The Field Of Serpentine Belt Drive System

The input shaft has a keyway cut which enables the motor to rotate the worm; this in turn results in the worm wheel rotating due to contact between the worm thread and the teeth of the worm wheel3. In order for the gearbox to continuously perform this function smoothly and efficiently over time it is important that the worm shaft’s material is carefully considered to avoid the three principle factors that will influence performance1.

Each separate truss (of the dimensions 920x5x50mm) consisted of a Pratt truss with nine diagonal members on each side of the centre. The model was tested in sufficiently isolated condition by tutors. It successfully passed the initial weight test, and satisfactorily resisted horizontal forces. Once fitted onto the testing rig, loads were applied and increased incrementally. Slight deformation was observed before failing at 12.5 kg, at which force a collection of members failed in succession, concluding the test.

Newton’s Second Law states that force times mass equals acceleration(fm=a). This law explains that when an unbalanced force is exerted on an object, the object will then accelerate in the direction of the force ("Newton's Second Law"). Therefore the greater force, the greater the acceleration. The pulley system that serves as a chain will be the unbalanced force since it is what changes the roller coasters motion and has the strength to pull it upwards. By conducting research on the total mass of roller coasters including their passengers, I came up with calculations that include the following:

The buckling resistance of slender webs can be increased by the provision of web stiffeners. In general the webs of plate girders used in buildings are either unstiffened or have transverse stiffeners

Three loops were then created on the string with two nodes present. The length of the string from the vibrator to the node closes was measured. The length of the string, tension and the number of loops were documented for future calculations.

Most cars built from 1990 on have serpentine belts, what winds along pulleys and powers various automotive components such as the alternator, power steering pump and air conditioner, and in certain models the water pump. Other cars may have timing, drive and V-belts, and just like serpentine belts, these are also subject to wear and eventual replacement. It is important for car owners to learn how to check belts on a car, in an effort to detect problems that may lead to a breakdown and costly repairs.

In this experiment, we determined the resultant and equilibrant of system of forces using the force table given and after gathering the data, we compared them with the different methods involved. The main material we used in this experiment is called force table. It has system of strings with varying tensions that act concurrently. It also has 4 pcs of super pulley with clamp and 4 pcs of mass hanger which weigh 5 grams each. There is a ring in the center of the force table that indicates if the forces are balance. We began the actual experiment by increasing differently the mass of each hanger using the slotted mass. Afterwards, we measured the angles of the strings by using trial and error in

For Case 2, the fourth pulley was at 15 degrees and 50 grams on the hanger. The experimental equilibrant force magnitude, 50 grams, was way higher than the calculated equilibrated force magnitude, 35.64 grams. Additionally, the calculated equilibrant force direction, 194.99 degrees, did not agree with the experimental equilibrant force direction, 15 degrees. During the experiment, when the fourth pulley was put on 194.99 degrees and tested with different grams on the hanger, the ring in the center of the force table was not able to hold firmly. So, different angles and masses were tested to achieve equilibrium. After various trial and errors, 15 degrees with 50 grams was the one that was able to hold the ring firmly in the center. Since the experimental equilibrant force was found through trial and errors, there was a pretty high percent error of 44.5%.

There were several sources of error in our experiment. But none affected the ability for a relationship between mass, acceleration, force to be drawn. The largest error was the one mentioned above. But its source was the easiest to account for. We mis-imputed the value of the spoke length into DataStudio. Luckley this mistake was easily remedied due to the design of the pulley. The electronic eye was recording a time that was exactly half of what it should have been. This time data produced an acceleration that was exactly double what it should be. Therefore this was issue was easily remedied by dividing the times by 2.

As a result of trail and error method we find the angle for the third pulley and the mass that should had be suspended from it. This will balance the forces deployed on the strings due to the other two masses. While the third force is defined as the equilibrant (������⃗������) Since it is the force that establishes the equilibrium. It is also the negative of the resultant -������⃗������ = ������⃗������ = ������⃗ ������ + ������⃗������. We gathered and recorded the mass and the angle required for the third pulley to enable to put the system into the equilibrium in table 1.

A four bar knee mechanism with two joints having clearance can have a dynamic response. One of the important factors that influence the dynamic stability and the performance of mechanisms is the joint clearance. The clearances always exist in the kinematic joints and they are known to be the sources for impact forces. These forces are the source of unwanted vibration that can cause a decrease in the reliability and life of the mechanism. The dynamic behavior of a four-bar mechanism with a clearance at any one of its connections can be described using a quasi-static model. The results showed that, in the presence of clearance, the mechanism responses were greatly influenced, and the coupler flexibility had a role of suspension for the mechanism. Kinematic analysis of the mechanism includes the determination of displacements, velocities and accelerations of the mass centers of moving links. As a practical implication, the proposed optimized values of the design variables lead to a

Figure 4.1, located below, shows the setup used for ANSYS. All of the nodes at the outermost corners of the truss are constrained to rotate about the z-axis only, and are fixed for the remaining 3 translational degrees of freedom and 2 rotational degrees of freedom. The force is applied at the location indicated by the red arrow: the same spot as in the lab.

Barsoum et al in 2014 [1] presents a finite element modelling framework to determine the torsion strength of hardened splined shafts by taking into account the detailed geometry of the involute spline

The force (F) was obtained by using five different weights that hung over a pulley system like shown in Figure 1, and the tension of the string acted

Abstract. Recently, the increased energy demand has led to explorations in other sources, particularly in renewable energies. Wind energy is one of the cleanest sources that plays a significant role in providing sustainable energy. Wind turbines, as wind energy power plants, are considered tall and slender structures, and depending on their location, which can be inland or offshore, can be exposed to high wind and/or strong wave loads. These loads can exert unwanted vibrations on the structure that may have detrimental effects on energy production. The current paper reviews some of existing methods to control these vibrations and investigates the influence of using different methods to suppress the motion of a wind turbine tower. In this study, the capability of the tuned mass dampers, tuned liquid column and sloshing dampers, and viscous dampers to decrease the tower’s vibration are evaluated. Finally, a comparison among these devices is made and recommendations on the application of each technique are suggested. Based on the results presented, viscous dampers can reduce both displacement and acceleration of the tower better than other types of dampers, for the same control effort (total control force). Nevertheless, the use of viscous dampers may require space considerations,