The peeling of a flexible strip attached by a cavitating viscous adhesive

Summary A theory is presented for the peeling of a completely flexible strip from a plane rigid surface to which it had been attached by a thin layer of adhesive. The adhesive is taken to be a purely viscousNewtonian liquid, and is assumed to fail by cavitation or the dilation of bubbles of trapped gas. By such a model a relation between peeling rate and peeling force (which in the absence of any reduction in pressure within the cavities would be linear) may be found.The significance of surface tension in defining boundary conditions in dividing liquid layers, is discussed, and the implication of a vanishing significance of surface tension on the limiting form of these conditions, provides a basis for the analysis.The absence of relevant experimental data precludes direct comparison, but the physical appearance of real adhesives in peeling is seen to be not inconsistent with the model proposed.This work was performed at the Cavendish Laboratory, University of Cambridge. The assistance of an Australian Commonwealth Public Service Board Scholarship, and the computing facilities at the Mathematical Laboratory, University of Cambridge, England, is gratefully acknowledged.     

The Laminar Boundary Layer over a Permeable Wall

An analysis is given of the laminar boundary layer over a permeable/porous wall. The porous wall is passive in the sense that no suction or blowing velocity is imposed. To describe the flow inside and above the porous wall a continuum approach is employed based on the Volume-Averaging Method (S. Whitaker The method of volume averaging). With help of an order-of-magnitude analysis the boundary-layer equations are derived. The analysis is constrained by: (a) a low wall permeability; (b) a low Reynolds number for the flow inside the porous wall; (c) a sufficiently high Reynolds number for the freestream flow above the porous wall. Two boundary layers lying on top of each other can be distinguished: the Prandtl boundary layer above the porous wall, and the Brinkman boundary layer inside the porous wall. Based on the analytical solution for the Brinkman boundary layer in combination with the momentum transfer model of Ochoa-Tapia and Whitaker (Int. J. Heat Mass Transfer 38 (1995) 2635). for the interface region, a closed set of equations is derived for the Prandtl boundary layer. For the stream function a power series expansion in the perturbation parameter is adopted, where is proportional to ratio of the Brinkman to the Prandtl boundary-layer thickness. A generalization of the Falkner–Skan equation for boundary-layer flow past a wedge is derived, in which wall permeability is incorporated. Numerical solutions of the Falkner–Skan equation for various wedge angles are presented. Up to the first order in wall permeability causes a positive streamwise velocity at the interface and inside the porous wall, but a wall-normal interface velocity is a second-order effect. Furthermore, wall permeability causes a decrease in the wall shear stress when the freestream flow accelerates, but an increase in the wall shear stress when the freestream flow decelerates. From the latter it follows that separation, as indicated by zero wall shear stress, is delayed to a larger positive pressure gradient.     

Interaction between elliptical and ellipsoidal inclusions under bending stress fields

Summary  This paper deals with interaction problems of elliptical and ellipsoidal inclusions under bending, using singular integral equations of the body force method. The problems are formulated as a system of singular integral equations with Cauchy-type or logarithmic-type singularities, where unknown functions are densities of body forces distributed in the x,y and r,θ,z directions in infinite bodies having the same elastic constants as those of the matrix and inclusions. In order to satisfy the boundary conditions along the elliptical and the ellipsoidal boundaries, the unknown functions are approximated by a linear combination of fundamental density functions and polynomials. The present method is found to yield the exact solutions for a single elliptical or spherical inclusion under a bending stress field. It yields rapidly converging numerical results for interface stresses in the interaction of inclusions. Received 9 September 1999; accepted for publication 15 January 2000     

Nonlinear axisymmetric static and transient analysis of orthotropic thick annular plates

Summary This paper deals with the geometrically nonlinear axisymmetric static and transient response of moderately thick cylindrically orthotropic circular plates subjected to uniformly distributed and ring loads. Immovable clamped and simply supported annular plates with and without a rigid plug subjected to static and step function loads have been considered. Shear deformation and rotary inertia have been included. Orthogonal point collocation method and Newmark- scheme have been employed to solve the differential equations expressed in terms of transverse displacement , shear rotation and stress function . The effect of transverse shear has been investigated for isotropic and orthotropic plates. A simple approximate method has also been used to predict the maximum dynamic response to step loads from the results for static loads.

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Nichtlineare, axialsymmetrische, statische und dynamische Analyse orthotroper, dicker Kreisringplatten

Übersicht Es wird das geometrisch nichtlineare, axialsymmetrische Verhalten orthotroper Kreisring-platten unter gleichmäßig bzw. ringförmig verteilten Lasten untersucht. Eingespannte und gelenkig gelagerte Platten mit oder ohne starrem Pfropfen unter statischer oder dynamischer Belastung werden behandelt, wobei Schubdeformation und Drehträgheit berücksichtigt werden. Eine Kollokationsmethode und das Newmarksche -Schema werden angewendet, um die Differentialgleichungen für die Durchbiegung , die Verdrehung und die Spannungsfunktion zu lösen.

     

Transversely isoiropic beam under initial stress

Starling from Novozhilov’s nonlinear equations of elasticity by appropriate simplification and integration over the beam cross-section, a linearized set of equations for a transversely isotropic beam under initial non-uniform state of stress is obtained. In the absence of initial stress, the obtained equations are reduced to well-known Timoshenko beam equations.These equations are applied to investigate the vibration and buckling characteristics of a transversely isotropic beam under uniform initial axial force and bending moment.     

The equations of motion for a nonholonomic system under the action of impulsive forces

The equations of impact for a nonholonomic system described with generalized coordinated have been discussed in detail in the general references of classical dynamics. But these equations contain undetermined multipliers which made the problem complicated. Through the appropriate treatment of mathematics, using the -function and expression of matrix in this paper, the author derived equations of impact for a nonholonomic system without undetermined multipliers. Therefore, the problem can be solved more simply.     

Nichtlineare Biegung und Beulen von Zylindern und krummen Rohren bei Normaldruck

Übersicht Es wird die reine nichtlineare Biegung eines elliptischen Rohres unter Normaldruckbelastung untersucht. Das Problem wird durch zwei Integrodifferentialgleichungen vom Reissner-Meissner-Typ beschrieben, die mittels der Fourierreihenapproximation der Lösungsfunktionen integriert werden. Die nichtlinearen Biegemoment-Krümmungsänderungskurven werden für verschiedene Parameter (Halbachsenverhältnis A/B, Normaldruckbelastung q, Krümmungsparameter ) angegeben und diskutiert. Das Beulen der Rohre bei Biegung wird mittels einer Hypothese des lokalen Beulens bestimmt.

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Nonlinear bending of elliptic tubes under normal pressure

Summary The pure nonlinear bending of an elliptic tube under normal pressure is investigated. The problem is described by two integro-differential equations of the Reissner-Meissner type which are integrated with the means of approximating the solution function by Fourier series. The curves bending moment vs curvature change are given and discussed for various parameters (ratio of axes A/B, normal pressure q, curvature parameter ). The buckling of the tubes under the bending load is determined by a hypothesis of local buckling.

     

Elasticity solutions for a transversely isotropic functionally graded circular plate subject to an axisymmetric transverse load qrk

This paper considers the bending of transversely isotropic circular plates with elastic compliance coefficients being arbitrary functions of the thickness coordinate, subject to a transverse load in the form of qr^k (k is zero or a finite even number). The differential equations satisfied by stress functions for the particular problem are derived. An elaborate analysis procedure is then presented to derive these stress functions, from which the analytical expressions for the axial force, bending moment and displacements are obtained through integration. The method is then applied to the problem of transversely isotropic functionally graded circular plate subject to a uniform load, illustrating the procedure to determine the integral constants from the boundary conditions. Analytical elasticity solutions are presented for simply-supported and clamped plates, and, when degenerated, they coincide with the available solutions for an isotropic homogenous plate. Two numerical examples are finally presented to show the effect of material inhomogeneity on the elastic field in FGM plates.     

Asymptotic analysis of the nonlinear equations for an infinite,rubber-like slab under an equilibrated vertical line load

An infinite slab of incompressible Rivlin-Saunders material of constant thickness 2H is subject to an equilibrated, radially varying, vertical body force, comprising a concentrated, downward line load and a smooth, upward, exponentially distributed load with a characteristic decay length R. The deformation is axisymmetric and described by three stretches and a shear strain (or, equivalently, four strains) and a rotation which satisfy three relatively simple compatibility conditions. Force equilibrium is satisfied identically by the introduction of three stress functions. The incompressibility constraint is used to eliminate the normal stretch. With the introduction of stress-strain relations, the field equations are reduced to a set of seven, first-order, quasilinear partial differential equations. The loads, the radial distance, and the unknowns are scaled by the small parameter =H/R. As 0, 11 possible sets of field equations are found, including linear plate theory, von Kármán plate theory, Föppl membrane theory, large-strain membrane theory, and Wu's large-stretch (asymptotic) membrane theory. Notably absent as limiting cases are thick plate theories.This work was supported by the National Science Foundation under grant MSM-8618657-02.     

Exact static solutions to piezoelectric smart beams including peel stresses. II. Numerical results,comparison and discussion

This part presents the numerical results, comparisons and discussion for the exact static solutions of smart beams with piezoelectric (PZT) actuators and sensors including peel stresses presented in Part I. (International Journal of Solids and Structures, 39, 4677–4695) The actuated stress distributions in the adhesive and the adhesive edge stresses varying with the thickness ratios are firstly obtained and presented. The actuated internal stress resultants and displacements in the host beam are then calculated and compared with those predicted by using the shear lag model. The stresses in the adhesive caused by an applied axial force, bending moment and shear force are calculated, and then used to compute the sensing electric charges for comparison with those predicted using the shear lag model. The numerical results are given for the smart beam with (a) one bonded PZT and (b) two symmetrically bonded PZTs, with a comparison to those predicted using the shear lag model. Novel, simple and more accurate formulas for the equivalent force and bending moment induced by applied electric field are also derived for the host beam with one PZT or two symmetrically bonded PZTs. The symmetric shear stress and the anti-symmetric peel stress components caused by a shear force are discussed. In addition, in the case of PZT edge debonding, the stress redistribution in the adhesive and the self-arresting mechanism are also investigated.     

Body-force stress fields defined by caustic rosettes

The method of reflected caustics was extended to the study of elastic fields due to body forces. It was shown that gage perforations create caustics under the influence of body forces which are different in shape and size than those developed in usual cases. The elastic solution of a perforated strip under the influence of an external loadp and body forcesqy was developed by defining a two-term Muskhelishvili complex stress function (z). The equations of the caustics and their initial curves were established. It was shown that as the body force intensity,q, was increased relative to the external loading,p, the classical two-lobe caustic for perforated strips without body forces evoluted to an open curve and, for a further increase ofq, to a three-lobe caustic. As the body force to external force ratio was increased this third lobe was rapidly increased, relative to the two principal lobes, whereas the position of the center of the caustic was displaced along the loading axis. The maximum diametersD _t of the caustics along the loading axis of the plate yield enough information for evaluating the body force intensity, if the mechanical properties of the material and the geometry of the optical set-up are known.     

General plane elasticity solution for non-homogeneous materials

In this study, we consider the general plane elasticity problem for non-homogeneous materials subjected to mechanical and thermal loads. The general equations are derived in x–y coordinate system. It is shown that, if the non-homogeneity varies exponentially, then the governing equations are reduced to partial differential equations with constant coefficients. To illustrate the validity and usefulness of the formulation, problems involving both mechanical and thermal loads with the non-homogeneity varying in both directions are considered. As examples, infinite non-homogeneous beams subjected to axial load and bending moment are considered and the solutions obtained in closed form. Then an example illustrating the effect of temperature change is presented. Again a closed form solution is obtained for the stress distribution. Also for limiting values of the non-homogeneity parameter, extensive asymptotic analyses are presented. In addition two problems where the Young’s Modulus or the coefficient of thermal expansion coefficient varies in both directions are presented. From the examples solved, it is found that non-homogeneity affects the stress distribution significantly, and leads to counterintuitive results with serious implication to the study of fracture problems in functionally graded materials.     

Dynamic geometrically nonlinear analysis of transversely compressible sandwich plates

In order to construct a plate theory for a thick transversely compressible sandwich plate with composite laminated face sheets, the authors make simplifying assumptions regarding distribution of transverse strain components in the thickness direction. The in-plane stresses and σ_yy (Fig. 1) are computed from the constitutive equations, and the improved values of transverse stress components and σ_zz need to be computed by integration of pointwise equations of motion in a post-process stage of the finite element analysis. The improved values of the transverse strains can also be computed in the post-process stage by substituting the improved transverse stresses into the constitutive relations. A problem of cylindrical bending of a simply supported plate under a uniform load on the upper surface is considered, and comparison is made between the displacements, the in-plane stress and the improved transverse stresses (obtained by integration of the pointwise equations of motion), computed from the plate theory, with the corresponding values of exact elasticity solutions. In this comparison, a good agreement of both solutions is achieved. In the finite element analysis of sandwich plates in cylindrical bending with small thickness-to-length ratios, the shear locking phenomenon does not occur. The model of a sandwich plate in cylindrical bending, presented in this paper, has a wider range of applicability than the models presented in literature so far: it can be applied to the sandwich plates with a wide range of ratios of thickness to the in-plane dimensions, with both thin and thick face sheets (as compared to the thickness of the core) and to the sandwich plates with both transversely rigid and transversely compressible face sheets and cores.     

A misfitting elastic inclusion in an infinite plane containing a crack

The problem discussed in this paper is that of a misfitting circular inclusion in an infinite elastic medium which contains a straight crack. The crack is stress free. The stresses develop in the elastic medium because of the misfit. The point force method is used to solve the problem. The problem reduces to finding two sets of complex potential functions: {(z), (z)}: One for the infinite medium and the other for the misfitting inclusion. The solution has been obtained in closed form. Graphs are drawn for stress intensity at the crack tip and also for normal, shear and hoop stresses at the common interface of medium and misfitting inclusion.     

A power-law fluid flow past a porous sphere

Summary A model has been developed for the flow of a non-Newtonian fluid past a porous sphere. The drag force exerted on a porous sphere moving in a power-law fluid is obtained by an approximate solution of equations of motion in the creeping flow regime. It is predicted that the effect of the pseudoplastic anomaly on the drag force is more pronounced at large porosity parameters.

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Zusammenfassung Es wird ein Modell für die Strömung einer nichtnewtonschen Flüssigkeit längs einer porösen Kugel entwickelt. Die auf die in einer Ostwald-DeWaele-Flüssigkeit bewegte Kugel ausgeübte Reibungskraft wird durch eine Näherungslösung der Bewegungsgleichungen für schleichende Strömung gewonnen. Man findet, daß der Einfluß der Abweichung vom newtonschen Verhalten um so ausgeprägter wird, je größer die Porosität ist.

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A, B, C, D a, b, c, d coefficients in eqs. [10] and [18] - F _D drag force - K consistency index in power-law model - k ₁ ,k ₂ coefficients defined by eq. [18] - m porosity parameter - n flow index in power-law model - P pressure - P ^* dimensionless pressure defined by eq. [4] - P pressure difference - R radius of porous sphere - r radial distance from the center of the sphere - U velocity of uniform stream - u _i velocity component - u _i ^* dimensionless velocity component defined by eq. [4] - Y drag force correction factor defined by eq. [27] - _ij rate of deformation tensor - _ij ^* dimensionless rate of deformation tensor defined by eq. [4] - , spherical coordinates - dimensionless radial distance defined by eq. [4] - second invariant of rate of deformation tensor - ^* dimensionless second invariant of rate of deformation tensor defined by eq. [4] - _ij stress tensor - _ij ^* dimensionless stress tensor defined by eq. [4] - stream function - ^* dimensionless stream function defined by eq. [4] - i inside the surface of the sphere - o outside the surface of the sphere With 1 figure and 1 table     

Chaotic phenomena in the dynamic buckling of an elastic-plastic column under an impact

The present study is concerned with the dynamic anomalous response of an elastic-plastic column struck axially by a massm with an initial velocityv ₀. This simple example is considered in order to clarify the influence of the impact characteristics and the material plastic properties on the dynamic buckling phenomenon and particularly on the final vibration amplitudes of the column when it shakes down to a wholly elastic behaviour. The material is assumed to have a linear strain hardening with a plastic with a plastic reloading allowed. These material properties are the reason a number of elastic-plastic cycles to be realized prior to any wholly elastic stable behaviour, which causes different amounts of energy to be absorbed due to the plastic deformations.The column exhibits two types of behaviour over the range of the impact masses — a quasi-periodic and a chaotic response. The chaotic behaviour is caused by the multiple equilibrium states of the column when any small changes in the loading parameters cause small changes in the plastic strains which result in large changes in the response behaviour. The two types of behaviour are represented by displacement-time and phase-plane diagrams. The sensitivity to the load parameters is illustrated by the calculation of a Lyapunov-like exponent. Poincaré maps are shown for three particular cases.Notation c elastic wave propagation speed - m impact mass - m _c column mass - s step of the spatial discretization - t time - u(x,t) axial displacement - v ₀ initial velocity - w ₀(x) initial imperfections - w(x,t)+w ₀(x) total lateral displacements - x axial axis - z axis along the column thickness - A cross-section areahb - E Young's modulus - E _t hardening modulus (Figure 2) - M(x,t) bending moment - N(x,t) axial force - impact mass ratiom/m _c - (x,z) strain - Lyapunov-like exponent - material density - (x,z) stress     

Evaluating Herschel-Bulkley fluids with the back extrusion (annular pumping) technique

A mathematical model was developed to describe the behavior of Herschel-Bulkley fluids in a back extrusion (annular pumping) device. A technique was also developed to determine the rheological properties (yield stress, flow behavior index, and consistency coefficient) of these fluids. Mathematical terms were expressed in four dimensionless terms, and graphical aids and tables were prepared to facilitate the handling of the expressions.Nomenclature a radius of the plunger, m - dv/dr shear rate, s^–1 - F force applied to the plunger, N - F _b buoyancy force, N - F _cb force corrected for buoyancy, N - F _T recorded force just before the plunger is stopped, N - F _Te recorded force after the plunger is stopped, N - g acceleration due to gravity, m/s² - H(t) momentary height between plunger and container bottom, m - K a/R, dimensionless - L length of annular region, m - L(t) depth of plunger penetration, m - n flow behavior index, dimensionless - p static pressure, Pa - P _L pressure in excess of hydrostatic pressure at the plunger base, Pa - p ₀ pressure at entrance to annulus, Pa - P pressure drop per unit of length, Pa/m - Q total volumetric flow rate through the annulus, m³/s - r radial coordinate, measured from common axis of cylinder forming annulus, m - R radius of outer cylinder of annulus, m - s reciprocal of n, dimensionless - t time, s - T dimensionless shear stress, defined in Eq. (3) - T ₀ dimensionless yield stress, defined in Eq. (4) - T _w dimensionless shear stress at the plunger wall - _p velocity of plunger, m/s - velocity, m/s - mass density of fluid, kg/m³ - Newtonian viscosity, Pa s - P p ₀ –p _L , Pa - consistency coefficient, Pa sⁿ - value of where shear stress is zero - _–, ₊ limits of the plug flow region (Fig. 1) - r/R - shear stress, Pa - _y yield stress, Pa - _w shear stress at the plunger wall, Pa - dimensionless flow rate defined in Eq. (24) - dimensionless velocity defined by Eq. (5) - _–, ₊ dimensionless velocity outside the plug flow region - _max dimensionless maximum velocity in the plug flow region - _p dimensionless velocity at the plunger wall     

Torsional rigidity of shells of revolution

In this paper, the general equations of equilibrium for axisymmetrical deformation including the torsional deformation of revolutional shells are derived. It is shown that the shearing stress distribution due to torsion is independent of other stress components including those of membrane stress and bending stress. In this paper, the torsional deformation is considered to be represented by membrane action only, and also by the combined action of bending membrane deformation. It is shown that the main contribution of torsional rigidity is that related to membrane action.     

Hydrodynamic lubrication of ball and socket joints

Summary As a step towards formation of design rules for ball and socket joints, a solution of the lubrication equations for an ideal joint (in which the socket completely surrounds the ball) under steady loading and rotation is presented. The results are compared with those for an infinitely wide plain bearing. The friction for the ball is found to be higher, and the load capacity lower, than that of the plain bearing under similar conditions.Notation h lubricant film thickness - p pressure - absolute viscosity - average of v, w, over film thickness h - v, w components of fluid velocity in , directions - U , U components of relative velocity of surfaces in , directions - R mean radius of spheres - H difference between ball and socket radii - c eccentricity ratio - angular speed of ball - B =pH ²/6cR ² - P load component along Oy - N load component along Oz - M driving moment to spin around Ox - moment coefficient - _p , P _p suffix p refers to unit width of plain bearing