** Journal of Modern Physics** Vol.5 No.1(2014), Article ID:42261,7 pages DOI:10.4236/jmp.2014.51010

MHD Flow of a Non-Newtonian Power Law through a Conical Bearing in a Porous Medium

^{1}Department of Mathematics, Faculty of Science, Benha University, Benha, Egypt

^{2}Department of Mathematics, Faculty of Science, Princess Norah Bint Abdelrahman University, Riyadh, KSA

Email: gamalm60@yahoo.com

Received October 10, 2013; revised November 12, 2013; accepted December 11, 2013

ABSTRACT

The problem of analytical study of the MHD effect through a porous medium of the non-isothermal flow of a non-Newtonian power law lubricant through the gap of conical bearing through a porous medium when an external magnetic field is applied. At first, the more general basic equations of motion, continuity and energy in curvilinear form in the width direction are derived. Then, as a special case, a conical bearing gap is considered. By integrating a modified form of Reynolds equation, the bearing characteristics for a non-Newtonian power law lubricant when an external magnetic field is applied through a porous medium are obtained. Numerical results were presented in each of these forms: pressure, temperature and capacity of the conical bearing. The effects of the parameters of the non-Newtonian power law, magnetic field and porous medium are shown and discussed.

**Keywords:**MHD; Non-Newtonian Fluid; Conical Bearing; Porous Medium

1. Introduction

Firstly the study of an electrically conducting fluid through a porous medium under the influence of a magnetic field has many applications in engineering problems such as magnetohydrodynamics (MHD) generators, liquid metal, plasma studies, nuclear reactors, metal working process, geothermal energy extraction and in many other applications. MHD flow of non-Newtonian fluids also has application in different fields. An important field is the electromagnetic propulsion. And some fluids with thixotropic behavior help in the flow of blood, coating of paper, plastic extension and lubrication with heavy oils and greases.

Advance in modern technology and extremely severe requirements for rotating elements of machines imposes upon design engineers the necessity of continous development of improved lubricants in order to assure the stability, safe operation and reliability of various bearings. For operations under high molecular-weight polymer components are used in modern bearings. Such lubricants exhibit a non-Newtonian Rheological behavior [1].

The effect of the non-Newtonian behaviour of lubricants on the performance of hydrodynamic cylindrical journal bearing of infinite width has been investigated by I. Teipel et al. [2,3], and K. wierzcholski [4]. A somewhat similar problem but for cylindrical bearing of finite width had been considered. Swamy et al. [5].

This problem was studied in the magnetic case by Z. Nowak et al. [1], and also had been studied in magnetic field and a Newtonian lubricant by R. Janiszweski [6]. Very recently, Abdel-Rahman G. M. [7] studied the above mention flow of a non-Newtioan power law through a conical bearing in an applied magnetic field in the absence of the porous medium ().

In the present paper a magnetohydrodynamic flow for a non-Newtonian power law lubricant through the gap of a conical journal bearing in a porous medium is investigated. At first, the more general basic equations of motion, continuity and energy in curvilinear form in the width direction are derived. Then, as a special case, a conical bearing gap is considered. By integrating a modified form of Reynolds equation the bearing characteristics for a non-Newtonian power law lubricant when an external magnetic field is applied through a porous medium are obtained. It seems to the author that they succeeded in omitting the numerical procedures and obtained a relatively solution to the problem discussed.

2. Mathematical Analysis

The analytical study of the MHD effect through a porous medium of the non-isothermal flow of a non-Newtonian power law lubricant through the gap of conical bearing when an external magnetic field through the curvilinear bearing gap will be performed by using the following basic equations in orthogonal curvilinear coordinates.

Equation of motion:

(1)

Equation of continuity:

(2)

Equation of energy:

(3)

where -is the stress tensor in the lubricant, is the local lubricant velocity vector, is the dynamic viscosity, is the lubricant mass density, is the permeability of the porous medium, is the specific heat of the lubricant, is the temperature in the lubricant, is its coefficient of thermal conductivity, is the electric conductivity in the lubricant and is the applied magnetic field.

The movable local coordinate system—connected with the rotating journal surface—is assumed to be curvilinear and orthogonal. The components of the stress tensor S are expressed as where is the hydrodynamic pressure and is the Kronecker symbol.

From the Reiner-Rivlin equations follows immediately that for a power law lubricant, as considered is this paper, the stress-strain relations are of the form:

(4)

where k is the fluid of consistency and n is the flow behaviour index of the lubricant.

The components of the strain tensor are:

(5)

where denote the components of velocity vector in -direction respectively.

In the first approximation, both the fluid of consistency, and the flow behaviour index, are assumed to be independent of temperature. The viscous dissipation (dissipation function) for the lubricant, however, taken into account. Since the journal of the bearing always is a rotating body, the lame’s coefficients become respectively. Assuming the ratio of the radial component of 1ubricant velocity to the peripheral velocity of the journal bearing to be of order of the relative radial clearance and hence, neglecting the terms having the order of the latter, than equations of: motion, continuity and energy, become

(6)

(7)

(8)

(9)

For Equations (6)-(9) describe the magneto-hydrodynamic flow of a non-Newtonian power law lubricant in a porous medium through the curvilinear (in width direction) gap of a slide bearing.

For n = 1, the equations listed above hold for a Newtonian gap flow [6], the unknown functions, p and T may be found by solving the Equations (6)-(9).

In the special case of a conical bearing gap , the curvilinear coordinates become, respectively, see Figure 1.

Thus, the Lame’s coefficients are where denotes the slope of the generating line of conical surface. The components of the local lubricant velocity, the hydrodynamic pressure and temperature are now assumed to be of the following forms:

Figure 1. Conical bearing gap.

(10)

where and are the dimensionless components of the local lubricant velocity in the and directions, respectively, is the dimensionless hydrodynamic pressure is the temperature, is the length of the cone generating line, e denotes the height of the gap, is the dimensional characteristic value of lubricant density, denotes the ambient temperature, w is the angular velocity of the journal, E_{c} and P_{r} are the Eckert and Prandtl numbers, respectively. Moreover

(11)

where is the modified Kinematic viscoity, is a dimensionless number that characterizes the magnetic field,

is a dimensionless porous medium and

is the relative redial clearance of the bearing.

Let be the dimensionless vertical coordinate, and be the dimensionless coordinate in the direction of cone generating line.

After substituting Equations (10) and (11) into Equations (6)-(9), provided that the axisymmetrical flow is considered, with simultaneous neglecting the terms of the -order, one obtains finally:

(12)

(13)

(14)

(15)

(16)

for, where and are the dimensionless thermal conductivity and density of the lubricant, respectively, is the dimensionless distance between the sleeve surface and the axis of the journal. Moreover, signifies the modified Reyolds number, defined by

(17)

The term appearing Equation (12) describes the centrifugal forces generated in the lubricant by the rotation of the journal. The expression occurring in Equations (12), (13) and (16) determines the dimensionless apparent viscosity of the lubricant. The remaining “viscous” terms in (12), (13) and (16) have been neglected since their values are of the -order. Equation (13) does not appear the term, , because of the

per-assumed axisymmetry of the lubricant flow.

Form the simplified form of Equation (14) follows immediately that the pressure has been assumed to be uniform along the film thickness.

In the equation of energy (16) the terms due to the forced heat convection in the lubricant have been disregarded, since their values are of the -order. However, it should be noted here that the terms due both to the viscous dissipation and heat conduction in the radial direction have been taken onto account.

3. Solution of Equations

Assuming the lubricant to be an incompressible flow, we have since the difference between the ambient temperature and the temperature both in the gap and in the bearing sleeve, is generally small, the coefficient of thermal conductivity is assumed to be independent of temperature i.e.

The boundary conditions to this system are

(18)

where is the dimensionless pressure, is the ambient pressure f_{c1} is the dimensionless temperature on the journal surface and _{ } is the dimensionless temperature of the bearing sleeve.

For Equation (13) solution for which satisfy the boundary condition (18) is

(19)

After substituting the function into Equation (12) and taking into account the boundary condition (18), we find as a function of the parameter, we get

(20)

substituting the function into Equation (15), hence, we get

(21)

The boundary condition at imposed upon the velocity component leads to an equation from which the pressure function may be determined. After solving this equation with the boundary condition (18), we obtain the sought-for function as

(22)

By inserting the function into Equation (16) and integrating it with boundary condition (18), we calculate the temperature function as

(23)

For the above relations hold for a nonNewtonian power law lubricant with time independent rheological properties, the apparent viscosity of which decrease with increasing shear rate for constant magnetic field.

4. Numerical Discussion and Conclusions

Numerical values for the pressure and temperature distributions from Equations (22) and (23) for, and in Figures 2-4 for

(a)(b)

Figure 2. Effect of magnetic parameter on (a) the dimensionless pressure profile and (b) the dimensionless temperature profile.

(a)(b)

Figure 3. Effect of a non-Newtonian power law lubricant parameter on (a) the dimensionless pressure profile and (b) the dimensionless temperature profile.

some values of the magnetic parameter the parameter of the non-Newtonian power law lubricant and the parameter of the porous medium from these results we can state the following:

Figures 2(a) and (b) display the dimensionless pressure and the dimensionless temperature profiles under the different the magnetic parameter. The pressure and the temperature profiles decrease with increasing the magnetic parameter.

Figures 3(a) and (b), it is clear that the pressure increases with the increase of the non-Newtonian power law lubricant parameter in comparison to the respective pressure values due to a Newtonian flow. These decreases are caused by a decreasing apparent viscosity of the non-Newtonian lubricant as compared to the dynamic viscosity of a Newtonian flow,

Figure 4. Effect of a porous medium parameter on the dimensionless pressure profile.

and the decreases of the temperature for a non-Newtonian lubricant are distinctly greater than those corresponding to the Newtonian flow. These decreases are due to viscous dissipation arising in the lubricant. The phenomenen discussed may be explained by the fact that for the non-Newtonian lubricant greater values of internal friction forces are generated than for a Newtonian flow. The latter produce, in turn, greater heat quantities during the motion of particles.

Figure 4 displays the dimensionless pressure profile under the different the porous medium parameter. The pressure profile decreases with increasing the porous medium parameter.

The capacity of the conical bearing can be expressed in the following dimensionless from:

(24)

substituting the function into Equation (22), hence, we get

(25)

where

where is the characteristic pressure value. Provided that.

In Figures 5(a) and (b), it is clear that the capacity increases with the increase of the nonNewtonian power law lubricant parameter, while the increases of the capacity for the porous medium parameter decreasing.

Figures 6(a) and (b), the capacity increases with the increase of each of the magnetic parameter and the porous medium parameter.

And in Figures 7(a) and (b), it is clear that the capacity increases with the decrease of the the magnetic parameter, while the increases of the capacity for the non-Newtonian power law lubricant parameter increasing.

(a)(b)

Figure 5. (a) The capacity for various and (b) The capacity for various.

(a)(b)

Figure 6. (a) The capacity for various and (b) The capacity for various.

(a)(b)

Figure 7. (a) The capacity for various and (b) The capacity for various.

REFERENCES

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