Figure 43. Some common mechanical systems involving contact.
|
|
- Merilyn Hill
- 6 years ago
- Views:
Transcription
1 33 Demonstration: experimental surface measurement ADE PhaseShift Whitelight Interferometer Surface measurement Surface characterization - Probability density function - Statistical analyses - Autocorrelation - Power spectrum - Fractal dimension Surface contact Contact of engineering surfaces - Power and motion are typically transmitted through an interface between mechanical components (power is lost and failure originates) - Some common examples: Gear teeth Cam and follower Rolling element bearing Figure 43. Some common mechanical systems involving contact. - Two major contact categories: 1. Conformal (highly conformal contacts have complicated mechanics usually solved through numerical computations by means of the finite element method) 2. Non-conformal, or counter-formal (solved analytically) Conformal contact Non-conformal contact Figure 44. Illustrations of conformal and non-conformal contact.
2 34 Contact of elastic bodies Based on Hertzian theories (1882) 1. Contact between two elastic cylinders (line contact) For no load, the contact footprint is a line (becomes a rectangle whose width is 2a as the load increases) Load P per unit length Figure 45. Schematic depiction of a line contact (Wang, 2002). - Contact half width: a = 4PR E * - Effective modulus: E* = E 1 - Effective radius: R = R 1 R 2 - Surface normal stress (pressure): (P /a) 1/2 1 E Pressure distribution: p(x) = 2P a 1 x 2 a 2 1/2 = PE * R 1 x 2 a 2 1/2 p(x) = 0 at x = a - Maximum pressure (at x = 0): p 0 = 2P a = PE * R 1/2 - a p(x) a x
3 35 - Stress distribution (3D within the body): Figure 46. Von Mises stress distribution due to the combined action of a contact pressure and frictional shear (Liu and Wang, 1999). - Maximum shear stress: 1 = 0.30p 0 at x = 0, z = 0.78a
4 36 2. Contact between two elastic spheres (point contact) For no load, the contact footprint is a point (becomes a circular area whose radius is a as the load increases) Figure 47. Schematic depiction of a point contact (Wang, 2002). - Contact radius: a = 3WR 4E * - Effective modulus: E* = E 1 1/3 E Effective radius: R = R 1 R 2 1 p(x,y) - Surface normal stress (pressure): (W /a 2 ) x - Pressure distribution: p(x, y) = 3W 2a 1 x 2 2 a y 2 2 a 2 1/2 p(x,y) = 0 at x = y = a y z W - Maximum pressure (at x = y = 0): p 0 = 3W 6WE *2 = 2 2a 3 R 2 - Normal approach (deformation): = a2 R = 9 W 2 16 RE * 2 1/3 1/3 2a
5 37 - Maximum shear stress: 1 = 0.31p 0 at r = 0, z = 0.48a - Maximum tensile stress: r = 1 3 (1 2) p 0 at r = a, z = 0 3. Extension of Hertzian theories - The above theories can also be used for the contact of a cylinder or sphere against a flat surface (R 2 = ) - The theories can also be used for conformal contact (R 2 is negative) Real area of contact Surface roughness significantly affects the contact between two bodies The true area of contact << the apparent area of contact The contact pressure (stresses) >> than the nominal contact pressure Figure 48. Contact stresses between asperities (Stachowiak and Batchelor, 2001). Contact of rough surfaces Greenwood and Williamson statistical model of multiple asperity contact (1966) z d Figure 49. Model for contact between a rough surface and a smooth rigid plane (Hutchings, 1992).
6 38 - All asperities are assumed to have spherical surfaces of the same radius r - Height of an individual asperity above the reference plane: z - Separation between the reference plane and the flat surface: d - If d < z, the asperity will be elastically compressed and will support a load w which can be predicted from Hertz s theory: w = 4 3 Er1/2 (z d) 3/2 - Asperity heights are statistically distributed The probability that a particular asperity has a height between z and z + dz will be (z)dz, where (z) is the probability density function describing the distribution of asperity heights (asperities are identified by neighboring height values) *Note that (z) is different from p(z), where p(z) is the probability density function of all surface heights - Probability that an asperity makes contact with the opposing plane surface = probability that its height z > plane of separation d: prob (z > d) = d (z)dz - For a total of N asperities on the surface, the expected number of contacts n is: n = N d (z)dz - The total load carried by all the asperities is W = 4 3 NEr1/2 (z d) 3/2 (z)dz d - The load W is linearly proportional to the total real area of contact Figure 50. Theoretical curve of true area of contact versus load for steel flats of 10 cm 2 nominal area (Hutchings, 1992).
7 39 - Plasticity index (proportion of asperity contacts at which plastic flow occurs) = E * H * r 1/2 where: E* = effective modulus of the two surfaces H = indentation hardness of the rough surface (a measure of the plastic flow stress of the asperities) * = standard deviation of the distribution of asperity heights Figure 51. Dependence of asperity deformation mode on plasticity index for aluminum surfaces with different roughness values (Hutchings, 1992). Thermoelastic deformation - Sliding between two interfaces creates frictional heating - The temperature increase on the surfaces can be calculated through thermodynamic equations - This frictional heating can cause thermoelastic surface deformations (when combined with the contact stresses, possibly resulting in thermally induced surface fatigue) - Frictional heating is usually locally concentrated at asperity contacts
8 40 Figure 52. Concentration of frictional energy at asperity contacts (Stachowiak and Batchelor, 2001). Example: Evolution of surface contact From: M.T. Siniawski, S.J. Harris, Q. Wang and S. Liu, Wear initiation of steel sliding against a thin boron carbide coating, Tribology Letters 15 n1, 2003, Background: A three-dimensional thermo-mechanical asperity contact model developed by Liu and Wang (2001) was used to model the contact evolution of a steel ball sliding against a B 4 C coated disc. The model takes into account steady-state heat transfer and asperity distortion due to thermoelastic deformations. Discrete convolution and FFT (DC-FFT) and a conjugate gradient method (CGM) were employed as the solution methods. By neglecting the thermal conductivity of the B 4 C coating (the thermal conductivity of the B 4 C coating is 92 W/m-K, whereas the thermal conductivity of steel is 46.6 W/m-K), the model treats the ball-disk contact as a steel surface contacting a rigid adiabatic plane, which gives an upper bound on the frictional heating.
9 41 Steel ball surface evolution Figure 53. Steel ball wear scar evolution for the first six data files (sliding distances).
10 42 Contact pressure evolution Figure 54. Evolution of the contact pressure contours for the first six data files (sliding distances), where the black dots represent regions of high contact pressure.
11 43 Evolution of the plastically deformed area Figure 55. Plastic deformation area as a function of sliding distance. Observations: Prior to wear initiation, the contact pressure is a highly concentrated circular patch. As the wear begins and sliding increases, the contact pressure becomes distributed over a larger surface area, corresponding to the increasing size of the wear scar. Although the overall size of the contact area increases with sliding distance, the size of the contact area experiencing plastic deformation remains nearly constant once wear begins. This result, that the nature of the contact is independent of the nominal contact area except for a spreading out of the contact points, is consistent with the Greenwood Williamson theory.
12 44 References Books K.L. Johnson, Contact Mechanics, Cambridge University Press, G.W. Stachowiak and A. W. Batchelor, Engineering Tribology, 2nd ed., Butterworth-Heinemann, Boston, I.M. Hutchings, Tribology: Friction and Wear of Engineering Materials, Edward Arnold, London, Articles G. Liu and Q. Wang, Thermoelastic Asperity Contacts, Frictional Shear and Parameter Correlation, ASME Journal of Tribology v122 n1, 1999, J.A. Greenwood and J.B.P. Williamson, Contact of nominally flat rough surface, Proceedings of the Royal Society of London A295, 1966, M.T. Siniawski, S.J. Harris, Q. Wang and S. Liu, Wear initiation of steel sliding against a thin boron carbide coating, Tribology Letters 15 n1, 2003, S. Liu and Q. Wang, A Three-Dimensional Thermomechanical Model of Contact Between Non-Conforming Rough Surfaces, ASME Journal of Tribology 123, 2001, Other Q. Wang, Introduction to Tribology, Lecture Notes, Northwestern University, 2002.
13 45 Homework 3 (Due 09/21/2006) Please complete the two problems listed below. Turn in a brief, typed report along with any created MATLAB programs, if appropriate. Problem 1 The contact stresses for gears in contact are typically determined through the AGMA formulas. However, the contact stress can also be directly determined through the methods discussed above. The diagram below shows the basic geometry of a pair of spur gears, where the base-circle radii are r b1 and r b2, the pitch-circle radii are r 1 and r 2. AP and BP are the radii of curvature for two gear teeth meshing at the pitch point. Figure 56. Basic geometry for a pair of spur gears in contact (Wang, 2002). If the pressure angle is = 20, the gear module is m = 5 mm, the numbers of teeth for the gears are N 1 = 20 and N 2 = 40, the materials are gear steel grade 1 (E = 210 GPa and hardness of 300 BHN), please determine the following: 1. The radii of curvature of the teeth at the pitch point. 2. The equivalent elastic modulus E* and the effective radius of curvature R, if we treat the tooth contact as a cylinder-plane contact. 3. The contact half width a, the maximum contact pressure p 0 and the normal approach, if the normal load is 40 kn/m. 4. The average pressure in the contact region. 5. How serious is the plastic deformation under this load? Does the material yield at all, or yield in the substrate only? Has surface flow been initiated?
14 46 Problem 2 Use the ASCII test surface data file for the worn surface, which is available from the course website. Find the asperity with the maximum height value and create a 2-D profile that includes this maximum asperity from the 3-D data set. The asperities can be approximated by spheres as shown below, where the radius of curvature is determined by means of the second-order differentiation of the data with the finite difference method: 1 R = 2z i z i1 z i+1 x 2 Figure 57. Finite difference approximation of the asperity tip radius (Wang, 2002). Please determine the following: 1. Identify the highest asperity and simplify it as a sphere whose height is that of the original asperity h and radius is that of the radius of curvature at the tip of the asperity R. 2. If this rough 2-D surface profile is for a typical steel (E = 210 GPa) that is now in contact with an ideally smooth surface of the same material, calculate the maximum contact pressure on this asperity when the normal approach is 1/5 of its height.
Contact Modeling of Rough Surfaces. Robert L. Jackson Mechanical Engineering Department Auburn University
Contact Modeling of Rough Surfaces Robert L. Jackson Mechanical Engineering Department Auburn University Background The modeling of surface asperities on the micro-scale is of great interest to those interested
More informationLecture Slides. Chapter 14. Spur and Helical Gears
Lecture Slides Chapter 14 Spur and Helical Gears The McGraw-Hill Companies 2012 Chapter Outline Cantilever Beam Model of Bending Stress in Gear Tooth Fig. 14 1 Lewis Equation Lewis Equation Lewis Form
More informationUniversity of Bath. Publication date: Document Version Early version, also known as pre-print. Link to publication
Citation for published version: Evans, M, Akehurst, S & Keogh, P 2014, 'Wear mechanisms in polyoxymethylene (POM) spur gears' Paper presented at 5th World Tribology Congress, WTC 2013, Torino, UK United
More informationInvestigations On Gear Tooth Surface And Bulk Temperatures Using ANSYS
Investigations On Gear Tooth Surface And Bulk Temperatures Using ANSYS P R Thyla PSG College of Technology, Coimbatore, INDIA R Rudramoorthy PSG College of Technology, Coimbatore, INDIA Abstract In gears,
More informationA Finite Element Study of Elastic-Plastic Hemispherical Contact Behavior against a Rigid Flat under Varying Modulus of Elasticity and Sphere Radius
Engineering, 2010, 2, 205-211 doi:10.4236/eng.2010.24030 Published Online April 2010 (http://www. SciRP.org/journal/eng) 205 A Finite Element Study of Elastic-Plastic Hemispherical Contact Behavior against
More informationCONTACT MODEL FOR A ROUGH SURFACE
23 Paper presented at Bucharest, Romania CONTACT MODEL FOR A ROUGH SURFACE Sorin CĂNĂNĂU Polytechnic University of Bucharest, Dep. of Machine Elements & Tribology, ROMANIA s_cananau@yahoo.com ABSTRACT
More informationLECTURE NOTES ENT345 MECHANICAL COMPONENTS DESIGN Lecture 6, 7 29/10/2015 SPUR AND HELICAL GEARS
LECTURE NOTES ENT345 MECHANICAL COMPONENTS DESIGN Lecture 6, 7 29/10/2015 SPUR AND HELICAL GEARS Dr. HAFTIRMAN MECHANICAL ENGINEEERING PROGRAM SCHOOL OF MECHATRONIC ENGINEERING UniMAP COPYRIGHT RESERVED
More informationEFFECT OF STRAIN HARDENING ON ELASTIC-PLASTIC CONTACT BEHAVIOUR OF A SPHERE AGAINST A RIGID FLAT A FINITE ELEMENT STUDY
Proceedings of the International Conference on Mechanical Engineering 2009 (ICME2009) 26-28 December 2009, Dhaka, Bangladesh ICME09- EFFECT OF STRAIN HARDENING ON ELASTIC-PLASTIC CONTACT BEHAVIOUR OF A
More informationA FINITE ELEMENT STUDY OF ELASTIC-PLASTIC HEMISPHERICAL CONTACT BEHAVIOR AGAINST A RIGID FLAT UNDER VARYING MODULUS OF ELASTICITY AND SPHERE RADIUS
Proceedings of the International Conference on Mechanical Engineering 2009 (ICME2009) 26-28 December 2009, Dhaka, Bangladesh ICME09- A FINITE ELEMENT STUDY OF ELASTIC-PLASTIC HEMISPHERICAL CONTACT BEHAVIOR
More information12/25/ :27 PM. Chapter 14. Spur and Helical Gears. Mohammad Suliman Abuhaiba, Ph.D., PE
Chapter 14 Spur and Helical Gears 1 2 The Lewis Bending Equation Equation to estimate bending stress in gear teeth in which tooth form entered into the formulation: 3 The Lewis Bending Equation Assume
More informationME 383S Bryant February 17, 2006 CONTACT. Mechanical interaction of bodies via surfaces
ME 383S Bryant February 17, 2006 CONTACT 1 Mechanical interaction of bodies via surfaces Surfaces must touch Forces press bodies together Size (area) of contact dependent on forces, materials, geometry,
More informationArbitrary Normal and Tangential Loading Sequences for Circular Hertzian Contact
Arbitrary Normal and Tangential Loading Sequences for Circular Hertzian Contact Philip P. Garland 1 and Robert J. Rogers 2 1 School of Biomedical Engineering, Dalhousie University, Canada 2 Department
More informationReview of Thermal Joint Resistance Models for Non-Conforming Rough Surfaces in a Vacuum
Review of Thermal Joint Resistance Models for Non-Conforming Rough Surfaces in a Vacuum M. Bahrami J. R. Culham M. M. Yovanovich G. E. Schneider Department of Mechanical Engineering Microelectronics Heat
More informationExperimental Investigation of Fully Plastic Contact of a Sphere Against a Hard Flat
J. Jamari e-mail: j.jamari@ctw.utwente.nl D. J. Schipper University of Twente, Surface Technology and Tribology, Faculty of Engineering Technology, Drienerloolaan 5, Postbus 17, 7500 AE, Enschede, The
More informationON THE EFFECT OF SPECTRAL CHARACTERISTICS OF ROUGHNESS ON CONTACT PRESSURE DISTIRBUTION
7 Paper present at International Conference on Diagnosis and Prediction in Mechanical Engineering Systems (DIPRE 09) 22-23 October 2009, Galati, Romania ON THE EFFECT OF SPECTRAL CHARACTERISTICS OF ROUGHNESS
More informationContact Stress Analysis of Spur Gear Teeth Pair
ontact Stress Analysis of Spur Gear Teeth Pair Ali Raad Hassan Abstract ontact stress analysis between two spur gear teeth was considered in different contact positions, representing a pair of mating gears
More informationUNLOADING OF AN ELASTIC-PLASTIC LOADED SPHERICAL CONTACT
2004 AIMETA International Tribology Conference, September 14-17, 2004, Rome, Italy UNLOADING OF AN ELASTIC-PLASTIC LOADED SPHERICAL CONTACT Yuri KLIGERMAN( ), Yuri Kadin( ), Izhak ETSION( ) Faculty of
More informationA Finite Element Study of the Residual Stress and Deformation in Hemispherical Contacts
obert Jackson 1 Mem. ASME e-mail: robert.jackson@eng.auburn.edu Itti Chusoipin Itzhak Green Fellow, ASME George W. Woodruff School of Mechanical Engineering, Georgia Institute of Technology, Atlanta, GA
More informationNormal contact and friction of rubber with model randomly rough surfaces
Normal contact and friction of rubber with model randomly rough surfaces S. Yashima 1-2, C. Fretigny 1 and A. Chateauminois 1 1. Soft Matter Science and Engineering Laboratory - SIMM Ecole Supérieure de
More informationAbstract. 1 Introduction
Elasto-plastic contact of rough surfaces K. Willner Institute A of Mechanics, University of Stuttgart, D-70550 Stuttgart, Germany E-mail: willner@mecha. uni-stuttgart. de Abstract If two rough surfaces
More informationContact Stress Analysis of Spur Gear Teeth Pair
Vol:3, No:0, 009 ontact Stress Analysis of Spur Gear Teeth Pair Ali Raad Hassan International Science Index, Mechanical and Mechatronics Engineering Vol:3, No:0, 009 waset.org/publication/365 Abstract
More informationADHESION OF AN AXISYMMETRIC ELASTIC BODY: RANGES OF VALIDITY OF MONOMIAL APPROXIMATIONS AND A TRANSITION MODEL
ADHESION OF AN AXISYMMETRIC ELASTIC BODY: RANGES OF VALIDITY OF MONOMIAL APPROXIMATIONS AND A TRANSITION MODEL A Thesis Presented By Fouad Oweiss to The Department of Mechanical and Industrial Engineering
More informationNotes on Rubber Friction
Notes on Rubber Friction 2011 A G Plint Laws of Friction: In dry sliding between a given pair of materials under steady conditions, the coefficient of friction may be almost constant. This is the basis
More informationTRACTION AND WEAR MECHANISMS DURING ROLL-SLIP CONTACT
TRACTION AND WEAR MECHANISMS DURING ROLL-SLIP CONTACT J. De Pauw 1, J. Van Wittenberghe 1, P. De Baets 1 1 Ghent University, Laboratory Soete, Belgium Abstract In the transportation industry every vehicle
More informationANALYTICAL MODEL FOR FRICTION FORCE BETWEEN A STEEL ROLLER AND A PLANE POLYMER SAMPLE IN SLIDING MOTION
6 th International Conference Computational Mechanics and Virtual Engineering COMEC 015 15-16 October 015, Braşov, Romania ANALYTICAL MODEL FOR FRICTION FORCE BETWEEN A STEEL ROLLER AND A PLANE POLYMER
More informationTribology Prof. Dr. Harish Hirani Department of Mechanical Engineering Indian Institute Of Technology, Delhi Module No. # 06
Tribology Prof. Dr. Harish Hirani Department of Mechanical Engineering Indian Institute Of Technology, Delhi Module No. # 06 Lecture No. # 37 Friction and Lubrication of Gears (Contd.) Hello and welcome
More informationFINITE ELEMENT ANALYSIS OF SLIDING CONTACT BETWEEN A CIRCULAR ASPERITY AND AN ELASTIC URFACE IN PLANE STRAIN CONDITION
7 th International LS-DYNA Users Conference Simulation Technology (1) FINITE ELEMENT ANALYSIS OF SLIDING CONTACT BETWEEN A CIRCULAR ASPERITY AND AN ELASTIC URFACE IN PLANE STRAIN CONDITION S. Subutay Akarca,
More informationChapter 2 A Simple, Clean-Metal Contact Resistance Model
Chapter A Simple, Clean-Metal Contact Resistance Model A contact resistance model is presented in this chapter. The model assumes that the contact surfaces are clean, that is, there are no insulating films
More informationTuesday, February 11, Chapter 3. Load and Stress Analysis. Dr. Mohammad Suliman Abuhaiba, PE
1 Chapter 3 Load and Stress Analysis 2 Chapter Outline Equilibrium & Free-Body Diagrams Shear Force and Bending Moments in Beams Singularity Functions Stress Cartesian Stress Components Mohr s Circle for
More informationA COMPACT MODEL FOR SPHERICAL ROUGH CONTACTS
A COMPACT MODEL FOR SPHERICAL ROUGH CONTACTS Majid Bahrami M. M. Yovanovich J. R. Culham Microelectronics Heat Transfer Laboratory Department of Mechanical Engineering University of Waterloo Ontario, Canada
More informationElastic-plastic Contact of a Deformable Sphere Against a Rigid Flat for Varying Material Properties Under Full Stick Contact Condition
B. CHATTERJEE, P. SAHOO Elastic-plastic Contact of a Deformable Sphere Against a Rigid Flat for Varying Material Properties Under Full Stick Contact Condition RESEARCH The present study considers finite
More informationDeterministic repeated contact of rough surfaces
Available online at www.sciencedirect.com Wear 264 (2008) 349 358 Deterministic repeated contact of rough surfaces J. Jamari, D.J. Schipper Laboratory for Surface Technology and Tribology, Faculty of Engineering
More informationUnloading of an elastic plastic loaded spherical contact
International Journal of Solids and Structures 42 (2005) 3716 3729 www.elsevier.com/locate/ijsolstr Unloading of an elastic plastic loaded spherical contact I. Etsion *, Y. Kligerman, Y. Kadin Department
More informationFriction Properties of Surface with Circular Micro-patterns
Friction Properties of Surface with Circular Micro-patterns Hideo Koguchi Mechanical Engineering, 603- Kamitomioka, Nagaoka Univ. of Tech., Nagaoka, Niigata, Japan Email: koguchi@mech.nagaokaut.ac.jp Takayoshi
More informationA CONTACT-MECHANICS BASED MODEL FOR DISHING AND EROSION IN
Mat. Res. Soc. Symp. Proc. Vol. 671 001 Materials Research Society A CONTACT-MECHANICS BASED MODEL FOR DISHING AND EROSION IN CHEMICAL-MECHANICAL POLISHING Joost J. Vlassak Division of Engineering and
More informationInfluential Factors on Adhesion between Wheel and Rail under Wet Conditions
Influential Factors on Adhesion between Wheel and Rail under Wet Conditions H. Chen, M. Ishida, 2 T. Nakahara Railway Technical Research Institute, Tokyo, Japan ; Tokyo Institute of Technology, Tokyo,
More information8. Contact Mechanics DE2-EA 2.1: M4DE. Dr Connor Myant 2017/2018
DE2-EA 2.1: M4DE Dr Connor Myant 2017/2018 8. Contact Mechanics Comments and corrections to connor.myant@imperial.ac.uk Lecture resources may be found on Blackboard and at http://connormyant.com Contents
More informationAME COMPUTATIONAL MULTIBODY DYNAMICS. Friction and Contact-Impact
1 Friction AME553 -- COMPUTATIONAL MULTIBODY DYNAMICS Friction and Contact-Impact Friction force may be imposed between contacting bodies to oppose their relative motion. Friction force can be a function
More informationFRICTION AND WEAR OF CARBON-CARBON COMPOSITE PART 2: TEMPERATURE AND STRESS FIELDS ANALYSIS
FRICTION AND WEAR OF CARBON-CARBON COMPOSITE PART 2: TEMPERATURE AND STRESS FIELDS ANALYSIS Kia-Moh Teo and Khalid Lafdi NSF-University-Industry Center For Advanced Friction Studies, Southern Illinois
More informationStiffness and deformation of asperities in a rough contact
Stiffness and deformation of asperities in a rough contact A. Haiahem ^\ L. Flamand ^ Institut de mecanique universite de Annaba, BP 12 Annaba 23000 Algerie Laboratoire de mecanique des contacts INS A
More informationLesson of Mechanics and Machines done in the 5th A-M, by the teacher Pietro Calicchio. THE GEARS CYLINDRICAL STRAIGHT TEETH GEARS
MESA PROJECT Lesson of Mechanics and Machines done in the 5th A-M, 2012-2013 by the teacher Pietro Calicchio. THE GEARS To transmit high power are usually used gear wheels. In this case, the transmission
More informationThree-dimensional thermo-mechanical analysis of layered elasticlplastic solids
Three-dimensional thermo-mechanical analysis of layered elasticlplastic solids W. Peng & Y.-T. Hsia Seagate Technology, U.S.A. Abstract At high temperature a layered solid undergoes intense thermal loading
More informationTE 75R RESEARCH RUBBER FRICTION TEST MACHINE
TE 75R RESEARCH RUBBER FRICTION TEST MACHINE Background: The Research Rubber Friction Test Machine offers the ability to investigate fully the frictional behaviour of rubbery materials both in dry and
More informationEMA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 3 Torsion
EMA 3702 Mechanics & Materials Science (Mechanics of Materials) Chapter 3 Torsion Introduction Stress and strain in components subjected to torque T Circular Cross-section shape Material Shaft design Non-circular
More informationNew Representation of Bearings in LS-DYNA
13 th International LS-DYNA Users Conference Session: Aerospace New Representation of Bearings in LS-DYNA Kelly S. Carney Samuel A. Howard NASA Glenn Research Center, Cleveland, OH 44135 Brad A. Miller
More informationSample Questions for the ME328 Machine Design Final Examination Closed notes, closed book, no calculator.
Sample Questions for the ME328 Machine Design Final Examination Closed notes, closed book, no calculator. The following is from the first page of the examination. I recommend you read it before the exam.
More informationAnalysis of contact deformation between a coated flat plate and a sphere and its practical application
Computer Methods and Experimental Measurements for Surface Effects and Contact Mechanics VII 307 Analysis of contact deformation between a coated flat plate and a sphere and its practical application T.
More information[7] Torsion. [7.1] Torsion. [7.2] Statically Indeterminate Torsion. [7] Torsion Page 1 of 21
[7] Torsion Page 1 of 21 [7] Torsion [7.1] Torsion [7.2] Statically Indeterminate Torsion [7] Torsion Page 2 of 21 [7.1] Torsion SHEAR STRAIN DUE TO TORSION 1) A shaft with a circular cross section is
More informationChapter 3. Load and Stress Analysis. Lecture Slides
Lecture Slides Chapter 3 Load and Stress Analysis 2015 by McGraw Hill Education. This is proprietary material solely for authorized instructor use. Not authorized for sale or distribution in any manner.
More informationMECH 401 Mechanical Design Applications
MECH 401 Mechanical Design Applications Dr. M. O Malley Master Notes Spring 008 Dr. D. M. McStravick Rice University Updates HW 1 due Thursday (1-17-08) Last time Introduction Units Reliability engineering
More informationAn analysis of elasto-plastic sliding spherical asperity interaction
Wear 262 (2007) 210 219 An analysis of elasto-plastic sliding spherical asperity interaction Robert L. Jackson, Ravi S. Duvvuru, Hasnain Meghani, Manoj Mahajan Department of Mechanical Engineering, Auburn
More informationEffect of Strain Hardening on Unloading of a Deformable Sphere Loaded against a Rigid Flat A Finite Element Study
Effect of Strain Hardening on Unloading of a Deformable Sphere Loaded against a Rigid Flat A Finite Element Study Biplab Chatterjee, Prasanta Sahoo 1 Department of Mechanical Engineering, Jadavpur University
More informationInternational Journal of Advance Engineering and Research Development
Scientific Journal of Impact Factor(SJIF): 3.134 e-issn(o): 2348-4470 p-issn(p): 2348-6406 International Journal of Advance Engineering and Research Development Volume 2,Issue 5, May -2015 A REVIEW OF
More informationExamination of finite element analysis and experimental results of quasi-statically loaded acetal copolymer gears
Examination of finite element analysis and experimental results of quasi-statically loaded acetal copolymer gears Paul Wyluda Ticona Summit, NJ 07901 Dan Wolf MSC Palo Alto, CA 94306 Abstract An elastic-plastic
More informationA statistical model of elasto-plastic asperity contact between rough surfaces
Tribology International 39 (2006) 906 914 www.elsevier.com/locate/triboint A statistical model of elasto-plastic asperity contact between rough surfaces Robert L. Jackson a,, Itzhak Green b a Department
More informationCHAPTER 7 FINITE ELEMENT ANALYSIS OF DEEP GROOVE BALL BEARING
113 CHAPTER 7 FINITE ELEMENT ANALYSIS OF DEEP GROOVE BALL BEARING 7. 1 INTRODUCTION Finite element computational methodology for rolling contact analysis of the bearing was proposed and it has several
More informationRoughness picture of friction in dry nanoscale contacts
Roughness picture of friction in dry nanoscale contacts Yifei Mo 1 and Izabela Szlufarska 1,2 1 Materials Science Program, University of Wisconsin, Madison, Wisconsin 53706-1595, USA 2 Department of Materials
More informationContact Mechanics and Elements of Tribology
Contact Mechanics and Elements of Tribology Lectures 2-3. Mechanical Contact Vladislav A. Yastrebov MINES ParisTech, PSL Research University, Centre des Matériaux, CNRS UMR 7633, Evry, France @ Centre
More informationA General Equation for Fitting Contact Area and Friction vs Load Measurements
Journal of Colloid and Interface Science 211, 395 400 (1999) Article ID jcis.1998.6027, available online at http://www.idealibrary.com on A General Equation for Fitting Contact Area and Friction vs Load
More informationElastic-plastic deformation near the contact surface of the circular disk under high loading
Elastic-plastic deformation near the contact surface of the circular disk under high loading T. Sawada & M. Horiike Department of Mechanical Systems Engineering Tokyo University of Agriculture and Technology,
More informationStress Distribution Analysis in Non-Involute Region of Spur Gear
Stress Distribution Analysis in Non-Involute Region of Spur Gear Korde A. 1 & Soni S 2 1 Department of Mechanical Engineering, Faculty of Technology and Bionics Hochschule Rhein-Waal, Kleve, NRW, Germany,
More informationAn Analysis of Elastic Rough Contact Models. Yang Xu
An Analysis of Elastic Rough Contact Models by Yang Xu A thesis submitted to the Graduate Faculty of Auburn University in partial fulfillment of the requirements for the Degree of Master of Science Auburn,
More informationDesign and Analysis of Helical Elliptical Gear using ANSYS
e t International Journal on Emerging Technologies 6(2): 152-156(2015) ISSN No. (Print) : 0975-8364 ISSN No. (Online) : 2249-3255 Design and Analysis of Helical Elliptical Gear using ANSYS Ms. Farheen
More informationImpact and Fracture Mechanics Assessment of a Fused Silica Window
Arnold AFB Wind Tunnel Impact and Fracture Mechanics Analysis Rev-0 1 of 41 Impact and Fracture Mechanics Assessment of a Fused Silica Window Objective: Determine the survival probability of a fused silica
More informationA Finite Element Study of an Elastic- Plastic Axisymmetric Sinusoidal Surface Asperity in Contact Against a Rigid Flat with Strain Hardening
A Finite Element Study of an Elastic- Plastic Axisymmetric Sinusoidal Surface Asperity in Contact Against a Rigid Flat with Strain Hardening by Geetanj Bhandari A thesis submitted to the Graduate Faculty
More informationTransactions on Engineering Sciences vol 1, 1993 WIT Press, ISSN
A stress analysis for contact problems involving rolling and sliding 0. Koca*^, F.-G. BuchhoW* "Institute of Strength of Materials, University of Tirana, Tirana, Albania ^Institute of Applied Mechanics,
More informationPES Institute of Technology
PES Institute of Technology Bangalore south campus, Bangalore-5460100 Department of Mechanical Engineering Faculty name : Madhu M Date: 29/06/2012 SEM : 3 rd A SEC Subject : MECHANICS OF MATERIALS Subject
More informationStress Analysis Lecture 3 ME 276 Spring Dr./ Ahmed Mohamed Nagib Elmekawy
Stress Analysis Lecture 3 ME 276 Spring 2017-2018 Dr./ Ahmed Mohamed Nagib Elmekawy Axial Stress 2 Beam under the action of two tensile forces 3 Beam under the action of two tensile forces 4 Shear Stress
More informationNano-Scale Effect in Adhesive Friction of Sliding Rough Surfaces
Journal of Nanoscience and Nanoengineering Vol. 1, No. 4, 015, pp. 06-13 http://www.aiscience.org/journal/jnn Nano-Scale Effect in Adhesive Friction of Sliding Rough Surfaces Prasanta Sahoo * Department
More informationA finite element study of the deformations, forces, stress formations, and energy losses in sliding cylindrical contacts
International Journal of Non-Linear Mechanics 4 (7) 914 97 www.elsevier.com/locate/nlm A finite element study of the deformations, forces, stress formations, and energy losses in sliding cylindrical contacts
More informationTransient Analysis of Disk Brake By using Ansys Software
Transient Analysis of Disk Brake By using Ansys Software G. Babukanth & M. Vimal Teja Department of Mechanical Engineering, Nimra College of Engineering & Technology, Ibrahimpatnam, Vijayawada E-mail :
More informationSOLUTION (17.3) Known: A simply supported steel shaft is connected to an electric motor with a flexible coupling.
SOLUTION (17.3) Known: A simply supported steel shaft is connected to an electric motor with a flexible coupling. Find: Determine the value of the critical speed of rotation for the shaft. Schematic and
More informationCHAPTER 3 TOOTH GEOMETRY
1 CHAPTER 3 TOOTH GEOMETRY 3.1 GEOMETRIC PARAMETERS Figure 3.1 shows a portion of the involute curve bounded by the outside where root diameters have been used as tooth profile. In a properly designed
More informationChapter 5 Torsion STRUCTURAL MECHANICS: CE203. Notes are based on Mechanics of Materials: by R. C. Hibbeler, 7th Edition, Pearson
STRUCTURAL MECHANICS: CE203 Chapter 5 Torsion Notes are based on Mechanics of Materials: by R. C. Hibbeler, 7th Edition, Pearson Dr B. Achour & Dr Eng. K. El-kashif Civil Engineering Department, University
More informationContents. Chapter 1 Introduction Chapter 2 Unacceptable Cam Curves Chapter 3 Double-Dwell Cam Curves... 27
Contents Chapter 1 Introduction... 1 1.0 Cam-Follower Systems... 1 1.1 Fundamentals... 1 1.2 Terminology... 4 Type of Follower Motion... 4 Type of Joint Closure... 4 Type of Follower... 5 Type of Cam...
More informationUnderstanding the Life of Power Transmission Elements of Wind Turbine Systems
Understanding the Life of Power Transmission Elements of Wind Turbine Systems Jian Cao and Q. Jane Wang Northwestern University March 2010 Northwestern University 2/22 Wind Resource Assessment 3/22 Google
More informationChemical Mechanical Planarization
Mechanics of Contact and Lubrication, MTM G230 Department of Mechanical & Industrial Enineering Northeastern University Spring 2006 Chemical Mechanical Planarization George Calota Northeastern University
More informationINFLUENCE OF NORMAL FORCE AND HUMIDITY ON FRICTION AND WEAR OF UNLUBRICATED STEEL/ STEEL COUPLES
INFLUENCE OF NORMAL FORCE AND HUMIDITY ON FRICTION AND WEAR OF UNLUBRICATED STEEL/ STEEL COUPLES D. KLAFFKE Federal Institute for Materials Research and Testing (BAM), Lab. VIII.2, Unter den Eichen 87,
More informationA Project on Wear and its Relation to Ball Valves. A project for MANE 6960 By Robert Sayre Submitted 12/9/2013
A Project on Wear and its Relation to Ball Valves A project for MANE 6960 By Robert Sayre Submitted 12/9/2013 Introduction Ball valves have many possible applications; they typically have low pressure
More informationGear Surface Roughness Induced Noise Prediction Based on a Linear Time-varying Model with Sliding Friction
Gear Surface Roughness Induced Noise Prediction Based on a Linear Time-varying Model with Sliding Friction SEUNGBO KIM RAJENDRA SINGH Acoustics and Dynamics Laboratory, Department of Mechanical Engineering
More informationThermal Contact Resistance of Nonconforming Rough Surfaces, Part 1: Contact Mechanics Model
JOURNAL OF THERMOPHYSICS AND HEAT TRANSFER Vol. 18, No. 2, April June 24 Thermal Contact Resistance of Nonconforming Rough Surfaces, Part 1: Contact Mechanics Model M. Bahrami, J. R. Culham, M. M. Yovanovich,
More informationComputational Modelling of the Surface Roughness Effects on the Thermal-elastohydrodynamic Lubrication Problem
Proceedings of the International Conference on Heat Transfer and Fluid Flow Prague, Czech Republic, August 11-12, 2014 Paper No. 192 Computational Modelling of the Surface Roughness Effects on the Thermal-elastohydrodynamic
More informationBoundary Conditions in Fluid Mechanics
Boundary Conditions in Fluid Mechanics R. Shankar Subramanian Department of Chemical and Biomolecular Engineering Clarkson University The governing equations for the velocity and pressure fields are partial
More informationD : SOLID MECHANICS. Q. 1 Q. 9 carry one mark each. Q.1 Find the force (in kn) in the member BH of the truss shown.
D : SOLID MECHANICS Q. 1 Q. 9 carry one mark each. Q.1 Find the force (in kn) in the member BH of the truss shown. Q.2 Consider the forces of magnitude F acting on the sides of the regular hexagon having
More information! Importance of Particle Adhesion! History of Particle Adhesion! Method of measurement of Adhesion! Adhesion Induced Deformation
! Importance of Particle Adhesion! History of Particle Adhesion! Method of measurement of Adhesion! Adhesion Induced Deformation! JKR and non-jkr Theory! Role of Electrostatic Forces! Conclusions Books:
More informationFriction of Polymer/Steel Gear Pairs
Friction of Polymer/Steel Gear Pairs Róbert KERESZTES, László ZSIDAI, Gábor KALÁCSKA, Mátyás ANDÓ and Rajmund LEFÁNTI Department of Maintenance of Machinery, Institute for Mechanical Engineering Technology
More information1. What would be the value of F1 to balance the system if F2=20N? 20cm T =? 20kg
1. What would be the value of F1 to balance the system if F2=20N? F2 5cm 20cm F1 (a) 3 N (b) 5 N (c) 4N (d) None of the above 2. The stress in a wire of diameter 2 mm, if a load of 100 gram is applied
More informationTHE WEAR OF GEAR TEETH WITH FUNCTIONALITY IN ABRASIVE RANDOMLY PARTICLES
UPB Sci Bull, Series D, Vol 7, Iss, 10 ISSN 1454-358 THE WEAR OF GEAR TEETH WITH FUNCTIONALITY IN ABRASIVE RANDOMLY PARTICLES Monica VLASE 1, Andrei TUDOR Se arată că particulele abrazive ce pătrund în
More informationHelical Gears n A Textbook of Machine Design
1066 n A Textbook of Machine Design C H A P T E R 9 Helical Gears 1. Introduction.. Terms used in Helical Gears. 3. Face Width of Helical Gears. 4. Formative or Equivalent Number of Teeth for Helical Gears.
More informationSpur Gear Des Mach Elem Mech. Eng. Department Chulalongkorn University
Spur Gear 10330 Des Mach Elem Mech. Eng. Department Chulalongkorn University Introduction Gear Transmit power, rotation Change torque, rotational speed Change direction of rotation Friction Gear + + Slip
More informationSURFACE SEPARATION AND CONTACT RESISTANCE CONSIDERING SINUSOIDAL ELASTIC-PLASTIC MULTISCALE ROUGH SURFACE CONTACT
SURFACE SEPARATION AND CONTACT RESISTANCE CONSIDERING SINUSOIDAL ELASTIC-PLASTIC MULTISCALE ROUGH SURFACE CONTACT Except where reference is made to the work of others, the work described in this thesis
More informationModeling of the Rolling and Sliding Contact Between Two Asperities
Modeling of the Rolling and Sliding Contact Between Two Asperities Vincent Boucly Daniel Nélias LaMCoS, UMR CNRS 5259, INSA Lyon, 69621, Villeurbanne Cedex, France Itzhak Green George W. Woodruff School
More informationEvaluation and Description of Friction between an Electro-Deposited Coating and a Ceramic Ball under Fretting Condition
Materials 25, 8, 4778-4789; doi:.339/ma884778 Article OPEN ACCESS materials ISSN 996-944 www.mdpi.com/journal/materials Evaluation and Description of Friction between an Electro-Deposited Coating and a
More information2191. Dynamic analysis of torus involute gear including transient elastohydrodynamic effects
2191. Dynamic analysis of torus involute gear including transient elastohydrodynamic effects Lei Liu 1, Jingwen Tan 2 College of Mechanical and Electrical Engineering, Nanjing University of Aeronautics
More informationBS-ISO helical gear fatigue life estimation and debris analysis validation
BS-ISO helical gear fatigue life estimation and debris analysis validation Muhammad Ali Khan 1, a, Dennis Cooper 2 and Andrew Starr 1 1 Extreme loading and design research group, School of Mechanical,
More informationStudy of Circular and Elliptical Holes as a Stress Relieving Feature in Spur Gear
Study of Circular and Elliptical Holes as a Stress Relieving Feature in Spur Gear Prof. S.B.Naik 1, Mr. Sujit R. Gavhane 2 Asst. Prof. Department of Mechanical Engineering, Walchand Institute of Technology,
More informationDesign against fluctuating load
Design against fluctuating load In many applications, the force acting on the spring is not constants but varies in magnitude with time. The valve springs of automotive engine subjected to millions of
More informationMECHANICS OF MATERIALS
2009 The McGraw-Hill Companies, Inc. All rights reserved. Fifth SI Edition CHAPTER 3 MECHANICS OF MATERIALS Ferdinand P. Beer E. Russell Johnston, Jr. John T. DeWolf David F. Mazurek Torsion Lecture Notes:
More informationANALYSIS OF GATE 2018*(Memory Based) Mechanical Engineering
ANALYSIS OF GATE 2018*(Memory Based) Mechanical ME Industrial 4% General Aptitude 15% Mathematics 14% Mechanics 4% Manufacturing 14% Mechanics of Materials 14% Thermodynamics 10% Heat Transfer 2% Fluid
More informationModeling of Thermal Joint Resistance for. Rough Sphere-Flat Contact in a Vacuum
Modeling of Thermal Joint Resistance for Rough Sphere-Flat Contact in a Vacuum by Majid Bahrami A research proposal Presented to University of Waterloo Department of Mechanical Engineering In fulfillment
More information