Analysis of Stress Beater Bracket R3

Author:	Raytec
Analysis Created:	Monday, 3 November 2008 4:34:04 p.m.
Analysis Last Modified:	Monday, 3 November 2008 4:34:04 p.m.
Report Created:	Monday, 3 November 2008 4:38:21 p.m.
Database:	C:\Users\Inventor User\Documents\Inventor\Gin Machine\Parts\Stress Beater Bracket R3.ipa
Software:	Autodesk Inventor Professional 2009 ANSYS Technology

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.

TABLE 1

Stress Beater Bracket R3.ipt Statistics
Bounding Box Dimensions	239.1 mm 132.0 mm 32.0 mm
Part Mass	0.5098 kg
Part Volume	1.881e+005 mm³
Mesh Relevance Setting	0
Nodes	8108
Elements	3808

Material Data

TABLE 2

Aluminum-6061-AHC
Young's Modulus	6.89e+004 MPa
Poisson's Ratio	0.33
Mass Density	2.71e-006 kg/mm³
Tensile Yield Strength	275.0 MPa
Tensile Ultimate Strength	310.0 MPa

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.

TABLE 3

Load and Constraint Definitions

Name Type Magnitude Vector

Force 1 Surface Force 1.e+004 N
0.0 N

1.e+004 N

0.0 N

Pin Constraint 1 Pin Constraint
Radial Direction: Fixed

Axial Direction: Fixed

Tangential Direction: Free
N/A

TABLE 3

Load and Constraint Definitions
Name	Type	Magnitude	Vector
Force 1	Surface Force	1.e+004 N	0.0 N 1.e+004 N 0.0 N
Pin Constraint 1	Pin Constraint	Radial Direction: Fixed Axial Direction: Fixed Tangential Direction: Free	N/A

TABLE 4

Constraint Reactions

Name Force Vector Moment Moment Vector

Pin Constraint 1 4955 N
-883.9 N

-4876 N

-0.5369 N
5.693e+004 N·mm
-5.409e+004 N·mm

1.775e+004 N·mm

-3.051e-003 N·mm

Results

TABLE 4

Constraint Reactions
Name	Force	Vector	Moment	Moment Vector
Pin Constraint 1	4955 N	-883.9 N -4876 N -0.5369 N	5.693e+004 N·mm	-5.409e+004 N·mm 1.775e+004 N·mm -3.051e-003 N·mm

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 5

Structural Results

Name Minimum Maximum

Equivalent Stress 0.1447 MPa 8.27e+004 MPa

Maximum Principal Stress -8206 MPa 6.308e+004 MPa

Minimum Principal Stress -3.149e+004 MPa 6256 MPa

Deformation 1.626e+006 mm 9.949e+006 mm

Safety Factor 3.325e-003 N/A

Figures

TABLE 5

Structural Results
Name	Minimum	Maximum
Equivalent Stress	0.1447 MPa	8.27e+004 MPa
Maximum Principal Stress	-8206 MPa	6.308e+004 MPa
Minimum Principal Stress	-3.149e+004 MPa	6256 MPa
Deformation	1.626e+006 mm	9.949e+006 mm
Safety Factor	3.325e-003	N/A

FIGURE 1

Equivalent Stress

FIGURE 2

Maximum Principal Stress

FIGURE 3

Minimum Principal Stress

FIGURE 4

Deformation

FIGURE 5

Safety Factor