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We investigate the cross-sectional buckling of multi-concentric tubular nanomaterials, which are called multiwalled carbon nanotubes (MWNTs), using an analysis based on thin-shell theory. MWNTs under hydrostatic pressure experience radial buckling. As a result of this, different buckling modes are obtained depending on the inter-tube separation d as well as the number of constituent tubes N and the innermost tube diameter. All of the buckling modes are classified into two deformation phases. In the first phase, which corresponds to an elliptic deformation, the radial stiffness increases rapidly with increasing N. In contrast, the second phase yields wavy, corrugated structures along the circumference for which the radial stiffness declines with increasing N. The hard-to-soft phase transition in radial buckling is a direct consequence of the core-shell structure of MWNTs. Special attention is devoted to how the variation in d affects the critical tube number Nc, which separates the two deformation phases observed in N -walled nanotubes, i.e., the elliptic phase for N < Nc and the corrugated phase for N > Nc. We demonstrate that a larger d tends to result in a smaller Nc, which is attributed to the primary role of the interatomic forces between concentric tubes in the hard-to-soft transition during the radial buckling of MWNTs.

The term “buckling” refers to a deformation through which a pressurized material undergoes a sudden failure and exhibits a large displacement in a direction transverse to the load [

An interesting class of elastic buckling can be observed in structural pipe-in-pipe cross sections under hydrostatic pressure [2,3]. Pipe-in-pipe (i.e., a pipe inserted inside another pipe) applications are commonly used in offshore oil and gas production systems in civil engineering. In subsea pipelines in deep water, for instance, buckling resistance to huge external hydrostatic pressure is a key structural design requirement. Pipe-inpipe systems may be an efficient design solution that meets this strict requirement, because their concentric structures enable the cross section to withstand high pressure without collapsing.

The above argument regarding macroscopic objects poses a question as to what buckling behavior may be observed in nanometer-scale (10^{–}^{9} m) counterpart objects. In nanomaterial sciences, the buckling of carbon-based hollow cylinders with nanometric diameters (called carbon nanotubes) has drawn great attention [

In this article, we focus our attention on the radial buckling of carbon nanotubes observed under hydrostatic pressure on the order of several hundreds of megapascal. Thin-shell-theory based analysis on the cross-sectional deformation of nanotubes leads us to the conclusion that the buckled patterns strongly depend on the inter-tube separation, the number of constituent tubes, and the innermost tube diameter. In particular, the expansion of from its equilibrium value (0.34 nm) causes a lowering of the critical tube number that characterizes the hard-to-soft transition in the nanotubes’ radial buckling. These results shed light on the possible control of the morphology of carbon nanotubes by experimentally tuning.

Carbon nanotubes are one of the most promising nanomaterials, and they consist of layers of graphene sheets that are each a single atom thick (two-dimensional hexagonal lattices of carbon atoms) rolled up into concentric cylinders [

The excellent mechanical properties of carbon nanotubes are characterized by the remarkably high Young’s modulus, which is on the order of terapascal (i.e., several times stiffer than steel), and the tensile strength, which is as high as tens of gigapascal [

Emphasis should be placed on the fact that on application of a mechanical deformation, carbon nanotubes show significant changes in their physical and chemical properties [34,35]. Precise knowledge of their deformation mechanism and available geometry is, therefore, crucial for understanding their structure-property relations and for developing next generation carbon-nanotube-based applications.

The aim of this section is to deduce the stable cross-sectional shape of a MWNT under a hydrostatic pressure. The continuum elastic approximation [36- 41] allows the mechanical energy of a MWNT per axial length to be expressed as follows:

Here, is the deformation energy of all concentric tubes, is the interaction energy of all adjacent pairs of tubes, and is the potential energy of the applied pressure. All these three energy terms are functions of and the deformation amplitudes and that describe the radial and circumferential displacements, respectively, of the th tube. See Equation (7) below for the precise definitions of and.

The optimal displacements and that minimize under a given are obtained via the calculus of variations to with respect to and. To proceed, we derive the explicit forms of, , and as functions of, , and in the subsequent section.

Evaluating the functional form of requires the relation between the displacements, and, and the circumferential strain, , of a hollow tube driven by cross-sectional deformation. Suppose there is a circumferential line element of length^{1} lying at an arbitrary point within the cross section of a tube with thickness. The hydrostatic pressure upon the tube causes an extensional strain of the line element, which is defined as follows:

Here, , and is the length of the line element after deformation (the asterisk symbolizes the quantity after deformation). The coordinates, of the element after deformation are given as follows:

where and are the components of the displacement vector in the radial and circumferential directions, respectively. We can then write the following relationships:

the following relationship can be obtained:

where, etc. The term in Equation (6) accounts for the rotation of the line element due to the deformation [

Hereafter, we assume that and are both significantly smaller than unity, because an infinitesimal deflection of the initially circular cross section is assumed to determine the critical buckling pressure. The second term in the right side in Equation (6) can therefore be omitted if the possibility that or is larger than is excluded. We further assume that the normals to the undeformed centroidal circle of the hollow tube’s cross section remain straight, normal, and unextended during the deformation [

where and denote the displacements of a point that lies on, and is a radial coordinate measured from. By substituting Equation (7) into Equation (6), we can derive the following strain-displacement relationship:

where the following definitions hold true:

Here, and are the in-plane and bending strains, respectively, of the th tube; is the radius of the undeformed circle. Equations (8) and (9) state that the circumferential strain at an arbitrary point in the cross section is determined by the displacements and of a point that lies on the undeformed centroidal circle.

We are now ready to derive the explicit form of the deformation energy. Suppose that the th constituent tube has a thickness. A surface element of the crosssection of the hollow tube can then be expressed by. The stiffness of the surface element for stretching along the circumferential direction is given as follows:

where and are the Young’s modulus and Poisson’s ratio, respectively, of the tube. Thus, the deformation energy per axial length can be written as follows:

in which the component associated with the th tube is written as follows:

From Equations (8) and (12) we obtain the following relationship:

which can also be written as follows:

The constant denotes the in-plane stiffness, the flexural rigidity, and the Poisson ratio of each tube.

For quantitative discussions, the values of and must be carefully determined. In cases of macroscopic objects, they are defined as and

. However, for carbon nanotubesthe macroscopic relations for and noted above fail because there is no unique way of defining the thickness of the graphene tube [^{2} Thus, the values of and should be evaluated ab-initio from direct measurements or through computations involving the properties of carbon sheets, without reference to the macroscopic relations. In actual calculations, we substitute nN/nm, nN·nm, and in a similar fashion as a previous study [

The energy associated with the van der Waals (vdW) interaction between adjacent pairs of tubes, designated by in Equation (1), can be written as a sum of components as follows:

We derive the coefficients in Equation (15) through a first order Taylor approximation of the vdW pressure [39,44] associated with the vdW potential as follows:

Here, is the distance between a pair of carbon atoms, nm is the equilibrium distance between two interacting atoms, and nN·nm is the well depth of the potential [

The vdW pressures on the inner and outer tubes of a concentric two-walled tube with radii and are given as follows [

where. The area density of carbon atoms is given by nm^{–2}.

In Equation (18), , ,

, and, and

.

In the following, we obtain analytical expressions for by linearizing the Equation (17) for the pressure [

where is the mean radius and is the vdW pressure on the th tube. The corresponding linearized pressure is given by. In Equation

(19), describes the length of the infinitesimal element on which the pressure is acting. Using the linearized pressure and comparing with Equation (15), the following expressions for the vdW coefficients can be found:

where the derivatives in Equation (20) are defined as follows:

Note that is symmetric. The set of Equations (15), (20), and (21) allows for the evaluation of.

We finally derive an explicit form of, which is the negative of the work done by the external pressure during cross-sectional deformation. Using this definition we can write the following expression:

where is the area surrounded by the th tube after deformation (the sign of is assumed to be positive inward). can then be obtained by evaluating the following expression:

By substituting Equations (3) and (4) into Equation (23), and by using the periodicity relation, the following expression can be obtained:

This section presents our method for determining the critical pressure above which the circular cross section of MWNTs is elastically deformed into a noncircular one. To carry out this analysis, we decompose the radial displacement terms according to . Here, indicates a uniform radial contraction of the th tube at, whose magnitude is proportional to. describes a deformed, non-circular cross section observed just above. Similarly, we can write, because at.

By applying the variational method to with respect to and, we obtain the following system of 2N linear differential equations:

where and. In deriving Equations (25) and (26), the quadratic and cubic terms in and are omitted because we only consider elastic deformation with sufficiently small displacements. In addition, the terms consisting only of and are also omitted; the sum of such terms should be equal to zero^{3} because represents an equilibrium circular cross-section under.

Because and are periodic in, the general solutions of Equations (25) and (26) are given by the Fourier series expansions as follows:

Substituting these into Equations (25) and (26) leads to the matrix equation, in which the vector consists of and with all possible and, and the matrix involves one variable as well as parameters such as and. The matrix can be expressed as a block diagonal matrix of the form due to the orthogonality of and. Here, is a submatrix that satisfies, where is a 2N-column vector composed of and . As a result, the secular equation that provides nontrivial solutions of Equations (25) and (26) can be rewritten as follows:

By solving Equation (27) with respect to, we obtain a sequence of discrete values of. Each of these values is the smallest solution of . The minimum of these values serves as the critical pressure that is associated with a specific integer. From the definition, the associated with a specific m allows only and to be finite, however, it also requires and. Immediately above, therefore, the circular cross section of MWNTs becomes radially deformed as follows:

where the value of is uniquely determined by the one-to-one relation between and.

Figures 1(a) and (b) show as a function of for various values of the initial tube-tube separation prior to the application of pressure. For all, we observe a rapid increase in with, which is followed by a slow decay when nm (and also for smaller D).^{4} The increase in for small is interpreted as the “hardening” of the MWNTs, i.e., an enhancement of the radial stiffness of the entire MWNT by encapsulation. This hardening effect disappears with a further increase in, which results in the decay of. A decay in implies that a relatively low pressure suffices to produce a radial deformation, which indicates an effective “softening” of the MWNT. These two contrasting effects, i.e., hardening and softening, are both due to the encapsulation of MWNTs.

^{4}Such a decay is also observed for D = 5.0 nm and larger D, in principle, if a sufficiently large N is considered [but omitted in

We emphasize that in

above for fixed nm and nm. The most striking observation is the successive transformation of the cross section with an increase in. We see from

Of further interest is that the critical number of tubes separating the elliptic phase () from the corrugation phase () is identified as the that

yields a cusp in the curve of [see