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Fluid mechanics is the study of fluids including liquids, gases and plasmas and the forces acting on them. Its study is critical in predicting rainfall, ocean currents, reducing drag on cars and aeroplanes, and design of engines. The subject is also interesting from a mathematical perspective due to the nonlinear nature of its equations. For example, the topic of turbulence has been a subject of interest to both mathematicians and engineers: to the former because of its mathematically complex nature and to the latter group because of its ubiquitous presence in real-life applications. This book is a follow-up to the first volume and discusses the concepts of fluid mechanics in detail. The book gives an in-depth summary of the governing equations and their engineering related applications. It also comprehensively discusses the fundamental theories related to kinematics and governing equations, hydrostatics, surface waves and ideal fluid flow, followed by their applications.
This paper analyses the steady-state operation of a generalized bioreactor model that encompasses a continuous-flow bioreactor and an idealized continuous-flow membrane bioreactor as limiting cases. A biodegradation of organic materials is modelled using Contois growth kinetics. The bioreactor performance is analysed by finding the steady-state solutions of the model and determining their stability as a function of the dimensionless residence time. We show that an effective recycle parameter improves the performance of the bioreactor at moderate values of the dimensionless residence time. However, at sufficiently large values of the dimensionless residence time, the performance of the bioreactor is independent of the recycle ratio.
We propose a locally smoothing method for some mathematical programs with complementarity constraints, which only incurs a local perturbation on these constraints. For the approximate problem obtained from the smoothing method, we show that the Mangasarian–Fromovitz constraints qualification holds under certain conditions. We also analyse the convergence behaviour of the smoothing method, and present some sufficient conditions such that an accumulation point of a sequence of stationary points for the approximate problems is a C-stationary point, an M-stationary point or a strongly stationary point. Numerical experiments are employed to test the performance of the algorithm developed. The results obtained demonstrate that our algorithm is much more promising than the similar ones in the literature.
We study the stability of inviscid, incompressible swirling flows of variable density with respect to azimuthal, normal mode disturbances. We prove that the wave velocity of neutral modes is bounded. A further refinement of Fung’s semi-elliptical instability region is given. This new instability region depends not only on the minimum Richardson number, and the lower and upper bounds for the angular velocity like Fung’s semi-ellipse, but also on the azimuthal wave number and the radii of the inner and outer cylinders. An estimation for the growth rate of unstable disturbances is obtained and it is compared to some of the recent asymptotic results.
One of the major reasons for the failure of materials or components is stress. The understanding and analysis of stress is a very important step in any design. Our primary objective here is to identify the stress, and then discuss the scheme of analysis for simple and complex situations.
10.2 Definitions
Stress is defined as the intensity of internal reaction. The intensity is measured with respect to the area. Consider a body in equilibrium under the action of certain forces as shown in Figure 10.1a.
Kinematics is the study of the motion of particles and rigid bodies disregarding the forces associated with these motions.
6.2 Kinematics of particle
Kinematics of particle involves the study of position, velocity and acceleration of the particle without any consideration of the forces working on it. Particle can move on a straight line, on a plane or in space. We will restrict our study to plane motion only. The plane motion of the particle is classified as:
(a) Straight line motion
(b) Motion on curved path
Following classification of motion on curved path is useful from application point of view
(a) Position, velocity and acceleration in terms of Cartesian components
(b) Position, velocity and acceleration in terms of path variables and
(c) Position, velocity and acceleration in terms of polar coordinates
A mechanical member subjected to a force system perpendicular to its axis is called beam. The moment of force system at any point on the beam is perpendicular to the axis of the beam. Stress developed in the beam due to bending moment is called bending stress. The bending stress developed on any section of the beam is normal to the section. The stress developed is such that the resultant reaction on the section is zero.
In general, the shear force and bending moment both are present at a section of a beam. In particular, if the shear force is absent and only bending moment is present on a beam, the beam is said to be in pure bending. Due to pure bending, the beam bends in the form of a circular arc as shown in Figure 11.1. The bending moment, which develops curvature upwards, is also called as sagging moment (Figure 11.1b). Similarly, the moment, which produces curvature downwards is called hogging moment (Figure 11.1a). It is clear from Figure 11.1 that the fibres toward the center of curvature are compressed and the outer fibres are elongated. The stresses developed in both the regions are shown in the Figure 11.1.
A mechanical member is, in general, subjected to different types of loads. The mechanical members, depending on the type of loading, have been given different names in technical literature. Some technical names and loadings are given as follows:
(a) Column: Member subjected to compressive force along its axis (Figure 3.1a). Visible effect: Shortening in axial length of the member.
(b) Shaft: Member subjected to moments along the axis. Such a moment is called torque or twisting moment (Figure 3.1b). Visible effect: The relative rotation of the sections about the axis.
(c) Beam: Member subjected to forces and/or moments perpendicular to the axis (Figure 3.1c). Visible effect: The axis becomes curved. This is called bending and the moment responsible for it is called bending moment.
3.2 Terminology
(a) On the basis of supports, the beams are classified as:
(i) Simply supported: Both the supports are at the end and are either pin or roller (Figure 3.2a).
(ii) Cantilever: Fixed at one end and free at the other (Figure 3.2b).
(iii) Overhanging: Beam is larger than the distance between the supports, and is projected beyond the supports (Figure 3.2c).
(iv) Fixed beam: Both the ends are fixed (Figure 3.2d).
(v) Continuous beam: Beams having more than two supports (Figure 3.2e).
Vibration is a very common phenomenon in machines. In certain situations, the control of vibration is very essential. To control the vibration, proper understanding of the phenomenon is desired. The essence of vibration is discussed below.
A mechanical system is said to vibrate if it executes a simple harmonic motion or oscillation.
The problem of oblique wave scattering by a rectangular submarine trench is investigated assuming a linearized theory of water waves. Due to the geometrical symmetry of the rectangular trench about the central line $x=0$, the boundary value problem is split into two separate problems involving the symmetric and antisymmetric potential functions. A multi-term Galerkin approximation involving ultra-spherical Gegenbauer polynomials is employed to solve the first-kind integral equations arising in the mathematical analysis of the problem. The reflection and transmission coefficients are computed numerically for various values of different parameters and different angles of incidence of the wave train. The coefficients are depicted graphically against the wave number for different situations. Some curves for these coefficients available in the literature and obtained by different methods are recovered.
We compare six fixed-stepsize fourth-order numerical methods for a number of test problems described by a system of coupled Korteweg–de Vries equations. Particular attention is paid to the ability of these methods to preserve fixed points (solitary waves) and the invariants of the system, and establishing to what extent the conservation of integral invariants is indicative of the solution error for these methods.