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abhishek-gorai
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APPLICATION OFDesign and Analysis of a Connecting Rod
: OVERVIEW• Product of ANSYS Inc., Pennsylvania, US founded in 1970• Over 40,000 customers (96 of top 100 in the FORTUNE 500 list)• Acquisitions : CFD Engineering, Airbus, CFX, Century Dynamics, Harvard
Thermal, Fluent Inc. (2006), Apache Design Solutions (2011), etc.• Static and Dynamic Analysis, Steady-state and Transient Thermal, Fluid
Flow and Modal Analysis• Extensive array of solvers• Accurate prediction according to theoretical models
DESIGN OF A CONNECTING ROD
• Connection between piston (gudgeon) pin and crank pin
• Converts linear motion to rotary motion
• Subjected to alternating compressive load
• Designed as a short strut against buckling using Rankine’s Formula
According to Rankine’s formula :• Wcr about x-axis = [for both ends hinged, l = L]• Wcr about y-axis = [for both ends fixed, l = L/2]
• For a connecting rod equally strong about both axes, the buckling loads must be equal. i.e.,
Ixx = 4 x Iyy [∴ = ×𝐼 𝐴 𝐾2 ]
Generally, Ixx = 3 to 3.5 times Iyy, and the connecting rod is designed to buckle in X direction.
X
X’
Y
Y’
5t
4t
tIn this case, we get :Ixx = 3.2 x Iyy
I - SECTION
PROBLEM SPECIFICATIONHonda 250 cc Specifications:
• Liquid cooled, 4-stroke, single cylinder, DOHC
• Displacement : 249.67 cc• Bore x Stroke : 76mm x 55 mm• Maximum Power : 28.6 BHP@9000 rpm• Maximum Torque : 23 NM@7500 rpm
STEPS IN AN ANALYSIS
Pre -processing
• Material Assignment• Creating/Importing CAD Model• Meshing• Applying Loads and Fixtures
Solving• Choosing a solver• Setting Analysis Parameters (if any)
Post-processing
• Viewing results• Interpreting results
MATERIAL ASSIGNMENTMechanical Properties of Forged Steel
CAD MODELLING
Section of the Connecting Rod :• I – Section
• B x H = 12 x 15 mm• Thickness of web and flange = 3 mm
Piston End Crank EndInner Diameter = 16 mm Inner Diameter = 24 mmOuter Diameter = 24 mm Outer Diameter = 32 mm
Length of the connecting Rod = (2 x stroke length) = 110 mm
LOADS AND FIXTURES
According to the formula :
Power = ½ • Mean Effective Pressure = 1.14 Mpa
• Considering Maximum Gas Pressure (Pmax) = 2 MPa,
• Buckling Load = Maximum Gas Force (PmaxApiston) = 9 kN
• Thickness of Web and Flange is taken 3 mm
MESH GENERATION• Model is divided into ‘Finite
Elements’• Calculations are done at the nodes
Meshing
1-D
• Beams• Pipes• Columns
2-D
• Sheet Metal• Instrument
Panel
3-D
• Engine block
• Crankshaft
Tetra Penta Brick(Hex)Pyramid
MESHING• Tetra-meshing• Max. size = 1.8 mm
• Fine Mesh :• High Accuracy• More Time
• Coarse Mesh :• Low Accuracy• Less Time
STRESSES AND DEFORMATION
LINEAR BUCKLING• The connecting rod buckles along
X-X direction as expected.
FATIGUE TESTS• S-N Diagram is constructed
according to the formula :Sa = σf ’ (2Nf) b
= 1131 (Nf) -0.0711 (MPa)• Alternating Loading is tested
according to Goodman’s Theory• Min. Safety Factor = 2.44• Min. Life = 108 cycles
RESULTSSl. No.
Test Value
1. Equivalent Stress (von Mises) 252.2 MPa2. Max. Principal Stress 97.73 MPa3. Normal Stress (X-axis) -60.26 MPa4. Normal Stress (Y-axis) -222.36 MPa5. Normal Stress (Z-axis) 97.73 MPa6. Total Deformation 0.05 mm7. Fatigue Test : Safety Factor 2.448. Linear Buckling : Load
Multiplier5.598
!!! Thank You !!!