Available online at www.sciencedirect.com Procedia Engineering 38 (2012 ) 264 269 Conference Title Contact Stress Distribution of Large Diameter Ball Bearing Using Hertzian Elliptical Contact Theory 1 Pandiyarajan.R, 2 Starvin.M.S, 3 Ganesh.K.C 1, 3. P.G Scholar, Anna University of Technology Tirunelveli 2. Assistant Professor, Anna University of Technology Tirunelveli Abstract The large diameter bearings (diameter >400mm) are of great importance in complex engineering mechanisms such as Aircraft gas turbines, Rolling Mills and Nuclear Reactor etc, in which varying load and critical environmental conditions leads to the failure of such bearings. Majorly spalling failure occurs due to contact mechanism. The contact mechanism of ball and raceway of bearing behaves highly non-linear and it reduces the service life of component considerably. This paper presents to determine the contact stress of large diameter ball bearings using analytical and numerical methods. In analytical method the contact stress is found out using the Hertzian Elliptical Contact Theory. The calculation procedure consists of calculation of the maximum contact pressure on the rolling element, which is done by the in-house developed program, and detailed finite element analysis of the contact between the ball and the raceway. The finite element analysis also performed to predict contact pressure in ball and raceway. Comparison of the results is made at the end. 2011 Published by Elsevier Ltd. Selection and/or peer-review under responsibility of [name organizer] Open access under CC BY-NC-ND license. Keywords: Hertzian elliptical contact theory, stress & displacement 1. Introduction A bearing may have to sustain severe static as well as cyclic loads while serving reliably in difficult environments. in both the radial and axial directions). The larger the contact angle, the higher the axial load supported, but the lower the radial load. It can take greater thrust load than maximum capacity of the ball bearing from only one direction. There are lots of researches developed to study the contact mechanics problems due to its nonlinear properties. This analysis used to study the failure behaviour at the contact zone and improving the contact behaviour to increase its service life. Basically the study starts with the components failure as 1877-7058 2012 Published by Elsevier Ltd. doi:10.1016/j.proeng.2012.06.034 Open access under CC BY-NC-ND license.
R. Pandiyarajan et al. / Procedia Engineering 38 ( 2012 ) 264 269 265 static contact [1], also to simplify the Hertzian contact problems the frictional effects in the analysis are not considered. The commercial numerical analysis packages like ANSYS, Abaqus, etc. are strongly proven its ability to predict the failure of component and the results can be justified through relevant experimental or mathematical models. The failure initiation, maximum load carrying capacity, life of components can be approximately predicted. Especially fatigue analysis to predict the minimum service life [5] on bearing is carried out by various researchers and the load carrying capacity and corresponding service life [7] are the important area of research to understand the component behaviour. NOMENCLATURE: A Distance between raceway groove curvature Centers at unloaded position, mm B Total conformity ratio d k d m Diameter of ball, mm Mean diameter of bearing, mm E Modulus of elasticity, N/mm 2 F I Curvature difference F a K i, K o K n Q Z Applied load, N Contact stiffness of ball and raceways Normal load deflection factor Ball-raceway normal load, N Number of rolling elements Curvature Sum, mm Contact angle, rad, o 0 Initial contact angle, rad, o n d k cos 0 / d m Normal deflection or contact deformation, mm 2. Mathematical modeling: 2.1Overview: Generally there are two contact classes: rigid-flexible and flexible-flexible. In rigid-flexible contact, one or more of the contacting surfaces are treated as rigid (i.e., it has a much higher stiffness compared to the deformable body it contacts). The other class flexible-flexible contact is the more common type. In this case, all contacting bodies are deformable (i.e., have similar stiffness). Contact analysis is highly nonlinear structure analysis. The nonlinearity of structure maybe comes from the following aspects. The contact stress refers to the localized stresses that develop as two curved surfaces come in contact and deform slightly under the imposed loads. The amount of deformation is dependent on the modulus of elasticity of the material in contact, Hertzian contact stress forms the foundation for the
266 R. Pandiyarajan et al. / Procedia Engineering 38 ( 2012 ) 264 269 equations for load bearing capabilities and fatigue life in bearings, gears, and other bodies where two surfaces are in contact. Failure from contact stresses generally falls into two categories: Localized deformations by yielding or distortions, and Fracture by progressive spreading of a crack (fatigue) 2.2Geometry of Ball Bearings: fig 1 geomaetry of ball bearing Race conformity is a measure of the geometrical conformity of the race and the ball in a plane passing through the bearing axis, which is a line passing through the center of the bearing perpendicular to its plane and transverse to the race. The race conformity can be expressed as f = r / D [1] Distance between raceway grooves curvatures Centers at unloaded position, A = BD [2] Where B = f o + f i 1 is known as the total conformity ratio and is a measure of the combined conformity of both the outer and inner races to the ball [3] Considering the geometry of two contacting solids (ellipsoids body 1 and 2) in a ball bearing we can arrive at the two quantities of some importance in the analysis of contact stresses and deformations. The curvature sum and curvature difference are expressed as [4] [5] 3. Hertzian Contact Stress Analysis: Contact problem definitions Fig.2. Contact analysis simplification [6]
R. Pandiyarajan et al. / Procedia Engineering 38 ( 2012 ) 264 269 267 a*, b [7] Normal deflection n i 0 [8] The calculated values of stresses should be less than allowable stresses. The maximum permissible compressive stress as referred by ANSI is 4000N/mm 2. 4. Contact stress Calculation: The introduction of numerical simulation has represented a considerable advance in this field. The numerical methods allow solving the differential equations that govern the process by solving in a computer an equivalent system of algebraic equations. The most popular of these methods to solve the Solids mechanics equations is the Finite Elements Method (FEM). The results of these models allow knowing accurately how the stresses and strains distributed along the component are, but the procedure to elaborate the appropriate fatigue calculations is not properly developed yet. The commercial packages that include the possibility of making this kind of calculations require the intervention of the user to give value to the parameters which characterize the fatigue behaviour of the different nodes in the model. This represents a hard work because of the great size of the realistic models or because of the difficulty of knowing the value of some of those parameters. In this paper, a methodology to calculate fatigue resistance by using FEM results of complex systems will be provided. 5. Procedure: Enumeration of the loads that will usually appear during the component life Determination of all the possible combinations of these loads, considering that each one of them can be present or not Determination of the stress distribution in the piece for each one of those load combinations. There will be so many complete stress solutions as load combinations calculated for each point of the solid. I associated to each one of the calculated stress states. I and determination of the associated principal direction. According to given explanations, it can be assumed that the fissure will progress (if it does) in a direction that is perpendicular to this one. For each other stress state that has been determined for the same point, calculation of the normal stress (with its sign) according to that privileged direction I max and the minor of those ones min [9]
268 R. Pandiyarajan et al. / Procedia Engineering 38 ( 2012 ) 264 269 6. Proposed Methodology: 7. Numerical Modelling: FEA is the familiar numerical modeling method used to analyze complex non-linear behaviours. The commercial software ANSYS Workbench.12.1 used as a FEA tool in this analysis work. By considering the hardware memory and reduction of CPU timing for the analysis, the model is reduced as shown in the fig. fig no 3 numerical modelling Further the reduced model is meshed using solid 187 elements by setting up the overall mesh size of 1 mm and the contact zone is meshed with contact size of 0.1 mm respectively. The reduced section comprises a half elliptical zone in the contact area with coefficient of friction 0.1. Corresponding loading conditions are setup in the load cases and applied on the top of ball while the race is fixed. The fatigue analysis followed by contact stress analysis is performed in the FEA. The results are displayed in the discussion topic. 8. Results and Discussions: Based on Hertzian contact theory the contact stress for variable loading condition is calculated. By setting up a program in MATLAB the contact stress are calculated and plotted graphically as follows, Fig.7. Contact pressure for max load Fig.8. Von Mises stress for max load Since the contact behaviour is a non-linear the stress extracted at the contact zone produces the parabolic curve for given incremental loading condition. Corresponding FEA is performed in order to justify the calculated contact stresses. The FEA results are plotted as fig.7and fig.8,
R. Pandiyarajan et al. / Procedia Engineering 38 ( 2012 ) 264 269 269 8.1Comparison of both results: The results of both analytical and FEA are compared and plotted which coincides satisfatoryly. 9. Conclusion: Non-linear behaviour of ball-raceway contact mechanism is studied based on Hertzian elliptical contact theory and corresponding numerical analysis performed by FEA. Initially the nonlinear finite element analysis is used for stress computation. Future work of this paper the stress history is then used to calculate the fatigue life of component. Fatigue life prediction by analytical and numerical model is performed to predict the service life of component for variable loading cases. This fatigue analysis can be used to understand the fatigue failure initiation life prediction of ball and race way contact problem. REFERENCES 1. Bernard J. Hamrock, William J. Anderson - 1983. 2. Yongming Liu, Brant Stratman, and Sankaran Mahadevan Journal of Fatigue 28, 2006, p 747 756. 3. A. Quesada, C. Álvarez-Caldas, E. Olmeda and J. L. San-Román,, 12th IFToMM World Congress, Besancon (France), June18-21, 2007. 4. W. Torbacki Journal of Achievements in Materials and Manufacturing Engineering, Volume 25, Issue 2, December 2007. 5. Rok Potocnik, Peter Goncz, Joze Flasker, Srecko Glodez, Irregular 6. Hassan Seyed Hassani, Ali Jafari, Seyed Saed Mohtasebi and Ali Mohammad Setayesh, Fatigue Analysis of Hydraulic Pump Gears Journal of American Science, 2010, p 62-67. 7. P. Goncz, R. Potocnik and S. Glodez, - 8. W.A. Glaeser, S.J. Shaffer -336. 9. Joseph E. Shigley, Charles R. Mischke, th edition, Chapter 7, 359-431. 10. Harris T, 11. Carmen Bujoreanu, Spiridon Cretu, - th international conference on tribology, France, 2003 12. Yuan Kanga, Ping-Chen Shenb, Chih-Ching Huangc, Shyh-Shyong Shyrc, Yeon-Pun Chang, Harris method for deep- 13. ilure analysis volume 4, 1997 14. Wang Chengbiao, Yu Xiang, Weng Lijun, Yu Deyang, -lubricated precise angular- 193, 2005 15. Yangang Wei, Yi Qinb, Raj Balendra, Qingyu Jiang, FE analysis of a novel roller form: a deep end-cavity roller for roller-type 241, 2004 16. Joel Hjalmarsson, Anes Memic FE Analysis of axial- project Thesis, 2010 17. V. S. Radchik and B. Ben-Nissan, 18. - ASME Journal Of Tribology. July 2005 19. : Application to 32CrMoV13.Nitrided. and M50 Steels 20. - Machine Theory 38, p 479 496, 2003