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Sudharsan Srinivasan Portfolio

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Accomplished project portfolio.

Accomplished project portfolio.

Published in: Technology, Business

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  • 1. PROJECT PORTFOLIO SUDHARSAN SRINIVASAN
  • 2. EXPERIMENTAL & ANALYTICAL INVETIGATION OF THE PISTON SECONDARY MOTION IN A DIESEL ENGINE Software Used – ADAMS-Engine Abstract Piston secondary motion is a well known phenomenon in internal combustion engines which cause friction and noise. This motion is caused from the clearance between the piston and the cylinder liner and the force components on the piston causes piston lateral motion as well as rotational motion about the piston pin axis. This motion is known as piston secondary motion which causes friction as well as noise. As the piston moves from TDC towards BDC during the expansion stroke, the side force on the piston changes the direction and increases the force magnitude due to the rise of combustion pressure. This accelerates the piston laterally across the cylinder and the piston skirt impacts against the liner. Several approaches were followed to minimize the piston secondary motion by varying the engine geometry and operational parameters. Understanding the piston dynamics and secondary motion will greatly help reduce the engine friction. In this work, a previously developed analytical model has been validated for the piston secondary motion under variable speed and load conditions to understand the piston motion. The simulation model was developed for dry pattern with no lubrication (rigid body) and temperature parameter. The piston secondary motion was measured using telemetric system and gap sensors for various load cases and these results were compared with the simulated data. Further to provide more substantiation for the model and to illustrate its effectiveness in engine analysis, a series of parametric studies were performed on a variety of characteristics of the engine performance. The results show that some of these parameters have profound effects on the frictional and impact forces at the piston-skirt/liner interface. ADAMS/Engine Assembly Model Telemetry Layout Comparison of Piston Travel in Different Strokes Under Full Load Condition @ 1400 RPM
  • 3. PISTON SKIRT DEFORMATION STUDY USING FEA Software Used – Catia V5. Abstract For a vehicle engine, the piston is the essential part that bears heavy mechanical and thermal loads; therefore it has very many influences on the reliability and durability of an engine. So the piston greatly hinders the increase of power of an engine. Piston dynamics and friction are two important characteristics determining the performance and the efficiency of an internal combustion engine. In this project an approach to the behavioral analysis of the piston skirt is presented that is based mainly on the Finite Element Method representation. The Finite Element Method was used to predict the deformation of the piston skirt and also the stress distribution across the piston. Piston Model Boundary Condition Displacement & Stress Contour for Piston Deformation @ 3.8 Mpa Gas Pressure, 410 RPM Displacement & Stress Contour for Piston Deformation @ 6 Mpa Gas Pressure, 1580 RPM
  • 4. FATIGUE LIFE OF SOLDER BALLS IN A FLIPCHIP PACKAGE Software Used – Hypermesh, Abaqus. Abstract In the development of packaging of electronics the main aim is to increase the packaging density, improve the performance while still maintaining or even improving the reliability of the circuits. The concept of flip-chip process where the semiconductor chip is assembled face down onto circuit board is ideal for size considerations, because there is no extra area needed for contacting on the sides of the component. The performance in high frequency applications is superior to other interconnection methods, because the length of the connection path is minimized. Also reliability is better than with packaged components due to decreased number of connections. In flip-chip joining there is only one level of connections between the chip and the circuit board. The objective of this work is to investigate the reliability of the flip chip package under completely filled case and incomplete case in which the underfill is partially and completely removed. A nonlinear finite element technique, in which the viscoplastic material properties (strain rate-dependent) of solder balls and underfill are considered, is adapted to simulate the corresponding “cleaning” and “non- cleaning” samples to assess the impact on solder interconnect reliability. The results of the analysis reveals that the incomplete model decreases the mechanical stability and shortens the life time of the flip chip package. Flip-Chip Hypermeh Model with Complete Underfill Material & No Underfill. Model with Underfill Model with no Underfill Step Plastic Strain Displacement (mm) Plastic Strain Displacement (mm) 1 .0193 .0241 .093 .0227 2 .0239 .024 .109 .0227 3 .0214 .00101 .0843 .00234 4 .0206 .000926 .0811 .00224 5 .0208 .024 .1 .0226 Comparing the result Parameters for the models with Underfill & no Underfill. 16 24.5 14 Max. Von Mises Stress (MPa) 24 mm) 12 23.5 -3 10 Displacement (10 8 23 6 22.5 4 22 2 0 21.5 11980 10438 9362 3000 118 Fatigue Life (Cycle) Von Mises Stress Displacement Life Cycle of Flipchip with & without Underfill. Stress & Displacement based on Underfill.
  • 5. CRANKSHAFT DESIGN FOR V8 ENGINE Software Used – Catia V5. Abstract The crankshaft for a V8 engine was designed using the fundamentals of engine dynamics & vibrations. This project was accomplished as a requirement for a course work which involved in depth designing from the fundamentals. After designing the base model it is refined with counterweights and balanced. Finally, the torsional vibration and the critical speed of the crankshaft are determined. Crankshaft & Flywheel Assembly with added counterweights. First Natural Mode Second Natural Mode 1.2 1 1 0.5 0.8 R ela tive A m plitude R ela tive A m plitude 0 0.6 0 1 2 3 4 5 6 0.4 -0.5 0.2 -1 0 0 1 2 3 4 5 6 -0.2 -1.5 Mass Number Mass Number First & Second Natural Modes for the Masses in Crankshaft Flywheel Assembly. To calculate the dynamic magnifier, N cyl r 1 θ 1 D = (48....58) N cyl ∑ θz z =1 1 D = (48....58) × 4.898 = 59......71 4 The amplitude of the vibration of the first mass is expressed as Θ1 = 60 × 0.000622 = 0.03678rad Θ1 = D Θ1 st Θ 1 = 2 .1 ° The maximum value of the torque produced by torsional vibration at resonance may be estimated by N cyl r θ M max k = D Mk ∑ z z =1 θ1 M max 8 = 60 × 22.4797 × 4.97 = 6606.33Nm
  • 6. OPTIMIZATION OF CALIPER HOUSING USIGN FEA Software Used – Catia V5. Abstract In automobile design, structural analysis is the most important engineering process in developing a high quality vehicle where the computer simulations have greatly enhanced safety, reliability and comfort of today’s automobiles. Optimization has become critically important area of application in the automotive industry. Structural optimization coupled with analysis is instrumental in driving the design process so that the design targets are met in a timely fashion where the design targets include minimization of vehicle weight. In this present work a disc brake caliper has been analyzed and the regions of material removal have been identified using FEA. The regions with least stress and deflection are identified and taken off from the component iteratively and analyzed using CATIA. The modified caliper with weight optimization by 20% has been validated for real working condition by standard validation. By virtue of this redesign, material saving and hence cost savings have been achieved. Rib Ventilation hole Lug Cylinder Carrier Bolt Existing & Proposed Caliper Housing Model. Displacement & Stress Contour for Existing Caliper Housing Deformation at 70 bar Brake Pressure. Displacement & Stress Contour for Proposed Caliper Housing Deformation at 70 bar Brake Pressure.
  • 7. COASTDOWN ANALYSIS FOR EXTREME WIND CONDITION Software Used – Matlab, Simulink. Abstract The coastdown analysis is a technique for measuring real world drag that enables us to improve the vehicle performance and efficiency. The results out of this technique are more realistic than other methods, since product improvements which reduce road load such as improved tyre construction or reduced aerodynamic drag are properly represented. This may seem to be an ideal way to infer the aerodynamic drag since the actual road vehicle is in its natural environment. It is also not straight forward as it is necessary to separate the aerodynamic resistance from the rolling resistance (the tyre being the primary source). Although the coastdown technique is not new, obtaining adequate test repeatability requires correction of observed road loads to standard conditions. Previously there were many assumptions to perform a coastdown and a few of them are: 1. Wind speed is steady. 2. Wind speed is less than car speed. 3. Aerodynamic yaw angles remain small. This project is upgraded with features including headwind and crosswind components on an extremely windy condition which play a very important role in absorbing most of the kinetic energy of the vehicle during the coasting freely in newutral. To define the aerodynamic drag and rolling coefficients, utmost care is taken from the inception of anemometer calibration. Also a huge role is played by the simulated coastdown for analyzing the procedure. A new drag model is introduced for optimizing the real data coefficients and the sensitivity analysis is achieved with the variation of the optimized coefficients.
  • 8. CHASSIS TORSIONAL STIFFNESS MEASUREMENT ON FORMULA SAE CAR Software used – Nastran. Abstract Finite element analysis is a very powerful engineering design tool that enables engineers and designers to simulate structural behavior, make design change and distinguish the effects of these changes. FEA is in effect a computer simulation of the whole process in which a physical prototype is built and tested, and then rebuilt and retested until an acceptable design in created. Clearly, this physical process can be costly and time consuming when compared with running a computer simulation. However, FEA is not meant to replace prototype testing, merely to complement it. Testing is a means of validating the computer model. In certain cases it can be impossible to accurately model a complex real life situation. This work deals with the investigation of torsional stiffness of a chassis frame structure for a Formula SAE car. The stiffness matrix is framed for the particular beam with fundamentals of frame element theory. The cutting edge of Nastran in used to design the chassis frame and it is observed for the deflections experienced for the loads applied in a particular section of the chassis.

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