block while considering or neglecting shear effect. The square block of the isotropic material is fully fixed at one end and loaded with uniform vertical pressure.
A composite plate consisting of three glass layers, one foil layer, and an inner space with dry air, is fully fixed and loaded with a variable temperature. Neglecting its self-weight, determine the plate's maximum deflection.
A compact disc (CD) rotates at a speed of 10,000 rpm. Therefore, it is subjected to centrifugal force. The problem is modeled as a quarter model. Determine the tangential stress on the inner and outer diameters and the radial deflection of the outer radius.
A cantilever beam with an I-beam cross-section of length L is defined. The beam has five mass points with masses m acting in the X-direction. The self-weight is neglected. The frequencies, mode shapes, and equivalent loads of this 5-DOF system are analytically calculated and compared with the results from RSTAB and RFEM.
A membrane is stretched by means of isotropic prestress between two radii of two concentric cylinders not lying in a plane parallel to the vertical axis. Find the final minimum shape of the membrane - the helicoid - and determine the surface area of the resulting membrane. The add-on module RF-FORM-FINDING is used for this purpose. Elastic deformations are neglected both in RF-FORM-FINDING and in the analytical solution; self-weight is also neglected in this example.