The objectives of this experiment were to evaluate flexure and stress distribution in a simple beam subject to varying loads in a four point bend test as well as to determine and compare the stresses present in a C-clamp subject to varying combined loads due to eccentric loading.
Background
In almost every structure, beams or flexural members are found. It is important then to understand how different beams will reach to different situations. To evaluate flexure and stress distribution in a simple beam, seen in Figure 1, a fundamental four point bending test can be conducted to induce pure bending on the center of a wide flange shape beam.
Figure 1: Schematic of simple I-beam
From a free-body diagram and statics, the general shear
…show more content…
This is done via a free-body diagram and statics calculation, as seen in Appendix B. The known equation of axial stress and flexure formula can then be used to find the stress in the C-clamp under eccentric loading. Equation (3) finds axial stress, where P is the applied load and A is the cross sectional area of the section:
σ_axial=P/A (3)
The individual stresses on the C-clamp can be combined using the principle of superposition, which states that “the effect of several loads acting simultaneously is equal to the algebraic sum of the effects of each load acting individually.” By combining Equation (1) and Equation (3) we get an equation for stress under combined flexural and axial loading, seen in Equation (4).
σ_x=σ_axial+ σ_bending=P/A+((-My)/I) (4)
The initial axial and bending stress distributions as well their resultants stress distribution can be theoretically drawn across the width of the C-clamp to visualize a shift of the neutral axis, included in Appendix C.
Procedures
The experiment was conducted in accordance with the procedures detailed in the lab handout.
To begin the four point bending experiment, the T6 Aluminum 6061 beam was loaded on the Instron Universal testing machine. Eight strain gages were mounted to the center of the beam and vertically
The specimen ends were not thick or had moving wedge grips to keep it secure in the holders of the servo-hydraulic load frame. The movement of the specimen in the machine causes some of the data to be an inaccuracy. Also, the transverse strain causes issues with the strain gages that are called transverse sensitivity. The transverse sensitivity affects the accuracy of the data that is being collected for the transverse strain more than the longitudinal strain. This is greatly seen in the percent difference in the strain values such as in one case the Longitudinal strain was .4% while the transverse strain was 30%. Another issue with the strain gages was that if the strain gages weren’t properly placed on the specimen the data accuracy would
The goal of the beam project is to design and construct a beam that can hold a given amount of weight without breaking. The beam is required to hold a concentrated load of 375 lbf on the X-axis and 150 lbf on the Y-axis. The maximum allowable weight of the beam is 250 grams. The maximum allowable deflection for the beam is 0.230 in. and 0.200 in. for the X and Y-axis respectively. The beam is required to be 24 in. in length, and it will be tested on a simply supported configuration spanning 21 in. All calculations are to be done under the assumption that the density of basswood is 28 lbm/ft3 and the modulus of elasticity for basswood is 1.46x106 lbm/in2. Given the constraints of a spending cost of $10.50, a maximum beam weight of 250 grams,
Load acts over outer circumference of on end of the cylinder, while the other end remains against a
This report aims to describe the experiment performed to investigate the stiffness of a channel section, and in particular calculate the flexural rigidity (EI) of the beam by two different sets of calculations based on the results gained in the experiment. The EI of an object is used
We used this equation along with the force and displacement data to determine the normal stress of the rod when it was axially loaded. P is the applied load and A is the cross sectional area of our sample.
His theory maintains that the truss is a structure that represents beam behaviour. Generally, Culmann considers every connection of the members in a truss flexible (basically a hinge) and formulates equilibrium equations at the point where members meet (Culmann 1851). Nowadays, this theory is known as the "Method of Joints" and is regularly used to calculate the internal forces in each member of the truss. Armed with a method to calculate the forces in the members of a truss, engineers optimized the design of trusses through addition and variation of
Following tables and graphs show the result of the experiment. The tables will demonstrate the experimental and theoretical deflection for each case. The graphs will show the relationship between the load applied and deflection, in addition to compare the experimental deflection and theoretical deflection.
In this paper the non-conventional reinforcement details of beam-column joint has been discussed. The non-conventional details includes using inclined crossed bars in the joint, and it can be placed as additional bars or by bending the longitudinal column’s bars. This paper first discusses types of joints, collapse of structures due to beam-column joint failure, explores some experimental studies about this type of reinforcement detail, and then the main advantages of using diagonal bars in the beam-column joint. Using diagonal bars has significant advantages for the beam-column joint: increasing ductility, affecting the
Problem 113 Find the stresses in members BC, BD, and CF for the truss shown in Fig. P-113. Indicate the tension or compression. The cross sectional area of each member is 1600 mm2.
The purpose of this lab is was to expose students to the manufacturing, fabrication, and testing of composites. In addition, it provides students with experience analyzing tensile and bending failures of composites. Three tensile specimens and two bend test specimens were tested during this lab. The tensile specimens were a wet lay-up of bi-directional E-glass, and the bend specimens were made up of a nomex honeycomb core with pre-preg uni-carbon faces. The three tensile specimens were tested, their elastic modulus and ultimate tensile strength calculated, and these value were compared to published approximately equivalent material properties. The two bend test specimens were tested, their face bending stresses were calculated, the shear stress in the core was calculated, and the bending and shear stresses were compared to published approximately equivalent material properties. A failure mode analysis was conducted for both the tensile and bend test specimens. This report summarizes the theory, procedure, and machines associated with the lab. Furthermore, it graphically and verbally displays the results draw from lab, and provides conclusions to improve the lab in the future.
The plate under study is a rectangular plate simply supported at four ends with load force at it extremes, the study aims to find the nodal displacement of the plate caused by the load. Also the plate was modeled in FEA software for comparison reason and to check the algorithm accuracy, the plate specification is as follows:
Since the base length is also the time taken it follows that the area under the graph is the
This section contains structural parts. The F.E. results are mainly shown in graphics. They are also compared to the experimental results obtained in the laboratory. Figure (5.126), Figure (5.127), Figure (5.128), Figure (5.129), Figure (5.130) and figure (5.131) show the principal stresses Ӏ for B1 up to B6.
Assuming BC and AC are principal planes, i.e. τθ = 0, and σ1 and σ2 are the principal stresses
The corresponding internal forces and displacements are determined using linear elastic analysis. The advantage of these linear dynamic procedures with respect to linear static procedures is that higher modes can be considered. However, they are based on linear elastic response and hence the applicability