Abstract
Proper tribological practices are extremely important from the view point of reliable and maintenance free operation of machine components. Friction, wear, and lubrication are three main domains of tribology. Proper interfacing among these domains is essential to have a better performance of machine components. Bearings are most critical machine elements which imparts constrained relative motion between two machine components. Bearings either have sliding contact or rolling contact. In the present chapter different types of bearings have been discussed. The main focus of this chapter is on hydrostatic/hybrid fluid-film journal bearings. The components of the hydrostatic/hybrid bearing system that have significant impact on bearing performance have been described. The analysis of fluid-film journal bearings and their performance characteristics parameters have been discussed. The chapter also discusses some current research trends in the design of hydrostatic/hybrid journal bearings. In concluding section the chapter discusses some of the results pertaining to the current issues of research, which needs to be considered for an accurate and realistic design of hydrostatic/hybrid journal bearing system, such as the number of recesses, type of restrictor, shape of recess, influence of turbulence and flexibility, etc.
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Abbreviations
- a b :
-
Axial land width, mm
- as :
-
Extent of slot width, mm
- d o :
-
Orifice diameter, mm
- c :
-
Radial clearance, mm
- A m :
-
Effective area of membrane, mm2
- A p :
-
Area of the pocket, mm2
- Ae :
-
Area of each element (mm2)
- C ij :
-
Fluid-film damping coefficients (i, j = x, z), N.s/m
- C1 :
-
Clearance due to circumscribed circle on the bearing (mm)
- C2 :
-
Clearance due to inscribed circle on the bearing (mm)
- D :
-
Journal diameter, mm
- d c :
-
Diameter of capillary, mm
- E :
-
Modulus of elasticity of bearing material, MPa
- e :
-
Journal eccentricity, mm
- F :
-
Fluid-film reaction (∂h/∂t ≠ 0), N
- F x , F z :
-
Fluid-film reaction components in X and Y direction (∂h/∂t ≠ 0), N
- F o :
-
Fluid-film reaction (∂h/∂t = 0), N
- K m :
-
Membrane stiffness, N mm−1
- g :
-
Acceleration due to gravity, m.s−2
- h :
-
Nominal fluid-film thickness, mm
- h T :
-
Average fluid-film thickness, mm
- h m :
-
Gap height for membrane restrictor, mm
- h min :
-
Minimum fluid-film thickness, mm
- Δh m :
-
Membrane deflection, mm
- h mo :
-
Gap height for zero external load in case of membrane restrictor, mm
- h 0 :
-
Fluid-film thickness in rigid bearing, mm
- l c :
-
Length of capillary, mm
- L :
-
Bearing length, mm
- m :
-
Consistency index, N.m2.s−n
- M c , M j :
-
Critical mass and Mass of journal, kg
- n :
-
Power law index
- n x n y :
-
Direction cosines in α and β directions respectively
- OL :
-
Lobe center
- p :
-
Pressure, N.mm−2
- p c :
-
Pressure at recess/pocket/hole, N.mm−2
- p s :
-
Supply pressure, N.mm−2
- Q :
-
Lubricant flow, mm3.s−1
- Q R :
-
Flow through restrictor, mm3 s−1
- r c :
-
Radius of capillary, mm
- r 1, r 2 :
-
Membrane radii, mm
- r m :
-
Mean radius of cone from apex, mm
- R j , R b :
-
Radius of journal and bearing, mm
- S ij :
-
Fluid-film stiffness coefficients (i, j = x, z), N.mm−1
- t :
-
Time, sec
- t h :
-
Thickness of bearing shell, mm
- t m :
-
Thickness of membrane, mm
- V rj , V rb :
-
Variance ratio of journal and bearing respectively
- W o :
-
External load, N
- x :
-
Circumferential coordinate
- y :
-
Axial coordinate
- X j , Z j :
-
Journal center coordinate
- X, Y, Z :
-
Cartesian coordinate system
- z :
-
Coordinate along film thickness
- γ, κ :
-
Material coefficient, N s; spin viscosity, N s m−2
- μ :
-
Lubricant Dynamic viscosity, N s m−2
- μ r :
-
Reference viscosity of lubricant, N s m−2
- σ :
-
RMS value of combined roughness, \( \sigma =\sqrt{\sigma_j^2+{\sigma}_b^2} \), μm
- σ j :
-
RMS value of journal surface roughness, μm
- σ b :
-
RMS value of bearing surface roughness, μm
- ω I :
-
(g/c)1/2, rad.sec−1
- ω j :
-
Journal rotational speed, rad.s−1
- ω th :
-
Threshold speed, rad.s−1
- ρ :
-
Density, kg.m−3
- ψ d :
-
Coefficient of discharge for orifice
- τ :
-
Shear stress, N. m−2
- \( \dot{\gamma} \) :
-
Shear strain rate, s−1
- \( {\overline{a}}_b \) :
-
a b /L
- \( {\overline{C}}_d \) :
-
Deformation coefficient
- \( {\overline{C}}_{ij} \) :
-
\( {C}_{ij}\left(\frac{c^3}{\mu_r{R}_j^4}\right) \)
- \( {\overline{C}}_{S2} \) :
-
Restrictor design parameter
- \( \overline{F},{\overline{F}}_o \) :
-
(F, F o /p s R 2 j )
- \( {\overline{F}}_x,{\overline{F}}_z \) :
-
(F x , F z /p s R 2 j )
- \( {\overline{F^{\hbox{'}}}}_o \) :
-
Cross film viscosity integrals, F′0(μ r /h L )
- \( {\overline{F}}_1 \) :
-
Cross film viscosity integrals, F 1(μ r /h 2 L )
- \( \overline{h} \) :
-
h/c
- \( {\overline{h}}_{\min },{\overline{h}}_T \) :
-
(h min,h T )/c
- \( \overline{K} \) :
-
Nonlinearity factor
- l m :
-
Nondimensional characteristic length, c/l
- \( \overline{m} \) :
-
\( m{\left(\frac{c{p}_s}{\mu_r{R}_j}\right)}^n\left(\frac{R_j}{c{p}_s}\right) \)
- \( {\overline{M}}_j \) :
-
\( {M}_j\ \left(\frac{c^5\ {p}_{{}_s}}{\mu_{\mathrm{r}}^2{R}_j^6}\right) \)
- N :
-
Coupling number, \( {\left(\frac{\kappa }{2\mu +\kappa}\right)}^{1/2} \)
- N i , N j :
-
Shape functions
- \( \overline{p},{\overline{p}}_c \) :
-
(p,p c )/p s
- \( {\overline{p}}_{\max } \) :
-
p max/p s
- \( \overline{Q} \) :
-
Q (μ r /c 3 p s )
- SWR :
-
Slot width ratio, a s /(a s )max
- \( {\overline{S}}_{ij} \) :
-
\( {S}_{ij}\ \left(\frac{c}{p_s{R}_j^2}\right) \)
- \( \overline{t} \) :
-
t (c 2 p s /μ r R j 2)
- \( {\overline{W}}_o \) :
-
\( \frac{W_o}{p_s{R}_j^2} \)
- \( \left({\overline{V}}_{rj},{\overline{V}}_{rb}\right) \) :
-
((σ j ,σ b )/σ)2
- \( \left({\overline{X}}_j,{\overline{Z}}_j\right) \) :
-
(X j ,Z j )/c
- α, β :
-
(x,y)/R j
- β*:
-
Concentric design pressure ratio, (p*/p s )
- ε :
-
e/c
- γ :
-
\( \frac{\lambda_{0.5x}}{\lambda_{0.5y}} \), Surface pattern parameter
- Λ :
-
\( 1/\overline{\sigma} \), Surface roughness parameter
- \( \overline{\sigma} \) :
-
σ/c
- φ x , φ y :
-
Pressure flow factors
- φ s :
-
Shear flow factor
- λ :
-
L/D, Aspect ratio
- \( \overline{\mu} \) :
-
μ/μ r
- υ :
-
Poisson’s ratio of bearing material
- Ω :
-
ω J (μ r R 2 j /c 2 p s ), Speed parameter
- \( {\overline{\omega}}_{th} \) :
-
ω th /ω I , Speed parameter
- \( \overline{\tau} \) :
-
τ(R j /c p s ), shear stress parameter
- \( \overline{\dot{\gamma}} \) :
-
\( \dot{\gamma}\left({\mu}_r{R}_j/c\ {p}_s\right) \), shear strain parameter
- \( \left[\overline{F}\right] \) :
-
Fluidity matrix
- \( \left\{\overline{p}\right\} \) :
-
Nodal pressure vector
- \( \left\{\overline{Q}\right\} \) :
-
Nodal flow vector
- \( \left\{{\overline{R}}_{X_J},{\overline{R}}_{Z_J}\right\} \) :
-
Nodal RHS vectors due to journal center velocities
- \( \left\{{\overline{R}}_H\right\} \) :
-
Column vector due to hydrodynamic terms
- –:
-
Nondimensional parameter
- e :
-
e th element
- j :
-
Journal
- max:
-
Maximum value
- min:
-
Minimum value
- o :
-
Steady State Condition
- R :
-
Restrictor
- r :
-
Reference value
- s :
-
Supply Pressure
- ∗:
-
Concentric operation
- .:
-
First derivative w.r.t. time
- ..:
-
Second derivative w.r.t. time
References
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Acknowledgement
The author is extremely grateful to Elsevier Publication, Taylor and Francis Publication, Emerald Group Publication, Sage Publication, and ASME publications for granting permission to use their copyright material in the present chapter. The used materials have been cited in the references. Further, I would like to acknowledge and thank my PhD scholars Mr. Arvind Kumar Rajput, Mr. G.D. Thakre, Mr. Nathi Ram, and Mr. P.B. Kushare, who provided their valuable assistance during the course of writing of this chapter.
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Exercise
Exercise
-
1.
Write a brief engineering note on the purpose of lubrication in machine component? How a liquid lubricant is better than a solid lubricant?
-
2.
Classify different bearing configurations? List the application of rolling contact Bearing?
-
3.
Enumerate the advantages of hydrostatic journal bearing over a hydrodynamic journal bearing?
-
4.
Describe in brief need of a restrictor in a hydrostatic journal bearing system? Which type of restrictor will you prefer in high variable load?
-
5.
Describe the phenomena of whirl and whip in journal bearing system? How these problems could be overcome?
-
6.
What are the advantages of recessed journal bearing over non-recessed journal bearing?
-
7.
Derive the generalized form of Reynolds equation in nondimensional form by using suitable nondimensional parameter.
-
8.
Write a brief engineering note on bearing performance characteristics parameters.
-
9.
Explain Elastohydrostatic/Elastohydrodynamic Lubrication phenomenon. How do these affects the performance of a journal bearing?
-
10.
What do you mean by the term Nonlinearity of lubricant? How does the nonlinearity of lubricant affect the performance of a journal bearing?
-
11.
Explain the phenomenon of turbulence in the fluid-film journal bearing system. Describe different theories for turbulence applicable to journal bearing.
-
12.
A capillary compensated hydrostatic journal bearing system has the following parameters-
Discharge through capillary
4 × 10−5 m3/s
Length of capillary
10 cm
viscosity of lubricant
2.18 × 10−3 N-s/m2
Supply pressure
1.4 MPa
Recess pressure
0.5 MPa
Determine the radius of the capillary.
-
13.
Determine the value of discharge of the lubricant through an orifice restrictor for an orifice restricted recessed hybrid journal bearing system with the following data.
Orifice diameter
10 mm
Coefficient of discharge
0.55
Density of lubricant
800 Kg/m3
Supply pressure
0.15 MPa
Recess pressure
0.06 MPa
-
14.
Determine the load carrying capacity and shear stress for a hydrodynamic journal bearing system for the following data.
Pressure
1 MPa
Aspect ratio
0.8
Length of the bearing
1 m
Clearance
10−3 m
Viscosity
2.08 × 10−5 N-s/m2
Speed of journal
1,000 rpm
-
15.
Determine the value of the coupling number and characteristics length for the lubricant with the following characteristics.
Linear viscosity
2.5 × 10−3 N-s/m2
Spin viscosity
1.2 × 10−3 N-s/m2
Characteristics coefficients
0.8 × 10−9 N-s
-
16.
Compare the value of the turbulent coefficients for the value of Reynolds number Re = 10,000 using Constantinescu theory.
-
17.
Derive the expression of critical mass of journal using the Routh’s criterion of Stability.
-
18.
Determine the wear zone for a hydrostatic journal bearing system for the values of nondimensional wear depth parameter of 0.25 and 0.5.
Solutions
-
12.
Given that
Q R = 4 × 10− 5 m 3/s; l c = 0.1 m; μ = 2.18 × 10− 3 Ns/m 2; p s = 1.4 MPa; p c = 0.5 MPa
$$ {Q}_R={K}_c\frac{\left({p}_s-{p}_c\right)}{\mu }=\frac{\pi {d_c}^4}{128{l}_c}\frac{\left({p}_s-{p}_c\right)}{\mu } $$$$ 4\times {10}^{-5}=\frac{\pi {d_c}^4}{128\times 0.10}\frac{\left(1.4-0.5\right)\times {10}^6}{2.18\times {10}^{-3}} $$$$ {d}_c=7.926\times {10}^{-4}m $$ -
13.
Given that
d0 = 10 mm; ρ = 800 kg/m3; p s = 0.15 MPa; p c = 0.06 MPa
$$ {Q}_R=\frac{\pi {\psi}_d{d}_0^2}{\sqrt{8\rho }}{\left({p}_s-{p}_c\right)}^{\frac{1}{2}} $$$$ {Q}_R=\frac{\pi \times 0.55\times {\left(10\times {10}^{-3}\right)}^2}{\sqrt{8\times 800}}{\left(\left(0.15-0.06\right)\times {10}^6\right)}^{\frac{1}{2}} $$$$ \begin{array}{l}=6.4795\times {10}^{-4}{m}^3/ \sec \\ {}\end{array} $$ -
14.
Given that
p = 1 MPa; L/D = 0.8; L = 1 m; C = 10−3 m; N = 1,000 rpm;
\( \mu =2.08\times {10}^{-5} Ns/{m}^2 \)
Load carrying capacity
Fo = p. A = p. π L.D= 1 × 106 × π × 1.25 = 3.92699 × 106 N
Shear stress
\( \begin{array}{l}\tau =\mu \frac{ du}{ dy}=2.08\times {10}^{-5}\times \frac{\pi \times 10000\times 1.25}{60\times {10}^{-3}}\\ {}=13.6135N/{m}^2\end{array} \)
-
15.
Given that,
\( \mu =2.5\times {10}^{-3}N-s/{m}^2 \)
Spin velocity, κ = 1.2 × 10− 3 N − s/m 2
\( {\gamma}_1=0.8\times {10}^{-9}N-s \)
\( N={\left(\frac{\kappa }{2\mu +\kappa}\right)}^{\frac{1}{2}}=0.4399 \)
\( \overset{.}{l}={\left(\frac{\gamma_1}{4\mu}\right)}^{\frac{1}{2}}=2.828\times {10}^{-4}m=0.2828\kern0.5em mm. \)
-
16.
Given that,
\( \begin{array}{l}{R}_e=10000\\ {}{G}_{\alpha }=12+0.026{\left({R}_e\right)}^{0.8265}=64.5985\\ {}{G}_{\beta }=12+0.0198{\left({R}_e\right)}^{0.741}=30.2249.\end{array} \)
-
18.
Given that,
Sinα = δ w − 1 by Dufrane’s abrasive wear model
\( \begin{array}{l} for,{\delta}_w=0.25\\ {} Sin\alpha =0.25-1\\ {}\alpha ={228.59}^0,{311.40}^0\end{array} \)
\( \begin{array}{l} for,{\delta}_w=0.50\\ {} Sin\alpha =0.50-1\\ {}\alpha ={210}^0,{330}^0\end{array} \)
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Sharma, S.C. (2013). Tribology in Machine Components. In: Menezes, P., Nosonovsky, M., Ingole, S., Kailas, S., Lovell, M. (eds) Tribology for Scientists and Engineers. Springer, New York, NY. https://doi.org/10.1007/978-1-4614-1945-7_25
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