Abstract
The present study deals with numerical simulation of textured hybrid thrust pad bearing. Influence of providing micro-dimples of different cross-sectional shapes on the bearing surface has been theoretically investigated on the performance of thrust pad bearing. Reynolds equation has been solved using mass-conserving algorithm based on Jakobsson–Floberg–Olsson cavitation boundary conditions. A parametric study is carried out to optimize dimple shapes from the viewpoint of load carrying capacity of bearings. The textured bearing surface is noticed to be beneficial in reducing the frictional power losses. Providing half-section dimples (second half in the direction of runner rotation) towards the leading edge of thrust pad, enhance the load carrying capacity and fluid film stiffness coefficient of bearings. Micro-roughness in a textured surface having transverse orientation is seen to improve the dynamic characteristics of hybrid thrust pad bearings.
Similar content being viewed by others
Abbreviations
- \(A_{b}\) :
-
Area of bearing \((\pi r_{o}^{2} )\) (mm2)
- \(A_{p}\) :
-
Area of 1/32th thrust pad surface \(\left( {\frac{\pi }{32}\left( {r_{o}^{2} - r_{i}^{2} } \right)} \right)\) (mm2)
- \(A_{t}\) :
-
Area of dimples/textures \((N_{d} *\pi r_{d}^{2} )\) (mm2)
- \(A_{oc}\) :
-
Area of recess \((\pi r_{i}^{2} )\) (mm2)
- \(A_{d}\) :
-
Area density of texture \(\left( {A_{d} = \frac{{A_{t} }}{{A_{p} }}} \right)\)
- \(\bar{A}_{r}\) :
-
Bearing to recess area ratio \((A_{b} /A_{oc} )\)
- \(C\) :
-
Damping coefficient of fluid film (N s/m) \(\left( {\bar{C} = \frac{{h_{o}^{3} }}{{r_{o}^{4} \mu }}C} \right)\)
- \(h_{d}\) :
-
Depth of micro-dimples (µm) \(\left( {\bar{h}_{d} = h_{d} /h_{o} } \right)\)
- \(F_{o}\) :
-
Fluid film reaction (N) \(\bar{F}_{o} = \left( {\frac{{F_{o} }}{{p_{s} r_{o}^{2} }}} \right)\)
- h :
-
Lubricant film thickness (mm) \(\left( {\bar{h} = h/h_{o} } \right)\)
- \(\dot{h}\) :
-
Squeeze velocity, (mm/s) \(\left( {\overline{{\dot{h}}} = \frac{{\partial \bar{h}}}{{\partial \bar{t}}}} \right)\)
- \(h_{o}\) :
-
Reference film thickness (mm)
- \(h_{T}\) :
-
Average film thickness for rough surfaces (mm) \(\left( {\bar{h}_{T} = h_{T} /h_{o} } \right)\)
- \(L_{t}\) :
-
Length of groove \(\left( {L_{t} = n_{d} *S_{p} } \right)\) (mm) \(\left( {\bar{L}_{t} = \frac{{L_{t} }}{{r_{o} }}} \right)\)
- \(N_{d}\) :
-
Number of micro-dimples \(\left( {N_{d} = 1{-}6} \right)\)
- \(n_{\theta } * n_{r}\) :
-
Number of nodes along circumferential and radial directions
- p :
-
Fluid film pressure (MPa) \(\left( {\bar{p} = \frac{{p - p_{c} }}{{p_{s} }}} \right)\)
- \(p_{oc}\) :
-
Pocket pressure \(\left( {\partial h/\partial t = 0} \right)\) (MPa) \(\left( {\bar{p}_{oc} = p_{oc} /p_{s} } \right)\)
- \(p_{c}\) :
-
Cavitation pressure (Pa)
- \(p_{f}\) :
-
Fluid film frictional power loss (Nm/s) \(\left( {\bar{p}_{fric} = \frac{{p_{f} }}{{p_{s} h_{o} \omega r_{o}^{2} }}} \right)\)
- \(p_{s}\) :
-
Supply pressure (MPa)
- Q :
-
Bearing flow (mm3/s)
- \(Q_{R}\) :
-
Restrictor flow (mm3/s) \(\left( {\bar{Q}_{R} = \frac{12\mu }{{p_{s} h_{o}^{3} }}Q_{R} } \right)\)
- \(r_{d}\) :
-
Dimple radius (µm) \(\left( {\bar{r}_{d} = \frac{{r_{d} }}{{r_{o} }}} \right)\)
- \(r_{i}\) :
-
Recess radius (mm)
- \(r_{o}\) :
-
Outer radius of thrust pad (mm)
- \(S_{p}\) :
-
Radial pitch between dimples \(\left\{ {\frac{{r_{o} - r_{i} }}{{\left( {N_{d} + 1} \right)}}} \right\}\) (mm) \(\left( {\bar{S}_{p} = \frac{{S_{p} }}{{r_{o} }}} \right)\)
- S :
-
Stiffness coefficient of fluid film (N/mm) \(\left( {\bar{S} = \frac{{h_{o} }}{{p_{s} r_{o}^{2} }}S} \right)\)
- u, w :
-
Fluid velocity along x and z direction (m/s)
- U, W :
-
Velocity component of runner pad along x and z direction (m/s)
- x, y, z:
-
Cartesian coordinates \(\left( {\bar{x} = \frac{x}{{r_{o} }};\bar{z} = \frac{z}{{r_{o} }};\bar{y} = \frac{y}{{h_{o} }}} \right)\)
- \(x_{l} , z_{l}\) :
-
Local co-ordinates of micro-dimples (mm) \(\left( {\bar{x}_{l} = \frac{{x_{l} }}{{r_{d} }};\bar{z}_{l} = \frac{{z_{l} }}{{r_{d} }}} \right)\)
- \(\rho_{c}\) :
-
Effective density of Lubricant in cavitation zone (kg/m3)
- \(\sigma\) :
-
Composite surface roughness (RMS) of thrust pad and runner surface (µm)
- \(\omega\) :
-
Angular velocity of runner (rad/s)
- \(\theta_{p}\) :
-
Angle of 1/32th model of thrust pad
- \(\phi_{x} , \phi_{z}\) :
-
Pressure flow factor along x and z direction
- \(\Lambda\) :
-
Film thickness parameter \(\left( {\Lambda = \frac{{h_{o} }}{\sigma }} \right)\)
- \(\upgamma\) :
-
Micro-roughness orientation parameter
References
Dowson D (1962) A generalized Reynolds equation for fluid-film lubrication. Int J Mech Sci 4(2):159–170
Rowe WB (1984) Hydrostatic and hybrid bearing design. Tribol Int 17(6):353
Sinhasan R, Jain SC (1984) Lubrication of orifice-compensated flexible thrust pad bearings. Tribol Int 17(4):215–221
Osman T, Dorid M, Safar Z, Mokhtar M (1996) Experimental assessment of hydrostatic thrust bearing performance. Tribol Int 29(3):233–239
Sharma SC, Jain SC, Bharuka DK (2002) Influence of recess shape on the performance of a capillary compensated circular thrust pad hydrostatic bearing. Tribol Int 35(6):347–356
Kumar V, Sharma SC (2017) Combined influence of couple stress lubricant, recess geometry and method of compensation on the performance of hydrostatic circular thrust pad bearing. Proc Inst Mech Eng Part J J Eng Tribol 231(6):716–733
Kumar V, Sharma SC (2018) Finite element method analysis of hydrostatic thrust pad bearings operating with electrically conducting lubricant. Proc Inst Mech Eng Part J J Eng Tribol 232(10):1318–1331
Charki A, Diop K, Champmartin S, Ambari A (2013) Numerical simulation and experimental study of thrust air bearings with multiple orifices. Int J Mech Sci 72:28–38
Kumar V, Sharma SC (2018) Dynamic characteristics of compensated hydrostatic thrust pad bearing subjected to external transverse magnetic field. Acta Mech 229(3):1251–1274
Coblas DG, Fatu A, Maoui A, Hajjam M (2015) Manufacturing textured surfaces: state of art and recent developments. Proc Inst Mech Eng Part J J Eng Tribol 229(1):3–29
Yang H, Ratchev S, Turitto M, Segal J (2009) Rapid manufacturing of non-assembly complex micro-devices by microstereolithography. Tsinghua Sci Technol 14:164–167
Etsion I (2005) State of the art in laser surface texturing. Trans ASME-F-J Tribol 127(1):248
Li J, Zhou F, Wang X (2011) Modify the friction between steel ball and PDMS disk under water lubrication by surface texturing. Meccanica 46(3):499–507
Etsion I, Halperin G, Greenberg Y (1997) Increasing mechanical seal life with laser-textured seal faces. In: 15th international conference on fluid sealing BHR group, Maastricht, The Netherlands, pp 3–11
Etsion I, Sher E (2009) Improving fuel efficiency with laser surface textured piston rings. Tribol Int 42(4):542–547
Ronen A, Etsion I, Kligerman Y (2001) Friction-reducing surface-texturing in reciprocating automotive components. Tribol Trans 44(3):359–366
Brizmer V, Kligerman Y, Etsion I (2003) A laser surface textured parallel thrust bearing. Tribol Trans 46(3):397–403
Rahmani R, Mirzaee I, Shirvani A, Shirvani H (2010) An analytical approach for analysis and optimisation of slider bearings with infinite width parallel textures. Tribol Int 43(8):1551–1565
Tauviqirrahman M, Ismail R, Jamari J, Schipper DJ (2013) A study of surface texturing and boundary slip on improving the load support of lubricated parallel sliding contacts. Acta Mech 224(2):365–381
Malik S, Kakoty SK (2014) Analysis of dimple textured parallel and inclined slider bearing. Proc Inst Mech Eng Part J J Eng Tribol 228(12):1343–1357
Cupillard S, Cervantes MJ, Glavatskih S (2008) Pressure build up mechanism in a textured inlet of a hydrodynamic contact. J Tribol 130(2):021701
Kango S, Singh D, Sharma RK (2012) Numerical investigation on the influence of surface texture on the performance of hydrodynamic journal bearing. Meccanica 47(2):469–482
Papadopoulos CI, Efstathiou EE, Nikolakopoulos PG, Kaiktsis L (2011) Geometry optimization of textured three-dimensional micro-thrust bearings. J Tribol 133(4):041702
Papadopoulos CI, Kaiktsis L, Fillon M (2014) Computational fluid dynamics thermohydrodynamic analysis of three-dimensional sector-pad thrust bearings with rectangular dimples. J Tribol 136(1):011702
Jakobsson B, Floberg L (1957) The finite journal bearing considering vaporization. Transactions of Chalmers University of Technology, Guthenburg, Sweden, Report No. 190
Olsson KO (1965) Cavitation in dynamically loaded bearing. Transactions of Chalmers University of Technology, Guthenburg, Sweden, Report No. 380
Elrod HG, Adams M (1974) A computer program for cavitation and starvation problems. In: Proceedings of the first LEEDS-LYON symposium on cavitation and related phenomena in lubrication, Leeds, UK, pp 37–41
Vijayaraghavan D, Keith T Jr (1989) Development and evaluation of a cavitation algorithm. Tribol Trans 32(2):225–233
Ausas R, Ragot P, Leiva J, Jai M, Bayada G, Buscaglia GC (2007) The impact of the cavitation model in the analysis of microtextured lubricated journal bearings. J Tribol 129(4):868–875
Ausas RF, Jai M, Buscaglia GC (2009) A mass-conserving algorithm for dynamical lubrication problems with cavitation. J Tribol 131(3):031702
Qiu Y, Khonsari M (2009) On the prediction of cavitation in dimples using a massconservative algorithm. J Tribol 131(4):041702
Yadav SK, Sharma SC (2016) Performance of hydrostatic textured thrust bearing with supply holes operating with non-Newtonian lubricant. Tribol Trans 59(3):408–420
Han Y, Fu Y (2017) Investigation of surface texture influence on hydrodynamic performance of parallel slider bearing under transient condition. Meccanica. https://doi.org/10.1007/s11012-017-0809-8
Tzeng ST, Saibel E (1967) Surface roughness effect on slider bearing lubrication. ASLE Trans 10(3):334–348
Christensen H (1969) Stochastic models for hydrodynamic lubrication of rough surfaces. Proc Inst Mech Eng 184(1):1013–1026
Patir N, Cheng HS (1978) An average flow model for determining effects of three-dimensional roughness on partial hydrodynamic lubrication. J Lubr Technol 100(1):12–17
Elsharkawy AA (2001) On the hydrodynamic liquid lubrication analysis of slider/disk interface. Int J Mech Sci 43(1):177–192
Qiu Y, Khonsari M (2011) Performance analysis of full-film textured surfaces with consideration of roughness effects. J Tribol 133(2):021704
Bujurke NM, Kudenatti RB (2007) MHD lubrication flow between rough rectangular plates. Fluid Dyn Res 39(4):334–345
Naduvinamani NB, Fathima ST, Jamal S (2010) Effect of roughness on hydromagnetic squeeze films between porous rectangular plates. Tribol Int 43(11):2145–2151
Author information
Authors and Affiliations
Corresponding author
Ethics declarations
Conflict of interest
The authors declare that they have no conflict of interest.
Appendix
Appendix
1.1 Appendix 1: Fluid film thickness expression for micro-dimples of different cross section shapes (Refer Fig. 1c)
Micro dimple shape | Expression for \(h_{tex}\) | Domain | Equations |
---|---|---|---|
Spherical: Sp | \(\sqrt {\left( {\frac{{h_{d}^{2} + r_{d}^{2} }}{{2h_{d} }}} \right)^{2} - \left( {x_{l}^{2} + z_{l}^{2} } \right)} - \frac{{r_{d}^{2} }}{{2h_{d} }} + \frac{{h_{d} }}{2}\) | \(\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d}\)—Sp | (14) |
Spherical half: Sp(h) | \(\left( {\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d} } \right)\) and \(z_{l} > 0\)—Sp(h) | ||
Conical: Con | \(\left[ {1 - \frac{{\sqrt {\left( {x_{l}^{2} + z_{l}^{2} } \right)} }}{{r_{d} }}} \right]h_{d}\) | \(\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d}\)— Con | (15) |
Conical half: Con(h) | \(\left( {\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d} } \right)\) and \(z_{l} > 0\)—Con(h) | ||
Conical frustum: Confr | \(\left[ {1 - \frac{{\sqrt {\left( {x_{l}^{2} + z_{l}^{2} } \right)} }}{{r_{d} }}} \right]h_{d}\) | \(\frac{{r_{d} }}{2} < \left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d}\)—Confr | |
\(h_{d}\) | \(\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} \le \frac{{r_{d} }}{2}\)—(confr) | (16) | |
Conical frustum half: Confr(h) | \(\left[ {1 - \frac{{\sqrt {\left( {x_{l}^{2} + z_{l}^{2} } \right)} }}{{r_{d} }}} \right]h_{d}\) | \(\left( {\frac{{r_{d} }}{2} < \left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d} } \right)\) and \(z_{l} > 0\)—Confr(h) | (17) |
\(h_{d}\) | \(\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} \le \frac{{r_{d} }}{2}\) and \(z_{l} > 0\)—Confr(h) | (18) | |
Cylindrical: Cyl | \(h_{d}\) | \(\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d}\)—Cyl | |
Cylindrical half: Cyl(h) | \(\left( {\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} < r_{d} } \right)\) & \(z_{l} > 0\)—Cyl(h) | ||
Untextured zone | \(0\) | \(\left( {\left( {x_{l}^{2} + z_{l}^{2} } \right)^{1/2} \geq r_{d} } \right)\) | (19) |
1.2 Appendix 2: Finite element formulation of modified Reynolds equation
The residue of Reynolds equation in FEM has been obtained as follows:
Weak formulation of modified Reynolds equation:
Elemental system of equation:
Matrix terms for eth element in the elemental system of equations can be expressed as:
Fluidity matrix:
Flow matrix:
Hydrodynamic term matrix:
Squeeze matrix:
Derivative of nodal pressure with respect to squeeze velocity and film thickness is expressed as:
Rights and permissions
About this article
Cite this article
Kumar, V., Sharma, S.C. Influence of dimple geometry and micro-roughness orientation on performance of textured hybrid thrust pad bearing. Meccanica 53, 3579–3606 (2018). https://doi.org/10.1007/s11012-018-0897-0
Received:
Accepted:
Published:
Issue Date:
DOI: https://doi.org/10.1007/s11012-018-0897-0