Research Article | Open Access

A. Van Hirtum, "Deformation of a Circular Elastic Tube between Two Parallel Bars: Quasi-Analytical Geometrical Ring Models", *Mathematical Problems in Engineering*, vol. 2015, Article ID 547492, 15 pages, 2015. https://doi.org/10.1155/2015/547492

# Deformation of a Circular Elastic Tube between Two Parallel Bars: Quasi-Analytical Geometrical Ring Models

**Academic Editor:**Francesco Tornabene

#### Abstract

Several engineering problems are confronted with elastic tubes. In the current work, homothetic quasi-analytical geometrical ring models, ellipse, stadium, and peanut, are formulated allowing a computationally low cost ring shape estimation as a function of a single parameter, that is, the pinching degree. The dynamics of main geometrical parameters due to the model choice is discussed. Next, the ring models are applied to each cross section of a circular elastic tube compressed between two parallel bars for pinching efforts between 40% and 95%. The characteristic error yields less than 4% of the tubes diameter when the stadium model was used.

#### 1. Introduction

An accurate description of a constricted channel’s geometry and related geometrical features is often crucial and, therefore, a recurrent problem in different engineering disciplines. Geometrical features will affect main fluid flow characteristics related to inertia, boundary layer development, flow detachment, or jet formation downstream from the constricted channel portion [1]. The same way, the accuracy of wave related problems will depend on the channels or waveguides geometry since it will influence among others the propagation or evanescence of higher order propagation modes [2]. Knowledge of the channel geometry is in particular an obstacle when dealing with natural occurring fluid flow or wave propagation through elastic channels for which no geometrical design is possible and in addition the shape can rapidly vary such as is the case for biological channel flows (lower and upper airway respiratory or blood circulation system) and related biomechanical phenomena.

Partly motivated by the large number of applications, a substantial amount of research is performed (see, e.g., [3–8]) on elastic tube modeling for a variety of boundary and loading conditions since the pioneering work [9–11] on thin-walled elastic tubes. Despite those efforts and the increased insight in the stability and bifurcation of circular elastic tubes, no analytical model is capable of providing geometrical features for channels subjected to rapidly varying loading resulting in small as well as large deformations of thin as well as thick wall tubes of variable length. Therefore, in the current work quasi-analytical parameterised geometrical ring models are used in order to provide geometrical features of a compressed elastic tube. Although those models do not give insight in the dynamics of the elastic ring, they do allow, due to their simplicity, to avoid or overcome some of the limitations of more advantaged analytical models depending on boundary conditions (loading, geometry, …). Therefore, when solely the ring shape (or an associated geometrical parameters) is searched, quasi-analytical geometrical models might be of interest in providing an estimation of the shape at a negligible computational cost while the parameterization favors usage in combination with other analytical model approaches exploiting a limited number of input parameters or when an initialization of the ring shape is needed. This might, for example, be the case for real-life applications for which the boundary conditions can be either unknown or rapidly changing. Moreover, for experimental validation the need to control few well defined geometrical parameters is attractive. In addition, an analytical expression of the sensitivity of the modeled shape (or an associated geometrical parameter) to an uncertainty of the imposed control parameters might be of interest for experimental setup characterization or design purposes.

Quasi-analytical ring models are considered using the minor axis as an input control parameter. The pinching degree of the ring is expressed as where the subscript refers to values associated with a circular ring. For a circular ring, both the minor and major axis yield half the internal diameter . We consider a circular ring with internal perimeter , which is compressed between two parallel bars of length as illustrated in Figure 1(a). It is assumed that the ring has constant wall thickness . Forcing the bars closer together (Figure 1(b)) deforms the ring so that for the ring’s minor axis holds, where denotes the minor axis of the undeformed circular ring. The distance between the pinching bars yields . Deforming the ring results in an elongated ring shape so that the area enveloped by the ring reduces as the bars are forced closer together. The deformed ring is assumed to be symmetrical with respect to its center lines containing the minor and major axis.

**(a) Circular**

**(b) Pinched**

Parameterised geometrical ring models are presented in Section 2 for nonbuckled and buckled rings. Next (Section 3), a simple data-driven procedure is proposed enabling to apply the ring models in order to obtain the geometry of an elastic tube pinched between two parallel bars. A concrete case study for is discussed.

#### 2. Geometrical Ring Models

The internal ring shape is modeled using quasi-analytical elastic ring models which are symmetrical with respect to the center lines. The main input parameters are the minor axis and internal diameter defining the perimeter of the unpinched circular ring. Consequently, the pinching degree of the ring is assumed a known quantity. The considered ring shapes are invariant under homothetic scaling. Therefore, in the following, lengths are normalised () by the internal diameter of the circular ring so that , , and are quantities associated with a circle with unit diameter. Note that the pinching degree is not altered by the normalisation since . Furthermore, since the wall thickness is assumed constant, the shape of the external ring is derived from the shape of the internal ring as , with sign function and the ring expressed in polar coordinates with normalised internal radius , normalised external radius , and angle . Depending on the length of the parallel pinching bars compared to the length of the major axis buckling of the elastic ring will occur (Figure 1) or not as the pinching degree is increased. Therefore, in Section 2.1, geometrical ring models are presented which does not allow to describe buckling. In Section 2.2, a ring model is presented for which buckling of the elastic ring occurs when the pinching degree increases.

##### 2.1. Geometrical Nonbuckling Ring Models: Ellipse and Stadium

The internal ring is pinched between long parallel bars so that as depicted in Figure 1. The ring shape is approximated as an ellipse or a stadium with rounded edges as illustrated in Figure 2.

**(a)**

**(b)**

###### 2.1.1. Ellipse

For given minor axis with , the elliptic ring shape is fully determined by considering a second geometrical parameter such as perimeter or major axis .

When the major axis and minor axis are known the elliptic ring shape in polar coordinates yields [12, 13] where and eccentricity . The perimeter is then obtained from the expression of Ramanujan [14]: and the area yields with . The sensitivity of the radius, perimeter, and area to a variation of the imposed parameters and yields

When the perimeter is used as a second model input parameter instead of the major axis , we assume that its value is conserved when the elastic ring deforms so that holds for all pinching degrees . The elliptic ring shape in polar coordinates for is again of the form (1) for which eccentricity is only a function of since using (2) it follows that

The area yields again or

The sensitivity of the radius to a variation of the imposed parameter yieldswhere the last term expresses the sensitivity of the major axis to a variation of the imposed parameter since

Finally, the sensitivity of the area to a variation of the imposed parameter for a constant perimeter becomes

###### 2.1.2. Stadium with Rounded Edges

The stadium shape, illustrated in Figure 2, consists of two flat portions connected by circular arcs with radius so that the minor axis of the stadium equals the minor axis of the ellipse. The critical angle is defined by the critical distance , which corresponds to half the extent of the flat portion in contact with the parallel pinching bars. As for the ellipse (Section 2.1.1) the stadium shape is fully determined by considering the minor axis and a second geometrical parameter such as perimeter or major axis .

Firstly, assume that the perimeter is conserved when the elastic rings deform so that holds for all pinching degrees . In this case, the stadium ring shape with parameters in polar coordinates is given as a piecewise function of which depends explicitly on the pinching degree :where critical angle and critical distance are a function of pinching degree :

The major axis and area are then expressed by a linear and, respectively, quadratic function of the imposed parameter :

Consequently, the sensitivity of the major axis and area to a variation of the imposed parameter results in, respectively, a constant and a linear function of : whereas the sensitivity of the radius to a variation of the experimental imposed parameter is again expressed by a piecewise function of : which (9) depends explicitly on the pinching degree or .

Next, the major axis instead of the perimeter is used as a second known geometrical parameter in addition to the minor axis . The stadium ring shape with parameters in polar coordinates is again a piecewise function of :

Therefore (14) does not depend explicitly on the pinching degree (), as was the case for (9), but it does depend explicitly on the critical distance and the stadium eccentricity . The perimeter and area are, respectively, a linear and quadratic function of and depend linearly on as well:

Consequently, the sensitivity of the perimeter and area to a variation of the input parameters and is, respectively, constant and linearly dependent on and :

The sensitivity of the radius to a variation of the experimentally imposed parameter is a piecewise function of : which depends explicitly on the stadium eccentricity since .

###### 2.1.3. Comparison of Ellipse and Stadium Ring Models with Perimeter

The geometrical ellipse and stadium ring models with the assumption of constant perimeter are fully determined as a function of a single parameter. We consider the minor axis as a parameter since it is directly related to the pinching degree and therefore a control parameter for ring deformation regardless of the applied model. Single parameter models are in particular of interest to be used in combination with other analytical flow or acoustic models which require a geometrical ring (or cross-section) parameter such as major axis or enveloped area . Therefore, in Figure 3 we consider the impact of the applied geometrical ring model in absence of buckling (ellipse or stadium) on these parameters as a function of pinching degree . Following (11) the normalised major axis of the stadium ring model increases linearly (Figure 8(c)) as a function of pinching degree whereas the normalised area of the stadium model decreases quadratically (Figure 8(d)). From (4) and (5) we deduce that the ring model results in the same tendencies for major axis (maximum difference between ellipse and stadium for all pinching degrees <) and area (maximum difference between ellipse and stadium for all pinching degrees <), although the increase for is not linear as is the case for the stadium model. Major axis of the ellipse is longer than the value of stadium model so that the area enveloped by the ellipse is smaller than the area enveloped by the stadium model. The relative difference between the stadium and ellipse model for major axis and area is further illustrated in Figure 3(c). Where the models are equivalent for both extreme pinching degrees, associated with a circular cross section in absence of pinching ( and ) and a completely pinched ring ( and cross-section area ), the maximum difference (<12%) of major axis between the ellipse and stadium model occurs for a pinching degree of 52% whereas the maximum difference (<7%) between both models for area occurs for a pinching degree of 66%. The sensitivity of major axis and area to a variation of minor axis is illustrated in Figures 3(d) and 3(e). It is seen that so that for both the ellipse and stadium varies less than (maximum difference for all pinching degrees between ellipse and stadium <). For the stadium, the variation of is independent from the pinching degree following (12). For the ellipse, becomes less sensitive to a variation of as the pinching degree increases as expressed in (7). For small pinching degrees the impact of a variation of on the area is small ( for pinching degrees ≤ for the ellipse and ≤ for the stadium). As the pinching degree increases the impact of a variation of on the area becomes more important. In general, the impact of a variation of on the area is of the same order of magnitude for the ellipse and the stadium (maximum difference for all pinching degrees <). Nevertheless, the area using the stadium ring is less sensitive to a variation than when an ellipse is used for pinching degrees ≤; for pinching degrees > the opposite holds. The ellipse and stadium ring shape and associated sensitivity to a variation of minor axis are illustrated in Figure 4(a) for a pinching degree of 50%. As expressed in (6) and in (13) the sensitivity depends on the angle so that it is of interest to consider a global measure of the ring shape to a variation of . Therefore, the maximum value of and mean sensitivity for the entire ring as a function of pinching degree are plotted in Figures 4(b) and 4(c), respectively. In contrast to the sensitivity of , which decreases or remains constant for increasing pinching degree as shown in Figure 3(d), both global measures indicate that the overall sensitivity of the shape increases with the pinching degree. Whereas the mean sensitivity increase remains limited (<3), the maximum sensitivity increase is more important since it yields up to >5 times the variation imposed on for both the ellipse and the stadium. As was observed for the area and major axis the stadium ring model is more sensitive than the elliptic ring model to a variation of for severe constriction degrees (≥60%). The observed maximum difference (>1 for pinching degrees >) is more of less averaged out since the difference in mean sensitivity between both ring models remains small (<0.3) regardless of the pinching degree.

**(a)**

**(b)**

**(c) and**

**(d)**

**(e)**

**(a) Ring shape (left) and sensitivity (right) for**

**(b)**

**(c)**

##### 2.2. Buckling Ring Model: Peanut

In Section 2.1, two geometrical ring models with low computational cost were considered. Both models reduced to a single parameter ring model of the minor axis when applying the assumption of conservation of the perimeter . In this section, a quasi-analytical elastic peanut ring models is outlined. Analytical elastic ring models are expected to become pertinent when the length of the parallel pinching bars (see Figure 1) reduces () so that the loading becomes axial and buckling is likely to occur [4, 6].

###### 2.2.1. Peanut

Each quarter of the peanut ring with center consists of two arc portions as schematised in Figure 5. The peanut ring is then expressed as a function of the radius of the outer arc (with origin ) and twice the angle spanned by the inner arc (with origin ) so that the peanut parameter set is . The peanut ring model is suitable to approximate nonbuckled () and buckled (, second mode) elastic rings. The assumption of conservation of perimeter is made so that the normalized perimeter of the total peanut equals the perimeter of the circular tube and consequently the quarter peanut has a constant length . The total curvature of each quarter peanut yields . The minor axis and major axis of the nonbuckled and buckled peanuts are obtained from parameter set as

**(a)**

**(b)**

The area of the total peanut is given as

Note that for the last term in (20) is omitted since . The bending energy of the quarter peanut yields with denoting the bending energy of the total peanut. The bending energy (21) is then used to express the Lagrange functional associated with the energy of deformation of the peanut ring as a function of as well: with isoperimetric difference of the quarter peanut (), normalized pressure denoting the ratio of hydrostatic pressure , and flexural rigidity modulus of the ring using Young’s modulus , Poisson’s ratio , and normalised wall thickness .

For a given , it is aimed to find the peanut defined by parameter set which minimises the bending energy . When using the normalised pressure as a Lagrange multiplier , the constrained minimisation problem satisfies the Euler-Lagrange equations in terms of : where the prime denotes the derivative with respect to . The system (23) is then solved firstly by eliminating using the first two expressions of (23)

The resulting expression (24) is resubstituted in (23) to find satisfying

Equation (25) is solved by substituting given by the last equation of (23) so that a single equation for is obtained, from which in turn the parameter is obtained straightforwardly.

Once and are determined for given , the polar equation of the corresponding peanut with center taken as the origin is directly given as a piecewise function describing two connected arc portions with centers and as depicted in Figure 5:

Instead of imposing the normalised area , the pinching degree can be used as a constrain parameter using the expression of the minor axis (19). The relationship between normalised area and pinching degree is depicted in Figure 6(a). It is seen that the peanut is fully pinched () when the area yields about 25% of . Pinching degrees greater than 100% result in nonphysical peanut shapes since it corresponds to a negative value of the minor axis and are therefore not considered further. The onset of buckling occurs for pinching degrees greater than 54% (or areas smaller than about 70% of ) so that for those pinching degrees the value of the parameter is greater than the minor axis as illustrated in Figure 6(b).

**(a)**

**(b)**

The Euler-Lagrange equations (23) can be seen as a mapping function for which the parameter vector is determined for each by solving . Consequently, an expression for the modulus of deformation of the peanut is computed by applying the chain rule to find the derivatives and furthermore using Cramer’s rule as [15]: with matrix where

Figure 7(a) illustrates the increase in normalised pressure when the normalised peanut area is decreased from the value of a circle with unit diameter () to complete closure () following (24). The resulting modulus of deformation as a function of normalised pressure is shown in Figure 7.

**(a)**

**(b)**

**(a) for**

**(b) for**

**(c)**

**(d)**

###### 2.2.2. Comparison of Peanut and Nonbuckling Ring Models with Perimeter

Examples of ring shapes obtained using the elliptic, stadium, and peanut ring model for pinching degrees of 30% and 80% are illustrated in Figures 8(a) and 8(b), respectively. The resulting rings are relatively similar for 30% for which the peanut ring is nonbuckled whereas for 80% the peanut ring buckles so that the difference between the peanut shape and the other ring models becomes more pronounced. The impact of the model choice is further quantified as a function of pinching degree for major axis (Figure 8(c)) and enveloped area (Figure 8(d)). It is seen that for the nonbuckled peanut shapes corresponding to pinching degrees ≤ the major axis and area of the peanut yields values in the range between the ones obtained with the elliptic and stadium model. Indeed, the peanut model results in values of and similar to the elliptic model for low pinching degrees (≤15%) and gradually evolves towards values obtained with the stadium model as the pinching degree is increased from 15% to 54%. Consequently, for pinching degrees ≤ the difference between the modeled ring values for and increases with pinching degree due to the increasing difference between the elliptic and stadium ring model which yields < for and < for (see Figure 3(c)). For pinching degrees > the peanut ring is buckled compared to the nonbuckled rings obtained with the elliptic and stadium model. As a result, the difference between modeled values of and obtained with the nonbuckling elliptic and stadium models reduces as the pinching degree increases whereas the difference between the nonbuckling models and the buckled peanut model increases with pinching degree up to 45% for and up to 25% for .

#### 3. Application to an Elastic Tube with

It is aimed to evaluate if the two-dimensional ring models outlined in the previous sections can be applied to model a three-dimensional elastic tube which is pinched somewhere along the longitudinal direction using a simple data-driven procedure. The parallel pinching bars have a length larger than twice the major axis so that holds regardless of the pinching degree. Consequently, it is aimed to model each cross-section as a two-dimensional nonbuckled ring with constant perimeter which is equal to the perimeter of the unpinched circular tube. Therefore, all previously discussed ring models (ellipse, stadium, and peanut) can be applied when one additional parameter, that is, local pinching degree, is known at each cross section. The longitudinal variation of the pinching degree is expressed as follows: since the minor axis depends on the longitudinal dimension . The tube’s geometry, the gathering of geometrical data, and a simple data-driven procedure to apply the two-dimensional (2D) ring models to model a three-dimensional (3D) tube geometry are outlined in Section 3.1. The comparison of modeled and measured geometrical tube features is then presented in Section 3.2.

##### 3.1. Extension from 2D Ring Models to 3D Tube Models: A Data-Driven Procedure

Geometrical data are acquired for a cylindrical elastic tube of length mm in the longitudinal -direction with wall thickness 3 mm and the internal diameter of the undeformed cylindrical tube yields 25 mm. The tube is equipped with a pincer at longitudinal position mm. Concretely, the pincer consists of two parallel circular bars of diameter 6.4 mm oriented along the -axis which enforces a symmetrical deformation of the tubes cross-section shape with respect to its center-plane. The elastic tube with pincer is illustrated in Figures 9(a) and 9(b).

**(a) Major axis , top view**

**(b) Minor axis , side view**

**(c) Laser line for scan**

In order to obtain geometrical data, the tube is mounted on a turning platform controlled by a step motor with accuracy 1.8°. At each rotational position a longitudinal profile of the tube is quantified using a calibrated line laser scan [16, 17]. The turning platform with mounted tube and single longitudinal laser line is illustrated in Figure 9. At the position of the pincer buckling is hindered due to the condition . Consequently, the distance between the parallel bars yields and the minor axis is a known quantity at the pincer position . The pincher effort is expressed by the imposed pincher degree at defined as with mm as before denoting the internal radius of the unpinched cylindrical tube.

Concretely, longitudinal profiles are assessed for 6 different pincher efforts in the range from 40% up to 95% [16, 17]. In order to model the 3D tube using the 2D ring models the minor axis need to be estimated for each cross section so that the required ring model parameter is a known quantity. This way the 2D ring models can be applied to each cross section of the 3D tube resulting in an elliptic, stadium, or peanut tube approximation. Therefore, firstly, the minor () and major () axis are extracted as a function of longitudinal position from the measured longitudinal profiles. Next, the following parameters of the measured longitudinal profiles are extracted: the amplitude at the pincer position of the major axis , the half width at half maximum amplitude of the major axis , and of the minor axis . The parameter values obtained from the 6 assessed pinching degrees are plotted in Figure 10(a) () and in Figure 10(b) (). Polynomial fits are applied to the measured parameters in order to estimate the parameter values for pinching degrees in the range from 40% up to 95%. Concretely, a linear fit is used to estimate the maximum amplitude as a function of pinching degree (coefficient of determination ). A second order polynomial fit is used to approximate the half width at half maximum amplitude of the major axis (coefficient of determination ) and the half width at half maximum amplitude of the minor axis (coefficient of determination ) along the longitudinal direction as a function of pinching degree in the range from 40% up to 95%. The polynomial parameter fits are shown in Figures 10(a) () and 10(b) ().

**(a)**

**(b) ,**

**(c) and for 94%**

Using the polynomial parameter fits for , , and as a function of pinching effort illustrated in Figure 10, the longitudinal minor and major axis are subsequently approximated by symmetrical peak functions centered around the position of the pincer and function of the applied pincer effort :

An example of the measured and estimated and using the data-driven procedure to obtain the parameters needed to apply (31) is illustrated in Figure 10(c). It is seen that the tube deforms symmetrically around the pincer position over a total length of which corresponds to 4 times the internal diameter of the circular tube. Following this simple procedure, the considered 2D ring models can be applied to each cross section of the tube for pinching efforts in the range using (31) and the assumption of a constant perimeter .

##### 3.2. Ring Model Selection: Comparison of Modeled and Measured Data Features

The simple data-driven procedure presented in Section 3.1 is applied to the tube for all 6 experimentally assessed pinching efforts in order to comment on the relevance of the geometrical ring models to estimate the tube geometry for different pinching degrees and the potential impact of the model choice between the elliptic, stadium, and peanut ring models.

We are particularly interested in validating the longitudinal major axis since, as argued in the introduction, this parameter impacts for instance physical phenomena related to wave propagation. Figure 11(a) presents the modeled and measured values of for all of the considered ring models for pinching efforts in the range from 40% up to 95%. The linear increase of with pinching effort characterizing the stadium model reflects the experimentally observed tendency. In particular, the rate of increase is well represented when using the stadium model whereas the offset is overestimated so that is slightly (less than 5% of ) overestimated for all pinching efforts. The elliptic model results in a much more severe overestimation (up to 20% of ) for all pinching degrees so that solely on the estimation of the elliptic model can be rejected. The stadium model does not exhibit the experimentally linear increase of with pinching effort. Nevertheless, for pinching efforts smaller than 70% the accuracy of estimated values of is of the same order of magnitude as obtained using the peanut model. For pinching efforts greater than 54% buckling starts to occur which results in a severe underestimation (up to 20% of ) of . Consequently, solely based on the estimation of , it can be argued that the ring model pick order is stadium, peanut, and elliptic. In general, the discrepancy between the modeled longitudinal profile and the measured profile along the corresponding laser lines (such as the one depicted in Figure 9(c)) is less than 7% of (or less than 4% of the tubes diameter) when applying the stadium ring model to each cross section with the local pinching degree computed using the peak function approximation of as expressed in (31). The discrepancy between the measured and estimated longitudinal stadium profiles is illustrated in Figure 11(b) for pincher effort using the local pinching degree associated with plotted in Figure 10(c).

**(a)**

**(b)**

#### 4. Conclusion

The minor axis of an elastic ring compressed between two parallel bars is directly related to the imposed pinching degree. Therefore, homothetic quasi-analytical geometrical ring models (ellipse, stadium, and peanut) are formulated for a circular ring with unit diameter as a function of pinching degree using the assumption of a constant perimeter. All three ring models reflect the same general tendencies for pinching degrees up to 54%. Therefore, the dynamics due to model choice for pinching degrees ≤ is limited (e.g., ≤7% for the area and ≤12% for the major axis) and is determined by the difference between an elliptic and stadium ring since the peanut ring evolves gradually from elliptic (≤15%) to stadium (at 54%). For pinching degrees greater than 54%, the peanut ring starts to buckle. As a consequence, the dynamics of geometrical features related to the model choice becomes more important (e.g., ≤25% for the area and ≤45% for the major axis).

Next, the ring models are applied to each cross section of an elastic circular tube compressed between two parallel bars for different pinching efforts between 40% and 95%. A simple data-driven procedure is used to provide the local pinching degree required as an input parameter. Overall, the stadium ring model provides the best approximation of the tube with a characteristic error yielding less than 4% of the tubes diameter. Moreover, the experimentally observed linear increase of the major axis with the pinching effort is an inherent property of the stadium model. Consequently, the case study illustrates that the outlined quasi-analytical models, such as the stadium model, can provide an accurate and computational low cost approximation of the tubes geometry suitable for applications such as geometry initialisation, combination with other parameterised physical/mathematical models or experimental setup design, and validation purposes as a function of pinching degree.

#### Conflict of Interests

The author declares that there is no conflict of interests regarding the publication of this paper.

#### Acknowledgments

This work was partly supported by EU-FET Grant (EUNISON 308874). Daniel Manica and Guillaume Popovici are acknowledged for their contribution to the experiments.

#### References

- P. Kundu,
*Fluid Mechanics*, Academic Press, London, UK, 1990. - A. Pierce,
*Acoustics. An Introduction to Its Physical Principles and Applications*, Acoustical Society of America, New York, NY, USA, 1991. - S. Houliara and S. A. Karamanos, “Buckling and post-buckling of long pressurized elastic thin-walled tubes under in-plane bending,”
*International Journal of Non-Linear Mechanics*, vol. 41, no. 4, pp. 491–511, 2006. View at: Publisher Site | Google Scholar - Y. Zhu, X. Y. Luo, and R. W. Ogden, “Asymmetric bifurcations of thick-walled circular cylindrical elastic tubes under axial loading and external pressure,”
*International Journal of Solids and Structures*, vol. 45, no. 11-12, pp. 3410–3429, 2008. View at: Publisher Site | Google Scholar | Zentralblatt MATH - A. Goriely, R. Vandiver, and M. Destrade, “Nonlinear Euler buckling,”
*Proceedings of the Royal Society A: Mathematical, Physical & Engineering Sciences*, vol. 464, no. 2099, pp. 3003–3019, 2008. View at: Publisher Site | Google Scholar | MathSciNet - Y. Zhu, X. Y. Luo, and R. W. Ogden, “Nonlinear axisymmetric deformations of an elastic tube under external pressure,”
*European Journal of Mechanics—A/Solids*, vol. 29, no. 2, pp. 216–229, 2010. View at: Publisher Site | Google Scholar | MathSciNet - P. A. Djondjorov, V. M. Vassilev, and I. M. Mladenov, “Analytic description and explicit parametrisation of the equilibrium shapes of elastic rings and tubes under uniform hydrostatic pressure,”
*International Journal of Mechanical Sciences*, vol. 53, no. 5, pp. 355–364, 2011. View at: Publisher Site | Google Scholar - S. K. Kourkoulis, C. F. Markides, and E. D. Pasiou, “A combined analytic and experimental study of the displacement field in a circular ring,”
*Meccanica*, vol. 50, no. 2, pp. 493–515, 2015. View at: Publisher Site | Google Scholar - R. von Mises, “Der kritische Aubendruck zulindrischer rohre,”
*VDI Zeitschrift*, vol. 58, pp. 750–755, 1914. View at: Google Scholar - A. E. H. Love,
*The Mathematical Theory of Elasticity*, Cambridge University Press, London, UK, 1927. - R. Levien, “The elastica: a mathematical history,” Tech. Rep., EECS Department, University of California, Berkeley, Calif, USA, 2008. View at: Google Scholar
- M. Abramovitz and I. A. Stegun,
*Handbook of Mathematical Functions*, US Government Printing Office, Washington, DC, USA, 1972. - B. D. Gupta,
*Mathematical Physics*, Vikas Publishing House, New Delhi, India, 2002. - S. Ramanujan, “Modular equations and approximations to $\pi $,”
*The Quarterly Journal of Pure and Applied Mathematics*, vol. 45, no. 1, pp. 350–372, 1914. View at: Google Scholar - F. Liu and A. Treibergs, “On the compression of elastic tubes,” Tech. Rep., 2011, http://www.math.utah.edu/~treiberg/LT2006.pdf. View at: Google Scholar
- D. Manica, “Realisation, calibration and implementation of a laser scan for object reconstruction,” Tech. Rep., Grenoble Universities, Grenoble, France, 2013. View at: Google Scholar
- G. Popovici, “Modeling of deformed tube geometries from reconstructed and measured data,” Tech. Rep., Grenoble Universities, Grenoble, France, 2014. View at: Google Scholar

#### Copyright

Copyright © 2015 A. Van Hirtum. This is an open access article distributed under the Creative Commons Attribution License, which permits unrestricted use, distribution, and reproduction in any medium, provided the original work is properly cited.