Influence of friction on buckling of a drill string in the circular channel of a bore hole
Abstract
Enhancement of technology and techniques for drilling deep directed oil and gas bore hole is one of the most important problems of the current petroleum industry. Not infrequently, the drilling of these bore holes is attended by occurrence of extraordinary situations associated with technical accidents. Among these is the Eulerian loss of stability of a drill string in the channel of a curvilinear bore hole. Methods of computer simulation should play a dominant role in prediction of these states. In this paper, a new statement of the problem of critical buckling of the drill strings in 3D curvilinear bore holes is proposed. It is based on combined use of the theory of curvilinear elastic rods, Eulerian theory of stability, theory of channel surfaces, and methods of classical mechanics of systems with nonlinear constraints. It is noted that the stated problem is singularly perturbed and its solutions have the shapes of localized harmonic wavelets. The calculation results showed that the friction effects lead to essential redistribution of internal axial forces, as well as changing the eigenmode shapes and sites of their localization. These features make the buckling phenomena less predictable and raise the role of computer simulation of these effects.
Keywords
Directed bore hole Drill string Critical states Singular perturbation Friction forces Harmonic wavelet1 Introduction
Not long ago, rather shallow wells with simple outlines were drilled in oil and gas fields. However, at the present time, deeper and more complicated trajectories of bore holes are designed in connection with exhaustion of easily accessible hydrocarbon sources. In 2015, the record 13.5 km horizontal bore hole was drilled in the Sakhalin region, Russia. According to experts’ opinions, most of the substantial achievements in the power engineering of the current century are associated with this technical direction. Particularly, some are related to the pioneering investigation of industrial extraction of shale oil and gas, whose deposits in the world essentially exceed conventional reserves. However, as a rule, drilling of such bore holes is attended by extraordinary phenomena bringing emergency situations. One of them is unstable bending buckling of a drill string (DS) in the channel of a curvilinear bore hole (Brett et al. 1989; Dawson and Paslay 1984; Kyllingstad 1995; Sawaryn et al. 2006; Gulyayev et al. 2009; Gao and Liu 2013; Huang and Gao 2014; Gao and Huang 2015). This effect is associated with deterioration of conditions of contact interaction between the DS and the bore hole wall, enlargement of friction forces, impossibility of transferring the required axial force to the bit, and the DS lockup situation. To predict these effects and exclude them in practice, computer simulation should be employed.
In parallel with the static phenomena of buckling of the DSs, there also can occur very complicated nonlinear dynamic processes accompanied by extraordinary stable and unstable changes of the DS rotation. Among them there are axial, torsional, bending, and whirl vibrations, inevitably linked with deterioration of the drilling efficiency (Liu et al. 2013, 2014a, b).
The effects of loss of equilibrium stability in these mechanical systems are manifestations of one of the most general law of nature—the law of quantitative changes transferring to qualitative ones. In different spheres of reality, these changes are realized by different ways. In mechanics, they are studied on the basis of bifurcation theory.
The problem of mechanical instability and bifurcational buckling acquires crucial urgency in the technology of long curvilinear bore hole drilling because it is specified by essential complications but is not yet understood. Current experience testifies that no well is drilled without problems. They are connected with the complexity of mechanical phenomena accompanying the drilling process and the absence of dependable methods of computer modeling providing the possibility to predict emergency situations and to exclude them in advance. In a vertical bore hole, the DS stability loss occurs at its lower part following the spiral buckling mode typical for a rod stretched, compressed, and twisted simultaneously (Lubinski et al. 1962; Gulyayev et al. 2009).
However, the problem of theoretic simulation of DS buckling in the channel of a curvilinear bore hole acquires supplementary difficulties associated with the necessity of integrating differential equations with variable coefficients in the full range of the large length of the DS. Besides, the problem possesses essential complications stemming from appearance of additional constraints, imposed on the DS by the well wall surface, and application of contact and friction distributed forces, as well as change of orientation of gravity forces compressing the DS to the well wall (Dawson and Paslay 1984; Wang and Yuan 2012; Gulyayev et al. 2014).
Comprehensive reviews of results achieved in this direction are presented in the literature (Cunha 2004; Mitchell 2008; Gao and Huang 2015). It stems from these analyses that, as a rule, the approaches used in bifurcational analysis are based on the eigenmode approximations by regular sinusoids and spirals, while the critical values of loads and buckling shapes are rather guessed. As Cunha notes apparently this circumstance is the reason of conclusions that solutions of the problem on stability loss of the DSs in curvilinear bore holes gained by different authors are in contradiction with each other and reality (Cunha 2004).
What is the critical buckling load in curved, 3D bore holes?
What effect does friction play in DS buckling?
The last achievements in this domain are discussed by Gao and Huang (2015).
Gulyayev et al. (2014, 2015) elaborated a new mathematic model of a DS stability loss in smooth curvilinear channels. Without taking into consideration friction effects, they showed that the stated problem was singularly perturbed and so, typically, the modes of buckling were represented by boundary and localized effects in the shapes of wave packages or wavelets.
In this problem, fundamental unresolved questions remain: What role is played by the friction factor in stability loss phenomena and how to include it in the analytical or numerical model. Mitchell remarks: “Perhaps the most important force, and the force least studied in the analysis of buckling, is friction” (Mitchell 2008). The magnitude of the friction force is usually not that difficult to determine. The difficulty is determining the direction of the friction vector. We agree that this vector cannot be determined for stationary elastic systems with friction contacts because this problem is statically indeterminable (Mitchell and Samuel 2009). But if one of the contacting bodies slides on the surface of another, then the vectors of sliding velocity and friction force are collinear and the last one can be easily determined. This peculiarity facilitates the problem on the analysis of friction effects on critical buckling of the DS.
In the first place, it is necessary to point out that every balanced stationary state of the DS is preceded by its steady sliding motion associated with tripping in or out operation and drilling is accompanied by kinematic friction. As a rule, the coefficients of kinematic friction exceed their magnitudes established in static equilibrium. Besides, usually, the indicated technological procedures happen with certain ultimate longitudinal velocities, while the DS buckling occurs with very small velocities. In this case, the lateral buckling velocities (and the appropriate lateral friction forces) can be assumed to equal zero. Then, all the friction forces are axial and are oriented in one direction. Then, the moving DS experiences action of the more intensive friction forces which have deleterious effects upon the stability of its quasi-static equilibrium. Therefore, at this state, the bifurcational buckling of the DS should first of all be analyzed.
Secondly, the friction forces acting on the DS and all the functions of its total stress–strain state can be specified by rather simple calculation means.
Thirdly, with the use of these functions, the constitutive linearized homogeneous equations of critical equilibrium of the DS can be constructed. Their eigenvalues and eigenmodes determine critical loads on the DS in the bore hole channel and shapes of its bifurcational buckling.
To realize this approach, the nonlinear theory of elastic curvilinear rods is used. Its foundations are stated in monographs (Antman 2005; Gulyayev et al. 1992). A three-dimensional statement of this theory is expounded by Gulyayev and Tolbatov (2004). Its application to analysis of the DSs buckling in inclined rectilinear bore holes is described by Gulyayev et al. (2014). Below, it is formulated in a concomitant reference frame moving on the bore hole surface constraining the DS transformation. Owing to this, the total order of the differential equation is reduced to four. A two-step algorithm is proposed. At the first step, the stress–strain state of the moving DS under action of gravity and friction forces is determined; at the second step, the eigenvalue problem for linearized equations is solved. It is shown, that the buckling modes have the shapes of harmonic wavelets with localization segments depending on the friction forces.
2 Basic assumptions concerning drill string bending in a curvilinear bore hole
It is believed, also, that the DS element displacements can be comparable with the bore hole cross-sectional dimensions, but the curvature radii of its axis line L are so large that the DS strains are small and its stress–strain states are elastic. They are specified by the principal vectors of internal forces \({\mathbf{F}}(s)\) and internal moments \({\mathbf{M}}(s)\), where s is the natural parameter defined by the length of the DS axis line L measured from some initial point to the considered one.
Then, to describe the line L transforming, it is convenient to introduce additional right-hand reference frame oxyz with unit vectors \({\mathbf{i}}\), \({\mathbf{j}}\), \({\mathbf{k}}\), moving on the constraining surface Σ along the line L. In doing so, the unit vector \({\mathbf{i}}\) is the internal normal to the surface Σ and the vector \({\mathbf{k}}\) is tangent to the curve L.
Here, Δψ is the elementary angle of vector \({\mathbf{i}}\) rotation.
The gained relations (6), (9), (12) permit one to study elastic bending of the DS in a movable reference frame (5).
3 Nonlinear constitutive equations of the drill string bending in a curvilinear channel
Here, \(\tilde{\text{d}} \ldots /\text{d} s\) is the symbol of local derivative in the oxyz system.
Assuming that the generated friction forces (Eq. (18)) stopped the buckling process, then w_{y}(s) = 0 and the lateral forces \(f_{y}^{\text{fr}} \left( s \right) = 0\). However, the critical axial forces are exceeded (though slightly), the DS remains unstable, and again it begins to buckle, but this time, it selects very small velocity w_{y}(s) in Eq. (18), inducing very small lateral forces \(f_{y}^{\text{fr}} \left( s \right)\), which cannot stop the buckling process. Therefore, it is considered that if in the DS, sliding along its axial line in the bore hole channel, the internal axial forces F_{z}(s) exceed critical value \(F_{z}^{\text{cr}}\), the influence of induced lateral friction forces \(f_{y}^{\text{fr}} \left( s \right)\) on the buckling process can be neglected.
Therefore, the friction force is collinear with the vector \({\mathbf{k}}\) and its value constitutes (Mitchell and Samuel 2009) \(f_{z}^{\text{fr}} = \pm \mu \left| {f_{x}^{\text{cont}} } \right|\), where signs “+”, “−” are selected depending on the direction of DS movement.
Hence, M_{z} = const and its value can be calculated with the help of appropriate boundary conditions.
However, the most overwhelming obstacle associated with this problem consists of the necessity to simulate friction forces accompanying DS deformation. These forces are statically indeterminate for elastic systems. So, it is expedient to analyze particular cases of the DS movement inside curvilinear channels of simple trajectories and to study their stability. Of particular interest in this avenue of inquiry is incipient buckling of a DS in different segments of a plane circular channel because it adequately depicts the most general regularities of friction forces impact on the buckling phenomena.
4 Bifurcational equations of DS equilibrium in a circular bore hole
Let a DS be lowering in a plane circular bore hole. Then, it slides along the bore hole bottom line and its axis line is a circle of a radius ρ + a, where ρ is the radius of the bore hole axis T and a is the system clearance. In sliding, the DS is subjected to action of gravity (f^{gr}), contact (f^{cont}), and friction (f^{fr}) forces. In consequence of these forces, the DS can be compressed in some segments of its length where it can begin to buckle without losing its contact with the well wall. It is necessary to predict the critical states of the DS and to construct the modes of its stability loss.
This system with appropriate boundary conditions, determining external axial forces and torques, can be used for modeling nonlinear elastic bending of a DS in the circular channel cavity of a bore hole. Assuming that in the general case the DS can bend and take new deformed shapes remaining in contact with the bore hole wall throughout its length. If during this shape transformation small elastic displacements of the DS correspond to small increments of the external force perturbation, then the considered equilibrium state is stable. In the vicinity of this state, the linear differential equations deduced from the nonlinear system (33) with the use of linearization procedure are not degenerate and have only one solution. However, if the DS is loaded further, the coefficients of the linearized equations continue to evolve and the state can be reached when these equations become degenerate and acquire an additional (bifurcating) solution along with the initial one. Because of this, the state reached is critical (unstable) and the bifurcating solution represents the buckling mode.
The peculiarity of the nonlinear problem stated for the buckling of a DS in the circular channel is that the tube does not change its shape in the subcritical states and so the coefficients of the linearized equations of the equilibrium change owing to the step-by-step enlargement of the axial force F_{z}(s) with the external load increase. In that event, the stated problem is analogous to the problem of Eulerian stability of a rectilinear rod because it is also associated with the eigenvalue search and eigenmode construction.
It is derived from the assumption that in buckling the friction force f^{fr} is directed along the DS axis line. To find states of bifurcational buckling of the DS, the Sturm–Liouville problem (eigenvalue problem) should be formulated for Eq. (39). Its statement is based on the finite difference method and the construction of the corresponding matrix of algebraic equation coefficients. The matrix elements depend on multiplier F_{z}(s) before the δv value in Eq. (39) which in its turn is determined by the boundary force F_{z}(U) and the distributed friction force in Eq. (38). Then, the critical (bifurcational or eigen) value of the external force F_{z}(U) applied at the end u = U (i.e., s = S) is found by its varying through the trial-and-error method application.
It is notable that the torque M_{z} is not present in Eq. (39). This means that critical states of DSs in circular bore holes do not depend on M_{z} values (as well as in rectilinear ones (Gulyayev et al. 2014)).
5 Critical buckling of a DS moving inside a channel of a circular bore hole
The primary objective of this paper lies in investigation of the influence of friction forces on the stability of a DS moving inside a curvilinear bore hole. Notwithstanding the fact that the simplest trajectory in the shape of a circular arc is chosen for the bore hole configuration, this example permits us to trace the principal peculiarities of the buckling processes proceeding in curve channels. It consists in the possibility to generate localized buckling wavelets in the most unexpected places of the hole length. Additional uncertainty is contributed to this situation by axial friction forces generated during lowering or hoisting the DS. It is considered that the motion is slow, and inertia forces can be disregarded. Then, the DS can be partially compressed and partially stretched by distributed variable gravity forces f^{gr}(s), variable frictional forces f^{fr}(s), and axial force F_{z}(U) applied at the DS end s = S with an angular coordinate u = U. So, Eq. (39) cannot be solved by analytical methods.
To find bifurcational states of the DS, Eq. (39) was algebraized by the finite difference method for different values of F_{z}(U) force, and the states when the matrix of linear algebraic equations became degenerate were assumed to be critical. At this state, the eigenfunction F_{z}^{cr}(s) and eigenmode δv(s), representing the shape of the buckling DS, were constructed.
In numerical analyses, the DS section 0 ≤ s ≤ S was divided into 500 finite difference pieces. The calculation results were tested with a doubled number of pieces. The checking confirmed the adequate precision of the computations.
In order to trace the influence of friction forces on the DS buckling, every calculation example was examined with the use of frictionless and frictional statements. The analytic results are compared.
Functions of the critical axial force F_{z}^{cr}(s) and buckling modes δv(s) for the case S = 1200 m, ρ = 1146 m, \(\varphi = 60^{\text{o}}\)
No. | a, m | Friction force value | Function of the critical axial force F_{z}^{cr}(s), kN | Mode δv(s) of stability loss |
---|---|---|---|---|
1 | 0.5 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
2 | 0.1 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
3 | 0.05 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
4 | 0.03 | f^{fr} = 0 | ||
f^{fr} ≠ 0 |
The situations change if f^{fr} ≠ 0 (see position 1 in Table 1). Then, the maximal compressive value F_{z}^{fr} = −93.97 kN of the axial force shifts to the bore hole interiority and the system becomes singularly perturbed inside its length. Then, the buckling wavelet also displaces inside the DS segment.
If a ≤ 0.1 m (positions 2–4 in Table 1), the DSs buckle under the action of greater forces and the smaller a is, the more complicated is the mode of stability loss. It becomes also harder to predict the zone of the buckling localization in the presence of friction forces. Besides, the buckled zone propagates through a larger region of the DS length and at a = 0.03 m the boundary effect drifts from the right end of the diagram to its left end. As this takes place, the buckling mode pitch (λ—pitch of the eigenmode wavelet) becomes smaller and smaller. Thus, the wavelet pitch λ ≈ 26 m for a = 0.5 m and it is 10.5 m for a = 0.03 m.
Functions of the critical axial force F_{z}^{cr}(s) and buckling modes δv(s) for the case S = 2400 m, ρ = 1146 m, φ = 120^{∘}
No. | a, m | Friction force value | Function of the critical axial force F_{z}^{cr}(s), kN | Mode δv(s) of stability loss |
---|---|---|---|---|
1 | 0.5 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
2 | 0.1 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
3 | 0.05 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
4 | 0.03 | f^{fr} = 0 | ||
f^{fr} ≠ 0 |
The presence of friction effects leads to shifting the buckling wavelet positions in both cases (see Figs. 5b, 6b) but the maximal values of the appropriate critical functions F_{z}^{cr}(S) (located in the wavelets zones) and wavelet pitches remain approximately equal, though shapes of their buckling modes acquire some distinctions.
Functions of the critical axial force F_{z}^{cr}(s) and buckling modes δv(s) for the case S = 3600 m, ρ = 1146 m, ϕ = 180°
No. | a, m | Friction force value | Function of the critical axial force F_{z}^{cr}(s), kN | Mode δv(s) of stability loss |
---|---|---|---|---|
1 | 0.5 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
2 | 0.1 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
3 | 0.05 | f^{fr} = 0 | ||
f^{fr} ≠ 0 | ||||
4 | 0.03 | f^{fr} = 0 | ||
f^{fr} ≠ 0 |
Extreme values of axial force F_{z}^{cr}(s) and wavelet pitches λ at critical states of the DSs
No. | a, m | Friction force value | ϕ = 120°, S = 2400 m | ϕ = 180°, S = 3600 m | ||
---|---|---|---|---|---|---|
F_{z}^{ext}, kN | λ, m | F_{z}^{ext}, kN | λ, m | |||
1 | 0.5 | f^{fr} = 0 | −98.29 (−91.26) | 26 (26.65) | −98.18 (−91.26) | 26 (26.65) |
f^{fr} ≠ 0 | −94.11 | 26 | −96.95 | 23.5 | ||
2 | 0.1 | f^{fr} = 0 | −233.9 (−204.1) | 15.5 (17.8) | −233.7 (−204.1) | 15.5 (17.8) |
f^{fr} ≠ 0 | −222.3 | 15–15.5 | −225.9 | 13.6–14 | ||
3 | 0.05 | f^{fr} = 0 | −347.0 (−288.6) | 13 (14.9) | −346.5 (−288.6) | 12 (14.9) |
f^{fr} ≠ 0 | −332.8 | 11–12.5 | −335.9 | 9.5–10.5 | ||
4 | 0.03 | f^{fr} = 0 | −468.9 (−372.6) | 10.5 (13.1) | −469.2 (−372.6) | 9.3 (13.1) |
f^{fr} ≠ 0 | −446.5 | 10–10.5 | −456.1 | 8.6–9 |
The influence of the friction forces on buckling modes is more appreciable. They cause not only the diversification of the buckling zone positioning but lead to these zones widening as well (see Table 3). Besides, in the every zone limits, the pitches of conventional harmonics become also variable (see Table 4 for f^{fr} ≠ 0).
Their bracketed values for the corresponding states are tabulated in Table 4. It can be seen that the calculated results are closely related for large values of clearance a and the difference between them grows with a reduction in a.
Summarizing obtained results, one can recognize that the found regularities of the realization of critical states and critical modes evolving are associated, in a large extent, with the circular geometry of a bore hole and invariability of its curvature radius ρ. One might expect that the considered phenomena will be far more intricate for the wells with a variable curvature both in the cases of frictionless contacts and when the frictional interactions occur.
Noteworthy also is the remark in relation to the influence of the bore hole geometry imperfections on the buckling process. The geometry imperfections entail enlargement of distributed friction forces and axial force F_{z}(s), on the other hand, the geometry distortions result in a change of the curvature radius ρ. Both these factors imply the essential effect on the buckling process and should be specially studied.
6 Conclusions
- (1)
On the basis of the theory of curvilinear elastic rods, a new statement of the problem of critical buckling of DSs in 3D curvilinear bore holes with allowance made for friction effects is suggested. It is assumed that a DS does not lose its stability in the state of its stationary equilibrium but it can buckle during its axial movement when friction forces and their directions can be easily determined.
- (2)
The fourth order system of linearized differential equations of the DS buckling in a curvilinear channel is deduced with the use of differential geometry methods, theory of channel surfaces, and classical mechanics of systems with nonlinear constraints. The method of numerical solutions of this system is elaborated.
- (3)
The problem is shown to belong to the singularly perturbed class, and for this reason, the buckling modes have the shapes of localized harmonic wavelets.
- (4)
As an example, the phenomena of DS stability in circular channels are studied. The cases of absence and presence of friction effects are considered. It is demonstrated that the friction forces stimulate redistribution of internal axial forces in the DSs and result in essential shifting of the buckling wavelet localizations, bringing the buckling phenomenon to the less predictable type.
- (5)
One might suppose that the considered phenomena will be far more complicated for the well with variable curvatures both in the cases of frictionless contacts and when the frictional interactions take place.
References
- Antman SS. Nonlinear problems of elasticity. New York: Springer; 2005.Google Scholar
- Berger EJ. Friction modeling for dynamic system simulation. Appl Mech Rev. 2002;55(6):535–76. doi:10.1115/1.1501080.CrossRefGoogle Scholar
- Brett JF, Beckett AD, Holt CA, et al. Uses and limitations of drill string tension and torque models for monitoring hole conditions. SPE Drill Eng. 1989;4:223–9. doi:10.2118/16664-PA.CrossRefGoogle Scholar
- Chang KW, Howes FA. Nonlinear singular perturbation phenomena. Berlin: Springer; 1984.CrossRefGoogle Scholar
- Crawford FS. Waves. Berkeley physics course, vol. 3. Noida: Mc Graw-Hill; 2011.Google Scholar
- Cunha JC. Buckling of tubulars inside wellbores: a review on recent theoretical and experimental works. SPE Drill Complet. 2004;19(1):13–8. doi:10.2118/87895-PA.CrossRefGoogle Scholar
- Dawson R, Paslay RR. Drill pipe buckling in inclined holes. J Pet Technol. 1984;36(10):1734–8. doi:10.2118/11167-PA.CrossRefGoogle Scholar
- Dubrovin BA, Novikov SP, Fomenko AT. Modern geometry-methods and applications. Berlin: Springer; 1992.CrossRefGoogle Scholar
- Elishakoff I, Li Y, Starnes JH. Non-classical problems in the theory of elastic stability. Cambridge: Cambridge University Press; 2001.CrossRefGoogle Scholar
- Gao DL, Huang WJ. A review of down-hole tubular string buckling in well engineering. Pet Sci. 2015;12(3):443–57. doi:10.1007/s12182-015-0031-z.CrossRefGoogle Scholar
- Gao DL, Liu FW. The post-buckling behavior of a tubular string in an inclined wellbore. Comput Model Eng Sci. 2013;90(1):17–36. doi:10.3970/cmes.2013.090.017.Google Scholar
- Gulyayev VI, Andrusenko EN, Shlyun NV. Theoretical modelling of post-buckling contact interaction of a drill string with inclined bore-hole surface. Struct Eng Mech. 2014;49(4):427–48. doi:10.12989/sem.2014.49.4.427.CrossRefGoogle Scholar
- Gulyayev VI, Gaidaichuk VV, Andrusenko EN, et al. Critical buckling of drill strings in curvilinear channels of directed bore-holes. J Pet Sci Eng. 2015;129:168–77. doi:10.1016/j.petrol.2015.03.004.CrossRefGoogle Scholar
- Gulyayev VI, Gaidaichuk VV, Koshkin VL. Elastic deforming, stability and vibrations of flexible curvilinear rods. Kiev: Naukova Dumka; 1992 (in Russian).Google Scholar
- Gulyayev VI, Gaidaichuk VV, Solovjov IL, et al. The buckling of elongated rotating drill strings. J Petr Sci Eng. 2009;67:140–8. doi:10.1016/j.petrol.2009.05.011.CrossRefGoogle Scholar
- Gulyayev VI, Tolbatov EYU. Dynamics of spiral tubes containing internal moving masses of boiling liquid. J Sound Vib. 2004;274:233–48. doi:10.1016/j.jsv.2003.05.013.CrossRefGoogle Scholar
- Huang WJ, Gao DL. Helical buckling of a thin rod with connectors constrained in a cylinder. Int J Mech Sci. 2014;84:189–98. doi:10.1016/j.ijmecsci.2014.04.022.CrossRefGoogle Scholar
- Kyllingstad A. Buckling of tubular strings in curved wells. J Pet Sci Eng. 1995;12(3):209–18. doi:10.1016/0920-4105(94)00046-7.CrossRefGoogle Scholar
- Liu X, Vlajic N, Long X, et al. Nonlinear motions of a flexible rotor with a drill bit: stick-slip and delay effects. Nonlinear Dyn. 2013;72:61–77. doi:10.1007/s11071-012-0690-x.CrossRefGoogle Scholar
- Liu X, Vlajic N, Long X, et al. Multiple regenerative effects in cutting process and nonlinear oscillations. Int J Dyn Control. 2014a;2:86–101. doi:10.1007/s40435-014-0078-5.CrossRefGoogle Scholar
- Liu X, Vlajic N, Long X, et al. Coupled axial-torsional dynamics in rotary drilling state-dependent delay: stability and control. Nonlinear Dyn. 2014b;78(3):1891–906. doi:10.1007/s11071-014-1567-y.CrossRefGoogle Scholar
- Lubinski A, Althouse WS, Logan JL. Helical buckling of tubing sealed in packers. JPT. 1962;14(6):655–70. doi:10.2118/178-PA.CrossRefGoogle Scholar
- Mitchell RF. Tubing buckling—the state of the art. SPE Drill Complet. 2008. doi:10.2118/104267-PA.Google Scholar
- Mitchell RF, Samuel R. How good is the torque/drag model? SPE Drill Complet. 2009;24(1):62–71. doi:10.2118/105068-PA.CrossRefGoogle Scholar
- Samuel R. Friction factors: what are they for torque, drag, vibration, bottom hole assembly, and transient surge/swab analysis. J Pet Sci Eng. 2010;73(3–4):258–66. doi:10.1016/j.petrol.2010.07.007.CrossRefGoogle Scholar
- Sawaryn SJ, Sanstrom B, McColpin G. The management of drilling-engineering and well-services software as safety-critical systems. SPE Drill Complet. 2006;21(2):141–7. doi:10.2118/73893-PA.CrossRefGoogle Scholar
- Wang X, Yuan Z. Investigation of frictional effects on the nonlinear buckling behavior of a circular rod laterally constrained in a horizontal rigid cylinder. J Pet Sci Eng. 2012;90–91:70–8. doi:10.1016/j.petrol.2012.04.011.CrossRefGoogle Scholar
Copyright information
Open AccessThis article is distributed under the terms of the Creative Commons Attribution 4.0 International License (http://creativecommons.org/licenses/by/4.0/), which permits unrestricted use, distribution, and reproduction in any medium, provided you give appropriate credit to the original author(s) and the source, provide a link to the Creative Commons license, and indicate if changes were made.