FINITE ELEMENT ANALYSIS REPORT PROJECT REPORT (JACK STAND) WEEK 12
LECTURER NAME: DR. JASRI BIN MOHAMED NURAINI BINTI SULONG MA14217 NUR AFIKAH BT KHAIRI @ ROSLI MA15074 SEC 01/01A(B) SEM2 2017
TABLE OF CONTENTS
NO.
CONTENTS
PAGE
1.
INTRODUCTION
3
2.
OBJECTIVE
4
3.
LITERATURE REVIEW
5
4.
SPECIFICATIONS
5
5.
METHODOLOGY
6
6.
FLOWCHART PROCESS
7
7.
RESULT
8
8.
CONCLUSION
11
INTRODUCTION
FEA is widely accepted in almost all engineering disciplines. The method is often used as an alternative to the experimental test method set out in many standards. The technique is based on the premise that an approximate solution to any complex engineering problem can be reached by subdividing the structure/component into smaller more manageable (finite) elements. The Finite Element Model (FEM) is analysed with an inherently greater precision than would otherwise be possible using conventional hand analyses, since the actual shape, load and constraints, as well as material property combinations can be specified with much greater accuracy than that used in classical hand calculations. The method is comprised of three stages:(A) Pre-processing, in which the analyst develops a finite element mesh of the geometry and applies material properties, boundary conditions and loads (B) Solution, during which the program derives the governing matrix equations (stiffness x displacement = load) from the model and solves for the displacements, strains and stresses. This is the case in implicit code applications. Alternatively explicit codes can be used, mostly for high strain rate engineering problems. (C) Post-processing, in which the analyst obtains results usually in the form of deformed shapes, contour plots etc. which help to check the validity of the solution.
A variety of reporting tools can be used to illustrate the behaviour of the analysis model including colour contour and vector plots, section cuts, isosurfaces, animations, graphs and text output. The results are interpreted and areas of concerns are discussed.
OBJECTIVES
Objectives of this project are: •
To learn about one of the AUTODESK MECHANICAL SIMULATION software which is FEA
•
To know and able to use the FEA software
•
To select a product that is only mechanical parts that can be done for FEA purpose
•
To simulate the model FEA using AUTODESK Mechanical Simulation software
•
To generate 3D meshing of the model and resulting results
LITERATURE REVIEW
JACK STAND
Jack stand is a combination of jack and stand which are so important to lift a heavy car, this stand whose height may be adjusted and which is used to support an automobile that has been raised by a jack part. SPECIFICATIONS No.
Part Name
Element Type
Material Name
01.
Jack Stand
Brick
Aluminum 6061-T6
02.
Jack
Brick
Aluminum 6061-T6
Brick
Stainless Steel (AISI 202)
(Head+Body) 03.
Lock Pin
JACK(Head +Body) LOCK PIN
JACK STAND Jack Stand Picture
METHODOLOGY MODELLING SELECTION Modeling selection based on any mechanical part that is suitable to be done Finite Element Analysis. At least, have two to three parts. PROPOSED TO LECTURER Done choosing the mechanical part, proposed to lecturer the model being choose so that lecturer can clarified either the model can be proceed for FEA purposed nor cannot be proceed and look for another model. 3D DRAWING The design of 3D model for modeling had been done using Solidwork 2014 software to draw the model of simple belt drive, after the drawing finish, save the file in the iges, STEP and many more formats that can be open in AUTODESK software. Finally can run the iges or STEP files successfully and get the final product Finite Element Analysis of the Belt drive model. FEA By using AUTODESK MECHANICAL SIMULATION to proceed with the Finite Element Analysis progress. COLLECT RESULT After done the FEM analysis result of Von Misses Stress and many more come out. Hence, all the result should be collected as a data report. REPORT Finally, report was in progress after all the results data were taken.
FLOWCHART PROCESS START
No
Choose Mechanical Model.
Change Model.
Yes Propose to Lecturer the title.
3D modelling by using solidwork.
Finite Element Analysis.
No Result . Yes Report.
END
Checking & do Correction
RESULTS
Distributed load
Fixed at Edge
Figure 1: Boundary Conditions
i.
Displacement analysis (mm)
Head Side
Figure 2: Displacement Analysis
This jack stand was tested with distributed forcesof 5000 N on the jack head. Noticed that the critical sections for jack stand is at the both side of the jack head area. As we can see that the maximum value of displacement is 347 081 mm which mean this jack head still can support for heavier load. ii.
Von misses (stress analysis)
Figure 3: Jack Von misses (stress analysis)
iii. Figure 4: Head & Body Von misses (stress analysis)
iv. Figure 5: Pin Von misses (stress analysis) From the picture above, this is stress analysis on the Jack Stand Component, where 5 000 N on top of the head of jack stand.
The force is distributed uniformly on top of the jack stand
head. If we noticed that, they are severe critical spot at the pin, head side and jack area. The maximum value of stress is 3479.79 N/mm². By refering to yield strength of 304 stainless steel data sheet, it can endure stress up untill 290 Mpa before its undergo plastic deformation and broken. So, it means that, the jack stand able to accept force greater than 5 000 N without problem. Based off the results from the original part, we determined that the pin was the limiting factor for the loading capabilities of the jack stand. This conclusion was derived from the fact that the majority of the stresses were concentrated around the surfaces that were in contact with the pin. The pin appears to have been manufactured by a casting method using a stainless steel material and the original diameter of this pin is 12.7mm. In order to improve the performance of the jack stand in terms of loading capability and increasing the factory of safety, our design iteration for the jack stand was to increase the pin diameter to 20mm. This increase in diameter of the pin should allow for the load that is applied to the jack stand to be distributed over a greater area thus increase the loading capability of the overall jack stand.
Although increasing the diameter of the pin would cause slight increase in the mass of the jack stand, this additional weight would be slightly offset by the additional material that would have to be removed from the body of the jack stand in order to accept the larger pin. The marginal increase in mass for the jack stand is irrelevant because it is not substantial enough to cause any inconvenience to the user.
CONCLUSION For the analysis on the jack stand, we used a linear static model with variables. The variable we had to tune the boundary conditions for our model. We fixed the base of the model legs to restrict the legs movement in all degrees of freedom. Lastly, as we know the jack stand function is as a lifter to heavy car. The demands on a Jack Stand system are large, and this has led to many variations on the theme. Its lift the heavy car rigidly and with little movement. As conclusion, 5 000 N turning forces applied on the jack stand would not able to failed. This is because material used was AISI 304 stainless steel. This type of stainless steel is good in term of its value of yield strength and modulus of elasticity.
