# Performance of Magnetic-Fluid-Based Squeeze Film between Longitudinally Rough Elliptical Plates

Authors: P. I. Andharia; G. M. Deheri
Journal: ISRN Tribology
 (2013)

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## Abstract

An attempt has been made to analyze the performance of a magnetic fluid-based-squeeze film between longitudinally rough elliptical plates. A magnetic fluid is used as a lubricant while axially symmetric flow of the magnetic fluid between the elliptical plates is taken into consideration under an oblique magnetic field. Bearing surfaces are assumed to be longitudinally rough. The roughness of the bearing surface is characterized by stochastic random variable with nonzero mean, variance, and skewness. The associated averaged Reynolds’ equation is solved with appropriate boundary conditions in dimensionless form to obtain the pressure distribution leading to the calculation of the load-carrying capacity. The results are presented graphically. It is clearly seen that the magnetic fluid lubricant improves the performance of the bearing system. It is interesting to note that the increased load carrying capacity due to magnetic fluid lubricant gets considerably increased due to the combined effect of standard deviation and negatively skewed roughness. This performance is further enhanced especially when negative variance is involved. This paper makes it clear that the aspect ratio plays a prominent role in improving the performance of the bearing system. Besides, the bearing can support a load even when there is no flow.


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## Body

## 1. Introduction

The transient load carrying capacity of a fluid film between two surfaces having a relative normal velocity plays a crucial role in frictional devices such as clutch plates in automatic transmissions. Archibald [1] studied the behaviour of squeeze film between various geometrical configurations. Subsequently, Wu [2, 3] investigated the squeeze film performance mainly for two types of geometries, namely, annular and rectangular when one of the surfaces was porous faced. Prakash and Vij [4] discussed the load carrying capacity and time height relations for squeeze film performance between porous plates. In that study various geometries such as circular, annular, elliptical, rectangular, conical, and truncated conical were considered. Besides, a comparison was made between the squeeze film performance of various geometries of equivalent surface area and it was established that the circular geometry registered the highest transient load carrying capacity, other parameters remaining same.The above studies dealt with conventional lubricant. Verma [5] considered the application of magnetic fluid as a lubricant. The magnetic fluid consisted of fine magnetic grains coated with a surfactant and dispersed in a non-conducting magnetically passive solvent. Later on, Bhat and Deheri [6] discussed the squeeze film behaviour between porous annular disks using a magnetic fluid lubricant with the external magnetic field, oblique to the lower disk. This analysis was improved further by Bhat and Deheri [7] to deal with the performance of a magnetic fluid based squeeze film in curved circular plates. Furthermore, Patel and Deheri [8] studied the behaviour of a magnetic fluid based squeeze film between porous conical plates. All these above studies established that the performance of the bearing system was modified and enhanced owing to the magnetic fluid lubricant.In all the above analyses bearing surfaces were assumed to be smooth. However, the bearing surfaces after having some run-in and wear develop roughness. In fact, due to elastic, thermal, and uneven wear effects, the configurations encountered in practice are usually far from smooth. Sometimes the contamination of the lubricant and chemical degradation of the surfaces result in roughness. The roughness appears to be random in character, which was recognized by many investigators who analyzed the effect of surface roughness resorting to a stochastic method [9–13]. Christensen and Tonder [14–16] mathematically modelled the random roughness and suggested a comprehensive general analysis for investigating the effect of transverse as well as longitudinal surface roughness. This approach of Christensen and Tonder was the basis for investigating the effect of surface roughness in a number of investigations [17–24].Recently, Andharia and Deheri [25] discussed the performance of a magnetic fluid based squeeze film in longitudinally rough conical plates. Here it has been proposed to study and analyze the performance of a squeeze film between longitudinally rough elliptical plates under the presence of a magnetic fluid lubricant.


## 2. Analysis

The configuration of the bearing system shown in Figure1 consists of two elliptical plates. The upper plate moves normally towards the lower plate with uniform velocity h˙0(=dh0/dt) where h0 is the central film thickness. The assumptions of usual hydrodynamic lubrication theory are taken into consideration in the analysis. The lubricant film is considered to be isoviscous and incompressible and the flow is laminar.Figure 1
Bearing configuration.The bearing surfaces are assumed to be longitudinally rough. The thicknessh of the lubricant film is
(1)h=h-+hs,
where h- is the mean film thickness and hs is the deviation from the mean film thickness characterizing the random roughness of the bearing surfaces. hs is considered to be stochastic in nature and governed by the probability density function f(hs), -c≤hs≤c, where c is the maximum deviation from the mean film thickness. The mean α, the standard deviation σ and the parameter ε which is the measure of symmetry, of the random variable hs, are defined by the relationships:
(2)α=E(hs),σ2=E[(hs-α)2],(3)ε=E[(hs-α)3],
where E denotes the expected value defined by
(4)E(R)=∫-ccRf(hs)dhs,
wherein
(5)f(hs)={3532(1-hs2c2)3,-c≤hs≤c0,otherwise.Axially symmetric flow of magnetic fluid between the elliptical plates is taken into consideration under an oblique magnetic fieldM¯ whose magnitude M is expressed as
(6)M2=ab(1-x2a2-z2b2),
where a is semimajor axis and b is semiminor axis. The direction of the magnetic field is significant since M¯ needs to satisfy the equations
(7)∇·M¯=0,∇×M¯=0.
Therefore, M¯ arises out of a potential function and the inclination θ of the magnetic field M¯ with the lower plate is determined from
(8)cotθ∂θ∂x+∂θ∂z=bx+az-xz+1(ab-ax+bz)xz+abx2z2.Following Prakash and Vij [4], Bhat and Deheri [6], and Andharia and Deheri [25], the Reynolds’ equation governing the film pressure p in the present case is obtained as
(9)(∂2∂x2+∂2∂z2)(p-0.5μ0μ-M2)=12μh˙0h3,
where μ is fluid viscosity, μ- is the magnetic susceptibility, and μ0 stands for permeability of the free space.It is easily observed thatα, σ, and ε are all independent of x and while α and ε can assume both positive and negative values, σ is always positive. Following the averaging process discussed by Andharia et al. [24] and using (6), (9) takes the form
(10)(∂2∂x2+∂2∂z2)(p¯-0.5μ0μ-M2)=12μh˙0m(h-)-1,
where p- is the expected value of the lubricant pressure p while
(11)m(h-)=h--3⌊1-3αh--1+6h--2(σ2+α2)-20h--3(ε+3σ2α+α3)⌋.Introduction of dimensionless quantities:(12)H=h-h0,X=xa,Z=zb,M(H)=h03m(h-),α-=αh0,σ-=σh0,ε-=εh0,k=ba,μ*=-μ0μ-h03μh˙0,P=-p-h03μh˙0πab,
presents (10) in the form
(13)(∂2∂X2+∂2k2∂Z2)(P-0.5μ*M2πab)=12M(H)kπ.The associated boundary conditions are(14)P(X1,Z1)=0;X12+Z12=1.
Solving (13) using boundary condition given in (14), one obtains the dimensionless pressure distribution:
(15)P=[μ*2π(1+1k2)+6M(H)kπ(1+1/k2)](1-X2-Z2),
where
(16)M(H)=H-3⌊1-3α¯H-1+6H-2(σ¯2+α¯2)-20H-3(ε¯+3σ¯2α¯+α¯3)⌋.The load carrying capacity of the bearing in non-dimensional form can be expressed as(17)W=1π∫X=-1X=1∫Z=-1-X2Z=1-X2PdXdZ=μ*4π(1+1k2)+3M(H)kπ(1+1/k2).


## 3. Results and Discussion

It is easily observed that the non-dimensional pressure is determined from (15) while (17) presents the distribution of load carrying capacity in dimensionless form. It is clearly seen from these two equations that the dimensionless pressure increased by (μ*/2π)(1+1/k2) while load carrying capacity is increased by (μ*/4π)(1+1/k2) due to magnetic fluid lubricant. In the absence of roughness this study reduces to the performance of a magnetic fluid based squeeze film in elliptical plates.To analyze the quantitative effect of various parameters such as the magnetization parameterμ*, the aspect ratio k(=b/a) and roughness parameters α, σ, and ε on the performance of the bearing, dimensionless load carrying capacity is computed numerically for different values of these parameters. Results are presented graphically in Figures 2, 3, 4, 5, 6, 7, 8, 9, 10, 11, 12, 13, 14, and 15.Figure 2
Variation of load carrying capacity with respect toμ* for different α.Figure 3
Variation of load carrying capacity with respect toμ* for different σ.Figure 4
Variation of load carrying capacity with respect toμ* for different ε.Figure 5
Variation of load carrying capacity with respect toμ* for different k.Figure 6
Variation of load carrying capacity with respect tok for different α.Figure 7
Variation of load carrying capacity with respect tok for different σ.Figure 8
Variation of load carrying capacity with respect tok for different ε.Figure 9
Variation of load carrying capacity with respect toε for different α.Figure 10
Variation of load carrying capacity with respect toε for different σ.Figure 11
Variation of load carrying capacity with respect toα for different σ.Figure 12
Variation of load carrying capacity with respect toσ for different μ*.Figure 13
Variation of load carrying capacity with respect toσ for different k.Figure 14
Variation of load carrying capacity with respect toσ for different α.Figure 15
Variation of load carrying capacity with respect toσ for different ε.In Figures2, 3, 4, and 5 one can have the variation of load carrying capacity with respect to magnetization parameter for different values of α, σ, ε, and k, respectively. All these figures suggest that the load carrying capacity increases sharply with respect to the magnetization parameter. Figures 6, 7 and 8 depict the variation of load carrying capacity with respect to the aspect ratio k for different values of α, σ, and ε, respectively. From these figures one can easily observe that the increasing values of the aspect ratio cause increased load carrying capacity. Figures 9 and 10 give the profile for load carrying capacity with respect to the skewness for different values of  α and σ respectively. It is clearly seen from these graphs that the positively skewed roughness decreases the load carrying capacity while the negatively skewed roughness increases the load carrying capacity. From Figure 11 it is observed that the trend of variance is quite similar to that of skewness so far as the distribution of load carrying capacity is concerned. It is also interesting to note that the effect of standard deviation is negligible beyond the variance’s value 0.1 with regards to the distribution of load carrying capacity. Lastly, Figures 12, 13, 14, and 15 describe the variation of the load carrying capacity with respect to the standard deviation for various values of μ*, k, α, and ε, respectively. Unlike the case of transverse roughness, here it is established that the standard deviation tends to increase the load carrying capacity. However, the increase at the initial stage is relatively less.


## 4. Conclusion

A close look at the figures reveals that the negative effect of positiveα can be compensated to a considerable extent by the positive effect of the magnetization parameter by choosing a suitable aspect ratio in the case of negatively skewed roughness. In the similar way the negative effect of positive ε can be compensated by choosing suitable combination of magnetization parameter and aspect ratio especially when negative variance occurs.Hence, this study makes it mandatory that the roughness must be given due consideration while designing the bearing system from bearing’s life period point of view.



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*Source: 482604-2013-02-06.xml*