Analysis of lug analysis inventor[1] - Autodesk · 2009-04-23 · Analysis of...

Analysis of lug_analysis_inventor[1].ipt

Introduction Autodesk Inventor Professional Stress Analysis was used to simulate the behavior of a mechanical part under structural loading conditions. ANSYS technology generated the results presented in this report.

Do not accept or reject a design based solely on the data presented in this report. Evaluate designs by considering this information in conjunction with experimental test data and the practical experience of design engineers and analysts. A quality approach to engineering design usually mandates physical testing as the final means of validating structural integrity to a measured precision.

Additional information on AIP Stress Analysis and ANSYS products for Autodesk Inventor is available at http://www.ansys.com/autodesk.

Geometry and Mesh The Relevance setting listed below controlled the fineness of the mesh used in this analysis. For reference, a setting of -100 produces a coarse mesh, fast solutions and results that may include significant uncertainty. A setting of +100 generates a fine mesh, longer solution times and the least uncertainty in results. Zero is the default Relevance setting.

Bounding box dimensions represent lengths in the global X, Y and Z directions.

Author: JDPetittAnalysis Created: Thursday, April 23, 2009 10:46:31 AM

Analysis Last Modified: Thursday, April 23, 2009 10:46:31 AM

Report Created: Thursday, April 23, 2009 11:06:37 AM

Database: C:\Documents and Settings\JDPetitt\Local Settings\Temporary Internet Files\Content.IE5\6AT06HGI\lug_analysis_inventor[1].ipa

Software: Autodesk Inventor Professional 2009 ANSYS Technology

TABLE 1lug_analysis_inventor[1].ipt Statistics

Bounding Box Dimensions80.0 mm 80.0 mm 20.0 mm

Part Mass 0.7993 kg Part Volume 1.02e+005 mm³Mesh Relevance Setting 100Nodes 15262Elements 3156

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4/23/2009file://C:\Documents and Settings\JDPetitt\Application Data\Ansys\AIP130\Report.htm

JDPetitt

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JDPetitt

Information Only

Material Data The following material behavior assumptions apply to this analysis:

Linear - stress is directly proportional to strain. Constant - all properties temperature-independent. Homogeneous - properties do not change throughout the volume of the part. Isotropic - material properties are identical in all directions.

Loads and Constraints The following loads and constraints act on specific regions of the part. Regions were defined by selecting surfaces, cylinders, edges or vertices.

Note: vector data corresponds to global X, Y and Z components.

Results The table below lists all structural results generated by the analysis. The following section provides figures showing each result contoured over the surface of the part.

Safety factor was calculated by using the maximum equivalent stress failure theory for ductile materials. The stress limit was specified by the tensile yield strength of the material.

TABLE 2Steel, High Strength Low Alloy

Young's Modulus 2.e+005 MPa Poisson's Ratio 0.287Mass Density 7.84e-006 kg/mm³Tensile Yield Strength 275.8 MPa Tensile Ultimate Strength 448.0 MPa

TABLE 3Load and Constraint Definitions

Fixed Constraint 1 Surface Fixed Constraint 0.0 mm 0.0 mm0.0 mm0.0 mm

Bearing Load 1 Cylindrical Bearing Load 9800 N 9800 N 0.0 N 0.0 N

Name Type Magnitude Vector

TABLE 4Constraint Reactions

Fixed Constraint 1 9800 N -9800 N 5.731e-006 N -2.047e-006 N

1.22e-004 N·mm -7.169e-005 N·mm-2.649e-005 N·mm9.506e-005 N·mm

Name Force Vector Moment Moment Vector



TABLE 5Structural Results

Equivalent Stress 0.1605 MPa 44.09 MPa Maximum Principal Stress -5.086 MPa 45.08 MPa Minimum Principal Stress -28.05 MPa 4.574 MPa Deformation 0.0 mm 5.693e-003 mmSafety Factor 6.255 N/A

Name Minimum Maximum



Figures FIGURE 1

Equivalent Stress



FIGURE 2Maximum Principal Stress



FIGURE 3Minimum Principal Stress



FIGURE 4Deformation



FIGURE 5Safety Factor

















Page 1 of 8Analysis of lug_analysis_inventor[1].ipt












Bearing Load 1 Cylindrical Bearing Load 9800 N 6930 N 6930 N 0.0 N



Fixed Constraint 1 9800 N -6930 N -6930 N 1.85e-006 N

2.775e+005 N·mm 2.912e-004 N·mm -2.626e-004 N·mm-2.775e+005 N·mm





Equivalent Stress 3.684e-002 MPa 52.53 MPa Maximum Principal Stress -6.143 MPa 55.25 MPa Minimum Principal Stress -38.77 MPa 9.919 MPa Deformation 0.0 mm 1.001e-002 mmSafety Factor 5.25 N/A




Figures FIGURE 1

Equivalent Stress



FIGURE 4Deformation













Bearing Load 1 Cylindrical Bearing Load 9800 N 0.0 N 9800 N 0.0 N



Fixed Constraint 1 9800 N -5.523e-006 N -9800 N 3.146e-006 N

3.925e+005 N·mm 3.792e-004 N·mm -4.118e-004 N·mm-3.925e+005 N·mm




Figures FIGURE 1

Equivalent Stress



FIGURE 4Deformation











Force 1 Surface Force 6930 N 0.0 N 0.0 N 6930 N


Bearing Load 1 Cylindrical Bearing Load 6930 N 6930 N 0.0 N 0.0 N



Fixed Constraint 1 9800 N -6930 N 1.082e-006 N -6930 N

2.772e+005 N·mm -3.386e-005 N·mm2.772e+005 N·mm3.05e-003 N·mm






Equivalent Stress 0.1875 MPa 71.25 MPa Maximum Principal Stress -18.09 MPa 92.81 MPa Minimum Principal Stress -77.51 MPa 18.97 MPa Deformation 0.0 mm 4.33e-002 mmSafety Factor 3.871 N/A




Figures FIGURE 1

Equivalent Stress



FIGURE 4Deformation












Force 1 Surface Force 9800 N 0.0 N 0.0 N 9800 N




Fixed Constraint 1 9800 N -4.122e-005 N 1.452e-005 N -9800 N

3.92e+005 N·mm 2.835e-004 N·mm 3.92e+005 N·mm -7.027e-004 N·mm




Figures FIGURE 1

Equivalent Stress



FIGURE 4Deformation



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