SN Applied Sciences

, 1:126

# Computer simulation of dragging with rotation of a drill string in 3D inclined tortuous bore-hole

• Valery Gulyayev
• Elena Andrusenko
• Sergey Glazunov
Research Article
Part of the following topical collections:
1. Engineering: New Technologies in Mechanical Engineering, Robotics, and Intelligent Transport Systems

## Abstract

This paper deals with the problem on determination of resistance forces impeding a drill string dragging in a deep curvilinear bore-hole channel. The bore-hole axis geometry is considered to be prescribed discretely at its separate points with the use of the results of geophysical measurements (bore-hole navigation). A “3D stiff-string differential model” for simulation of the drag/torque phenomena accompanying hoisting, lowering and drilling operations is proposed. The system of ordinary differential equations is derived based on the theory of curvilinear flexible elastic rods. The transfer from the tabular to analytic description of the bore-hole trajectory geometry is performed with the application of the cubic spline interpolation. The elaborated approach can be used for simulation of the drill string dragging with rotation, its contact and frictional interaction with the bore-hole surface and prognostication of the string lock up situations. Numerical examples are presented to illustrate the proposed techniques advantages.

## Keywords

Curvilinear drilling Drill string raising Contact forces Resistance forces

## List of symbols

$$a$$

DS sliding velocity

$$a_{k}$$, $$b_{k}$$, $$c_{k}$$, $$d_{k}$$

Interpolation coefficients

$$D$$

Metric multiplier

DS

Drill string

$$E$$

Elasticity module

$${\mathbf{f}}(s)$$

Vector of external distributed forces

$${\mathbf{f}}^{gr} ,\;{\mathbf{f}}^{cont} ,\;{\mathbf{f}}^{fr}$$

Vectors of distributed external forces of gravity, contact and friction

$$f(x_{i} )$$

Values of $$y(x)$$ function at $$x_{i}$$ points

$${\mathbf{F}}(s)$$

Principal vector of internal elastic forces

$$F(x_{i} )$$

Interpolated function

$$F_{n}$$, $$F_{b}$$, $$F_{t}$$

Appropriate components of the $${\mathbf{F}}$$ force

$$h$$

Depth of the bore-hole

$${\mathbf{i}},\;{\mathbf{j}},\;{\mathbf{k}}$$

Unit vectors of the Cartesian coordinate system

$$I$$

Inertia moment of the DS tube

$$k(s)$$

Natural parametrization of the bore-hole curvature

$$k(\vartheta )$$

Dimensionless parametrization of the bore-hole curvature

$$k_{R}$$

Main curvature of a spatial curve

$$k_{T}$$

Torsion of a spatial curve

$$l$$

Horizontal distance

$${\mathbf{m}}(s)$$

Vector of distributed external moment

$${\mathbf{M}}(s)$$

Principal vector of internal elastic moments

$$M_{n}$$, $$M_{b}$$, $$M_{t}$$

Appropriate components of the $${\mathbf{M}}$$ moment

$${\mathbf{n}},\;{\mathbf{b}},\;{\mathbf{t}}$$

Unit vectors of the Frenet trihedron

$$N$$

Number of interpolation points

$$Oxyz$$

Cartesian coordinate system

$$P_{n} (x)$$

Interpolating polynomial

$$r$$

External radius of the DS tube

$${\mathbf{r}}_{0}$$

Radius-vector of the bore-hole curve points

$$r_{1}$$, $$r_{2}$$

External and internal radii of the DS tube

$$s$$

Natural parameter of the bore-hole curve

$$S$$

Bore-hole trajectory length

$$t_{z}$$

Appropriate component of the $${\mathbf{t}}$$ vector

$$x_{i}$$

Discrete values of independent variable

$$y_{i}$$

Discrete values of the interpolated function

$$x_{0}$$, $$y_{0}$$, $$z_{0}$$

Planned coordinates of the bore-hole trajectory

$$\gamma$$

Linear weight of the DS tube

$$\delta$$

Symbol of small variation

$$\Delta$$

Symbol of small increment

$$\varepsilon$$

Eccentricity of the hyperbola

$$\vartheta$$

Dimentional parameter of the bore-hole curve

$$\mu$$

Friction coefficient

$$\nu$$

Ratio of the axial and circumferential velocities of the DS tube

$$\varphi_{k} (x_{k} )$$

Interpolating functions

$$\omega$$

Angular velocity of the DS rotation

$${\varvec{\Omega}}$$

Darboux vector

## 1 Introduction

One of the most important factors, impeding drilling the hyper deep and extensional bore-holes with curvilinear trajectories, is specified by the resistive (frictional) forces. In their generating, the great role is played by the bending stiffness of a drill string (DS), bore-hole tortuosity and its length, as well as by the type of the technological operation [3, 19]. These forces hamper permeability of the force on bit and torque on bit, provoke buckling of the drill string [6, 10] and can result in dead lock situations.

To predict and eliminate these effects, the mathematic models and software should be elaborated for simulation of the drilling processes in long 3D tortuous bores.

Appearance of these emergency situations is principally caused by three factors. First of all, this is the large length of the DSs. Under conditions of the geometric similarity, they are equivalent to a human hair. Therefore, the phenomena, occurring at one end of a DS, can influence, poorly influence and do not influence on the effects, taking place at its other end. In mathematics, the equations, describing such effects, are named singularly perturbed. They are characterized by poorly converging solutions with the modes, possessing singularities in the shapes of boundary effects or internal irregularities.

The second factor is connected with the special character of frictional effects, showing themselves in tortuous curvilinear bore-holes. The matter is that in them, the friction force depends on the pressure force between the contacting bodies. But in the curvilinear pieces of the trajectory, the pressure force is determined by the axial force of the DS tension and the bore curvature. In this case, it is said in mechanics that the friction forces have a multiplicative (i.e., they are multiplied) but not additive (they are not added) nature, as it occurs in sliding of one body on the shaggy plane surface of another one [19].

Finally, the third factor is associated with the fact that the problems on mathematic simulation of mechanical phenomena, attending the drilling processes, are multiparametric, as they depend on large number of geometric and mechanic values. Therefore, the questions become very important which are associated with analysis of these phenomena under specific particular values of the constitutive parameters and establishment of general regularities of the proceeding processes. Some additional detrimental effects are generated by dynamic phenomena [18, 23].

Because of this, the drilling technology for inclined and horizontal bore-holes is featured by its complexity and is not completely mature. The world statistics indicates that the accident rate is 1 in 3 for driving bore-holes of this type [16]. It is associated to a large extent with the complexity of mechanical and physical phenomena accompanying the drilling process and the lack of reliable methods of computer simulation that enables us to predict the emergency situations and to prevent them beforehand.

The efforts to simulate the inclined drill problems with the use of computer models present considerable difficulties determined by a number of factors [5, 11, 12, 14, 15, 17]. Among them the relatively complex geometry of the drill string is the main concern. Being founded on the geometrical similarity, the drill columns can be compared to a very flexible rod with negligible bending stiffness. Early, this circumstance permitted to simulate the internal and external forces acting on them with the use of simplified mathematical models based on the theory of absolutely flexible threads [1, 2, 21]. Analysis of these forces was performed only on the basis of investigations of geometrical peculiarities of the bore-hole axis line without considering the contribution of elastic forces and contact effects generated during raising–lowering operations and rotation of the drill string. With the use of this approach, a number of researches on the designs of bore-holes with the simplest outlines have been presented [1, 20, 21].

In papers [4, 22], a more general approach called the minimum curvature method has been adopted, by considering the well axis outline as a smooth curve made up of segments of straight lines and circular or catenary curves. By this approach, explicit analytical equations were derived to model the drill string (thread) with tension and friction forces for tripping in and out operations. In addition, explicit expressions were developed for the drill column to include the effects of drag and torque under the combined axial motion and rotation. Using the equalities, the total drag and torque were derived as the sum of their separate contributions from each section of the hole. Different algorithms and software programs were presented. Several examples were prepared to demonstrate the use of the analytical models. It was shown that any change of direction in the well path contributed to increased friction.

The conclusion achieved based on assumption of well trajectory smoothness and negligible bending stiffness of the drill string tube may underline the weakness of the theory used. In practice, the axial trajectories of bore-holes cannot be represented as lines with smooth geometry because of the geometrical imperfections involved in drilling. They can be caused by distortions of the bit geometry, dynamic imbalance of the bottom-hole-assembly, and physical non-homogeneities of the drilled rock medium. These factors impact on mobility of the drill string inside that sort of bore-holes and can be investigated only with the use of 3D stiff string drag and toque models elaborated on the basis of the theory of curvilinear flexible rods and methods of differential geometry. The model of that kind and software were elaborated by [7, 8]. Through their application, different examples of bore-holes with localized spiral, harmonic, and irregular (dog leg) imperfections described by analytic correlations were considered. It was demonstrated that additional short-pitched tortuosities led to essential enlargement of contact and resistance forces, provoking decrease of the dill string mobility and appearance of dead lock states.

Yet, in practice, the situation is much more complicated. The point is that the imperfections incorporated into the bore-hole geometry during drilling are not well-ordered and cannot be represented by analytic correlations. They are established by means of geophysical measurements performed at separate points with certain step throughout the bore-hole axis line length and can be rendered only in a tabular (discrete) form.

Therefore, if to take into account that the effects of the DS bending can be described only with the use of differential equations based on the continuity hypotheses, it becomes evident that the geometry of the planned or drilled bore-holes must be restructured to the analytical form.

Considered below is the problem of computer simulation of a drill string dragging with rotation in the channel of a curvilinear tortuous bore-hole with the centerline prescribed in a tabular form. To create the analytical mathematic model of the DS dragging with allowance made for the resistance (gravity, contact, and friction) forces, the transfer from the discrete description of the bore-hole axis to its continuous (differentiable) presentation was performed. It was done via utilization of methods of spline interpolation, differential geometry, mechanics of structures, and methods of numerical integration. This smoothing of the trajectory geometry enabled us for the first time to create a universal 3D stiff string drag and torque model based on application of a spatial theory of elastic curvilinear flexible rods. With its application, the constitutive differential equations were deduced. They can be used for prognostication of resistance forces and exclusion of emergency (sticking) situations at the stages of the bore-hole design and drivage. The results of the performed computer analysis confirmed efficiency of the proposed approach.

## 2 Analytic presentation of the bore-hole axis line geometry

In the applied mathematics the interpolation procedure is associated with construction of an interpolating function, passing through the prescribed points of tabular data [13]. This procedure essence consists in prescription of a set of points $$x_{i}$$ ($$1 \le i \le N$$) from some domain and assumption that the values of some desired function $$f$$ are known only at these points
$$f(x_{i} ) = y_{i} \quad (1 \le i \le N).$$
(1)
The interpolation task consists in selection of some interpolating $$F(x)$$ function, which satisfies conditions
$$F(x_{i} ) = y_{i} \quad \left( {1 \le i \le N} \right)$$
(2)
and can be used instead of the sought—for function $$f(x)$$.
In practice, usually a polynomial interpolation is used as it is easy to calculate derivatives of these functions with the help of analytical approaches. In this case, interpolating function $$F(x)$$ is constructed as a linear combination of some polynomials
$$F(x) = \sum\limits_{k = 1}^{N} {a_{k} \;\varphi_{k} (x)} ,$$
(3)
where $$\varphi_{k} (x)$$ are some specified functions; $$a_{k}$$ are the unknown coefficients.
It issues from this equality that interpolating function $$F(x)$$ should coincide with the desired $$f(x)$$ function at some points $$x_{i}$$. These conditions are reduced to system
$$\sum\limits_{k = 1}^{N} {a_{k} \;\varphi_{k} (x_{i} )} = f(x_{i} ) = y_{i} \quad \left( {1 \le i \le N} \right).$$
(4)
But this approach has one essential disadvantage because the matrix of coefficients $$\varphi_{k} (x_{i} )$$ in Eq. (4) is poorly conditioned and, as a rule, solutions of system (4) have significant miscalculations. In this connection, the spline interpolations are of great utility in applied mathematics. Unlike the polynomial approximation, the spline interpolation is constructed separately in every segment [$$x_{k - 1}$$, $$x_{k}$$], satisfying certain conditions of smoothness at node points $$x_{k}$$. In computing mathematics, the most commonly encountered splines are cubic ones, which can be described by expression
$$P_{k} (x) = a_{k} + b_{k} (x - x_{k} ) + \frac{{c_{k} }}{2}(x - x_{k} )^{2} + \frac{{d_{k} }}{6}(x - x_{k} )^{3} .$$
(5)
here coefficients $$a_{k}$$, $$b_{k}$$, $$c_{k}$$, $$d_{k}$$ are found from the conditions of continuity of function $$P(x)$$ and its first and second derivatives.
The noted properties of the cubic splines render them convenient for interpolation of the tabular data on the curvilinear bore-hole axis geometry, because in this event, its curvature described by equalities [13]
$$k(s) = \sqrt {(x^{\prime \prime } )^{2} + (y^{\prime \prime } )^{2} + (z^{\prime \prime } )^{2} } \quad {\text{or}}\quad k(\vartheta ) = \sqrt {\frac{{(\dot{x}^{2} + \dot{y}^{2} + \dot{z}^{2} )(\ddot{x}^{2} + \ddot{y}^{2} + \ddot{z}^{2} ) - (\dot{x}\ddot{x} + \dot{y}\ddot{y} + \dot{z}\ddot{z})^{2} }}{{(\dot{x}^{2} + \dot{y}^{2} + \dot{z}^{2} )^{3} }}}$$
(6)
is also continuous.

Here, $$x(s)$$, $$x(\vartheta )$$, $$y(s)$$, $$y(\vartheta )$$,$$z(s)$$, $$z(\vartheta )$$ are the axis line coordinates; $$s$$ is the natural parameter measured by the length of the axis line from some initial point till the current one; $$\vartheta$$ is the dimensionless parameter; the symbol prime designates the derivative with respect to $$s$$; the dot denotes the differentiation operation relative to $$\vartheta$$.

As the right parts of Eqs. (6) contain only the first and second derivatives (which are continuous), curvatures $$k(s)$$ or $$k(\vartheta )$$ are also continuous.

### 2.1 3D stiff string drag and torque model of the drill string axial motion with rotation

Assume that a drill string performs axial motion with rotation inside a bore-hole cavity with curvilinear axial line. Its planned axis line is described by equation
$${\mathbf{r}}_{0} = {\mathbf{r}}_{0} (s) = x_{0} {\mathbf{i}} + y_{0} {\mathbf{j}} + z_{0} {\mathbf{k}},$$
(7)
where $${\mathbf{i}},\;{\mathbf{j}},\;{\mathbf{k}}$$ are the unit vectors of the Cartesian coordinate system $$Oxyz$$.

During the drilling process, the table of real values $$x(S_{i} ) = x_{0} (S_{i} ) + \delta \,x(S_{i} )$$, $$y(S_{i} ) = y_{0} (S_{i} ) + \delta \,y(S_{i} )$$, $$z(S_{i} ) = z_{0} (S_{i} ) + \delta \,z(S_{i} )$$ of the real drilled bore-hole trajectory points is formed through the use of geonavigation measurements. They are converted to analytic relations $$x_{i} = x_{i} (s)$$, $$y_{i} = y_{i} (s)$$, $$z_{i} = z_{i} (s)$$ by interpolation with the cubic splines help within the limits of every segment $$\Delta \;S_{i} = S_{i + 1} - S_{i} = {S \mathord{\left/ {\vphantom {S {(N - 1)}}} \right. \kern-0pt} {(N - 1)}}$$ throughout the bore-hole length $$0 \le s \le S$$.

Assume that axis lines of the bore-hole and drill string coincide. There is a need to deduce the differential equations of quasi static equilibrium of the drill sting in its axial motion with rotation and to calculate internal forces and moments, as well as distributed external contact and friction forces, hindering its motion.

This problem has a distinctive feature associated with the consideration about coincidence of axial lines of the DS and bore-hole. Then, some of the components of the internal forces can be expressed immediately through the DS stiffness and the bore-hole geometry parameters. In mechanics of structures, the similar problems are known as inverse ones. Yet, at the same time, the internal axial force $$F_{t} (s)$$ and torque $$M_{t} (s)$$ in the DS are unknown and they should be calculated. Therefore, the considered problem is partially inverse and partially direct.

To deduce the constitutive equations of elastic deforming a curvilinear rod, a concomitant reference frame moving along its axial line with parameter $$s$$ change should be introduced. Study of these equations is most convenient with the use of the Frenet natural trihedron with unit vectors of the principal normal $${\mathbf{n}}$$, binormal $${\mathbf{b}}$$, and tangent $${\mathbf{t}}$$.

At any cross-section of the DS, the principal vectors of internal forces $${\mathbf{F}}(s)$$ and moments $${\mathbf{M}}(s)$$ and the vectors of distributed external forces $${\mathbf{f}}(s)$$ and moments $${\mathbf{m}}(s)$$ satisfy the following equilibrium equations [9]
$$\frac{{d{\mathbf{F}}}}{ds} = - \,{\mathbf{f}},\quad \frac{{d{\kern 1pt} {\mathbf{M}}}}{ds} = - \,{\mathbf{t}} \times {\mathbf{F}} - {\mathbf{m}}.$$
(8)
Since the Frenet reference frame rotates with its moving along the DS axis, the total derivatives $${{d{\kern 1pt} {\mathbf{F}}} \mathord{\left/ {\vphantom {{d{\kern 1pt} {\mathbf{F}}} {ds}}} \right. \kern-0pt} {ds}}$$, $${{d{\kern 1pt} {\mathbf{M}}} \mathord{\left/ {\vphantom {{d{\kern 1pt} {\mathbf{M}}} {ds}}} \right. \kern-0pt} {ds}}$$ should be expressed in the following form
$$\frac{{d{\mathbf{F}}}}{ds} = \frac{{\tilde{d}{\mathbf{F}}}}{ds} + {\varvec{\Omega}} \times {\mathbf{F}},\quad \frac{{d{\kern 1pt} {\mathbf{M}}}}{ds} = \frac{{\tilde{d}{\mathbf{M}}}}{ds} + {\varvec{\Omega}} \times {\mathbf{M}}.$$
(9)
here $$\tilde{d} \ldots /ds$$ is the local derivative; $${\varvec{\Omega}}$$ is the Darboux vector, determined through the expression
$${\varvec{\Omega}} = k_{R} {\mathbf{b}} + k_{T} {\mathbf{t}}.$$
(10)
With allowance made for Eq. (10), one can represent Eq. (8) as follows:
$$\frac{{\tilde{d}{\mathbf{F}}}}{ds} = - \,{\varvec{\Omega}} \times {\mathbf{F}} - {\mathbf{f}},\quad \frac{{\tilde{d}{\mathbf{M}}}}{ds} = - \,{\varvec{\Omega}} \times {\mathbf{M}} - {\mathbf{t}} \times {\mathbf{F}} - {\mathbf{m}}.$$
(11)
Consider that the process of the DS dragging inside the bore-hole channel is operated with constant axial velocity $$a$$ and rotation velocity $$\omega$$. Then, the external distributed forces $${\mathbf{f}}(s)$$ and moments $${\mathbf{m}}(s)$$ can be represented by the equalities
$${\mathbf{f}} = {\mathbf{f}}^{gr} + {\mathbf{f}}^{cont} + {\mathbf{f}}^{fr} ,\quad {\mathbf{m}} = {\mathbf{m}}^{fr} = {\mathbf{m}}_{\tau }^{fr} {\mathbf{t}}.$$
(12)
here fgr is the gravity, fcont is the force of contact interaction between the surfaces of the DS and bore-hole, ffr is the force of friction interaction between these surfaces, mfr is the distributed moment of friction forces.
It is convenient to represent the vector force values at the $${\mathbf{n}},\;{\mathbf{b}},\;{\mathbf{t}}$$ basis
\begin{aligned} {\mathbf{F}} & = F_{n} {\mathbf{n}} + F_{b} {\mathbf{b}} + F_{t} {\mathbf{t}},\quad {\mathbf{M}} = M_{b} {\mathbf{b}} + M_{t} {\mathbf{t}}, \\ {\mathbf{f}}^{gr} & = - \gamma n_{z} {\mathbf{n}} - \gamma b_{z} {\mathbf{b}} - \gamma t_{z} {\mathbf{t}},\quad {\mathbf{f}}^{cont} = f_{n}^{cont} {\mathbf{n}} + f_{n}^{cont} {\mathbf{b}} \\ {\mathbf{f}}^{fr} & = \pm \mu \sqrt {\left( {f_{n}^{cont} } \right)^{2} + \left( {f_{b}^{cont} } \right)^{2} } {\mathbf{t}}, \\ \end{aligned}
(13)
where bending moment $$M_{b}$$ is
$$M_{b} = EIk_{R} .$$
(14)
here $$\gamma$$ is the linear weight of the DS tube calculated with allowance made for the buoyancy effect of the mud, $$\mu$$ is the friction coefficient, $$E$$ is the elasticity module of the DS material, $$I$$ is the inertia moment of the DS tube cross-section.
Then, equilibrium Eq. (11) can be transformed to the scalar form:
\begin{aligned} \frac{{dF_{n} }}{ds} & = - k_{R} F_{t} + k_{T} F_{b} - f_{n}^{gr} - f_{n}^{cont} , \\ \frac{{dF_{b} }}{ds} & = - k_{T} F_{n} - f_{b}^{gr} - f_{b}^{cont} , \\ \frac{{dF_{t} }}{ds} & = k_{R} F_{n} - f_{t}^{gr} - f_{t}^{fr} , \\ \end{aligned}
(15)
\begin{aligned} 0 & = - k_{R} M_{t} + EIk_{R} k_{T} + F_{b} , \\ \frac{{dk_{R} }}{ds} & = - \frac{1}{EI}F_{n} , \\ \frac{{dM_{t} }}{ds} & = - m_{t}^{fr} . \\ \end{aligned}
(16)
Via the use of Eq. (16), internal shear forces $$F_{n}$$ and $$F_{b}$$ are expressed in the form:
$$F_{n} = - EI\frac{{dk_{R} }}{ds},\quad F_{b} = k_{R} M_{t} - EIk_{R} k_{T} .$$
(17)
Thereafter, distributed contact forces $$f_{n}^{cont}$$ and $$f_{b}^{cont}$$ are determined
\begin{aligned} f_{n}^{cont} & = - k_{R} F_{t} + k_{R} k_{T} M_{t} - EIk_{R} k_{T}^{2} + EI\frac{{d^{2} k_{R} }}{{ds^{2} }} - f_{n}^{gr} , \\ f_{b}^{cont} & = k_{R} m_{t}^{fr} + 2EIk_{T}^{{}} \frac{{dk_{R} }}{ds} - M_{t} \frac{{dk_{R} }}{ds} + EIk_{R} \frac{{dk_{T} }}{ds} - f_{b}^{gr} . \\ \end{aligned}
(18)
Consider that the DS is being dragged with axial velocity $$a$$ and rotates with angular velocity $$\omega$$. Then, the total friction force is [3]
$$\left| {{\mathbf{f}}^{fr} } \right| = \mu \,\left| {{\mathbf{f}}^{cont} } \right| = \mu \sqrt {\left( {f_{n}^{cont} } \right)^{2} + \left( {f_{b}^{cont} } \right)^{2} } .$$
(19)
and it is resolved to the lengthwise and rotary constituents [8]
$$f_{t}^{fr} = \pm \mu f^{cont} \frac{a}{{\sqrt {a^{2} + (\omega r)^{2} } }},\quad f_{b}^{fr} = \pm \mu f^{cont} \frac{\omega r}{{\sqrt {a^{2} + (\omega r)^{2} } }}.$$
(20)
here $$\mu$$ is the Coulomb friction coefficient, $$r$$ is the DS tube radius, signs “+” and “−” are selected depending on directions of the DS axial movement and rotation. Coefficient $$\mu$$ is determined by mechanical properties of the tube material, rock formation and mud viscosity. It can vary in some diapason depending on combination of these factors.
Based on Eqs. (13)–(18), the system of constitutive equations of the DS dragging with rotation is deduced as follows:
\begin{aligned} \frac{{dF_{t} }}{ds} & = k_{R} F_{n} + \gamma t_{z} \mp \mu f^{cont} \frac{a}{{\sqrt {a^{2} + (\omega r)^{2} } }}, \\ \frac{{dM_{t} }}{ds} & = \mp \mu f^{cont} \frac{{\omega r^{2} }}{{\sqrt {a^{2} + (\omega r)^{2} } }}. \\ \end{aligned}
(21)
Under this approach, the problem of calculation of the bore-hole axis geometry parameters becomes the principal complexity. To determine the coefficients of the differential Eqs. (17)–(21), methods of differential geometry should be used for determination of the components of unit vectors $${\mathbf{n}},\;{\mathbf{b}},\;{\mathbf{t}}$$ and magnitudes $$k_{R}$$ and $$k_{T}$$. To define the first ones, the correlations
$${\mathbf{t}} = {{d{\kern 1pt} {\mathbf{r}}} \mathord{\left/ {\vphantom {{d{\kern 1pt} {\mathbf{r}}} {ds}}} \right. \kern-0pt} {ds}},\quad {\mathbf{n}} = {{Rd{\mathbf{t}}} \mathord{\left/ {\vphantom {{Rd{\mathbf{t}}} {ds}}} \right. \kern-0pt} {ds}},\quad {\mathbf{b}} = {\mathbf{t}} \times {\mathbf{n}}$$
(22)
are used [13].
Here, $$R = 1/k_{R}$$ is the curvature radius. It is calculated via the formula
$$k_{R} = 1/R = \sqrt {\left( {\frac{{d^{2} x}}{{ds^{2} }}} \right)^{2} + \left( {\frac{{d^{2} y}}{{ds^{2} }}} \right)^{2} + \left( {\frac{{d^{2} z}}{{ds^{2} }}} \right)^{2} } .$$
(23)
After this, the $$k_{T}$$ torsion is found as follows:
$$k_{T} = R^{2} \left| {\begin{array}{*{20}c} {x^{\prime } } & {y^{\prime } } & {z^{\prime } } \\ {x^{\prime \prime } } & {y^{\prime \prime } } & {z^{\prime \prime } } \\ {x^{\prime \prime \prime } } & {y^{\prime \prime \prime } } & {z^{\prime \prime \prime } } \\ \end{array} } \right|.$$
(24)
It is apparent that the transformations represented by correlations (22)–(24) cannot be performed analytically. Therefore, in the elaborated software, they are fulfilled numerically at every discrete point $$s_{i}$$ through the use of finite difference method:
\begin{aligned} \left. {t_{x} } \right|_{i} & = \left. {\frac{dx}{ds}} \right|_{i} = \frac{{x_{i + 1} - x_{i - 1} }}{{2\Delta {\kern 1pt} s}},\quad \left. {t_{y} } \right|_{i} = \left. {\frac{dy}{ds}} \right|_{i} = \frac{{y_{i + 1} - y_{i - 1} }}{2\Delta s},\quad \left. {t_{z} } \right|_{i} = \left. {\frac{dz}{ds}} \right|_{i} = \frac{{z_{i + 1} - z_{i - 1} }}{2\Delta s}, \\ \left. {k_{R} } \right|_{i} & = \sqrt {\left( {\frac{{x_{i + 1} - 2x_{i} + x_{i - 1} }}{{\Delta s^{2} }}} \right)^{2} + \left( {\frac{{y_{i + 1} - 2y_{i} + y_{i - 1} }}{{\Delta s^{2} }}} \right)^{2} + \left( {\frac{{z_{i + 1} - 2z_{i} + z_{i - 1} }}{{\Delta s^{2} }}} \right)^{2} .} \\ \end{aligned}
(25)
Derivatives $${{d{\kern 1pt} k_{R} } \mathord{\left/ {\vphantom {{d{\kern 1pt} k_{R} } {ds}}} \right. \kern-0pt} {ds}}$$, $${{d^{2} k_{R} } \mathord{\left/ {\vphantom {{d^{2} k_{R} } {ds^{2} }}} \right. \kern-0pt} {ds^{2} }}$$, $${{d{\kern 1pt} k_{T} } \mathord{\left/ {\vphantom {{d{\kern 1pt} k_{T} } {ds}}} \right. \kern-0pt} {ds}}$$ used in Eqs. (17), (18) are calculated analogously
\begin{aligned} \left. {\frac{{dk_{R} }}{ds}} \right|_{i} & \approx \frac{{(k_{R} )_{i + 1} - (k_{R} )_{i - 1} }}{{2\Delta {\kern 1pt} s}},\quad \left. {\frac{{d^{2} k_{R} }}{{ds^{2} }}} \right|_{i} \approx \frac{{(k_{R} )_{i + 1} - 2(k_{R} )_{i} + (k_{R} )_{i - 1} }}{{\Delta s^{2} }}, \\ \left. {\frac{{dk_{T} }}{ds}} \right|_{i} & \approx \frac{{(k_{T} )_{i + 1} - (k_{T} )_{i - 1} }}{{2\Delta {\kern 1pt} s}}. \\ \end{aligned}
(26)

Since the geometric functions calculated with the use of Eqs. (22)–(26) are changing fast at the points of the variables $$\delta x$$, $$\delta y$$, $$\delta z$$ irregularities, to achieve satisfactory convergente of their computing, it is necessary to select sufficiently small values of the $$\Delta {\kern 1pt} s$$ increments. In our analysis it was chosen to be $$S/1000$$.

## 3 Analysis of the numerical results of the generated resistance forces simulation

The elaborated techniques were used for numerical investigation of resistance forces generated in the channel of a bore-hole with geometric imperfections. Firstly, the case was considered when the planned trajectory of the bore-hole was ideal and was represented by smooth planar hyperbolic curve $$x_{0} (\vartheta )$$, $$y_{0} (\vartheta )$$, $$z_{0} (\vartheta )$$ described by equalities (Fig. 1)
\begin{aligned} x_{0} &= \frac{l(1 + \varepsilon )\cos \vartheta }{1 + \varepsilon \cos \vartheta },\quad y_{0} = 0,\quad z_{0} = \frac{h\sin \vartheta }{1 + \varepsilon \cos \vartheta } \hfill \\ & \quad \left( {3\pi /2 \le \vartheta \le 2\pi } \right). \hfill \\ \end{aligned}
(27)

Its lower point $$A$$ corresponds to initial values of constitutive parameters $$\vartheta = 3\pi /2$$, $$s = 0$$. At this end the drilling bit is attached and during drilling operation the DS is loaded by axial force $$F_{t} (0)$$ (FOB—force on bit) and torque $$M_{t} (0)$$ (TOB—torque on bit). The DS is suspended at its top end $$B$$ where $$\vartheta = 2\pi$$ and $$s = S$$. Here, it is powered by driving force $$F_{t} (S)$$ and torque $$M_{t} (S)$$.

In Eq. (27), $$l$$ = 8000 m is the horizontal distance between the lower and top points of the trajectory, $$h =$$ 4000 m is the bore-hole depth, $$\varepsilon$$ is the hyperbola eccentricity, dimensionless parameter $$\vartheta$$ is connected with natural parameter $$s$$ through metric multiplier
$$D = \sqrt {\dot{x}^{2} + \dot{y}^{2} + \dot{z}^{2} } = \frac{{\sqrt {l^{2} (1 + \varepsilon )^{2} \sin^{2} \vartheta + h^{2} (\cos \vartheta + \varepsilon )^{2} } }}{{(1 + \varepsilon \cos \vartheta )^{2} }}.$$
(28)
Under these parameters values, the DS length measures
$$S = \int\limits_{3\pi /2}^{2\pi } {D\,d\vartheta } = 9220\;{\text{m}}.$$
Then, the natural parameter $$s$$ was introduced in limits $$0 \le s \le S$$ and step $$\Delta {\kern 1pt} s = S/1000$$ of numeric integration was selected. Inside segment $$0 \le s \le S$$, points $$s_{i} = \Delta {\kern 1pt} s \cdot (i - 1)$$ ($$1 \le i \le n + 1$$) were preassigned. At these points, the corresponding values $$\vartheta_{i}$$ of parameter $$\vartheta$$ were calculated with the help of formula
$$\vartheta_{i} = \frac{3\pi }{2} + \int\limits_{0}^{{s_{i} }} {\frac{1}{D}ds} .$$
(29)

This enabled the coordinate values $$x_{0} (\vartheta_{i} )$$, $$y_{0} (\vartheta_{i} )$$, $$z_{0} (\vartheta_{i} )$$ to be found through the use of Eq. (27) at every point $$\vartheta_{i}$$ (and accordingly, $$s_{i}$$) and subsequently to transfer to presetting the same values $$x_{0} (s_{i} )$$, $$y_{0} (s_{i} )$$, $$z_{0} (s_{i} )$$ at the same points $$s_{i}$$ (Fig. 1). Thereupon, it became possible to calculate all geometric characteristics (22)–(24) by finite difference approximations (25), (26) usage, to compute internal and external forces (17)–(20), and to integrate Eq. (21) by the Runge–Kutta method.

Initially, this approach was utilized to analysis of a tripping out operation in a curvilinear bore-hole. It is characterized by the feature connected with the same orientations of the gravity $$f^{gr} (s)$$ and friction $$f^{fr} (s)$$ forces and addition of their resisting effects. For these reason, the resistance forces achieve their maximal values.

The external and internal radii of the DS tube were assumed to be $$r_{1} = 0.08415\,{\text{m}}$$ and $$r_{2} = 0.07415\,{\text{m}}$$, correspondingly. Its material was steel with the elasticity module $$E = 2.1 \cdot 10^{11} \,{\text{Pa}}$$, the tube linear gravity determined taking into account the mud buoyancy effect was considered to equal $$\gamma = 310.79\,{\text{N/m}}$$.

The calculations were performed at three values of the ratio $$\nu$$ of the axial velocity $$a$$ to the circumferential velocity $$\omega \,r_{1}$$ of the points on the outer surface of the tube: $$\nu = a/\omega \,r_{1}$$ = 100, 2, and 0.01. The stated problem for Eq. (21) was solved by the Runge–Kutta method with the step value $$\Delta \,s = S/1000$$. As a consequence of the performed computations, the distribution diagrams for the external gravity, contact, and friction forces, as well as the internal elastic forces and moments were constructed.

After completion of this analysis, the supposition was done that during the bore-hole drivage, some geometric deviations $$\delta {\kern 1pt} x(s)$$, $$\delta {\kern 1pt} y(s)$$, $$\delta {\kern 1pt} z(s)$$ were allowed because of technological factors and the rock heterogeneity. These deviations were measured by the methods of geophysic navigation and processed in tabular form with the $$\Delta \,s_{j}$$ step equal $$S/70 = 131.7$$ m. Two cases of the tabular distortions were considered. The first set of their values is represented in Table 1. The second set can be gained by simple doubling of the first values.
Table 1

Table values of increments $$\delta {\kern 1pt} x(s{}_{j})$$, $$\delta {\kern 1pt} y(s{}_{j})$$, and $$\delta {\kern 1pt} z(s{}_{j})$$ (case 1)

$$j$$

$$s{}_{j}$$ (m)

$$\delta {\kern 1pt} x_{j}$$ (m)

$$\delta {\kern 1pt} y_{j}$$ (m)

$$\delta {\kern 1pt} z_{j}$$ (m)

1

0.0

0.0

0.0

0.0

2

626.9

0.2930

0.0

0.9561

3

1200.3

0.2989

− 1.0

− 0.9543

4

1726.5

− 3.0499

0.0

9.5236

5

2210.7

1.5568

8.0

− 4.7515

6

2657.5

4.7701

− 3.0

− 14.2210

7

3070.7

− 1.6246

− 18.0

4.7287

8

3453.8

− 9.9637

− 8.0

28.2970

9

3809.8

− 13.5851

0.0

37.6230

10

4141.1

− 10.4230

20.0

28.1310

11

4450.0

− 1.7778

38.0

4.6733

12

4738.7

5.4605

10.0

− 13.9710

13

5008.8

1.8643

− 18.0

− 4.6394

14

5261.8

− 3.8207

0.0

9.2413

15

5499.3

0.3166

5.0

− 0.9201

16

5722.4

− 0.4017

0.0

0.9158

The graphic representation of the digital distortions $$\delta {\kern 1pt} x(s_{j} )$$, $$\delta {\kern 1pt} y(s_{j} )$$, $$\delta {\kern 1pt} z(s_{j} )$$ is shown in Fig. 2.

It should be emphasized that though the distortions outlined on the basis of discrete tabular data are introduced in the form of broken lines, in reality, they look like even differentiable (although, tortuous) curves.

With the aim to smoothen the digitally distorted trajectories $$x_{0} (s_{j} ) + \delta {\kern 1pt} x(s_{j} )$$, $$y_{0} (s_{j} ) + \delta {\kern 1pt} y(s_{j} )$$, $$z_{0} (s_{j} ) + \delta {\kern 1pt} z(s_{j} )$$, their spline interpolation (15) was performed. Schemes of their outlines for cases 1 and 2 are shown in Fig. 3a, b, correspondingly.
One can see that because imperfections included into the bore-hole geometry are small in comparion with its over all dimension these trajectories visually remained nearly unchanged and do not practically differ from the ideal bore-hole represented in Fig. 1. However curvatures $$k_{R}$$ of these smoothened trajectories essentially distinguished between each other (Fig. 4).

This feature is explained by the fact that the curvature is determined as the second derivative of a line profile and it depends not only on the imperfection magnitude but also on its pitch.

In the upper run of the bore-hole, its geometry is not distorted, so curvature values in the right segments of the presented graphs are not large, though the planned trajectory is maximum bent in this segment. In zone $$s$$ < 6000 m, functions $$k_{R} (s)$$ acquired drastic perturbations. It is seen in Fig. 4 that the maximal value of this function exceeds 0.0022 $${\text{m}}^{ - 1}$$, for case 2, while it is under 0.0001 $${\text{m}}^{ - 1}$$ for the ideal trajectory. This is the reason of the contact ($$f^{cont} (s)$$) and friction ($$f^{fr} (s)$$) forces enlargement in this zone.

The constructed geometries were used for computer investigation of the external and internal forces acting on the DS during carrying out the tripping out operation. By virtue of the fact that the DS is free at its lower end, the initial conditions
$$F_{t} (3\pi /2) = 0,\quad M_{t} (3\pi /2) = 0$$
(30)
were used for integration of Eq. (21).
Friction coefficient was assumed to be $$\mu = 0.2$$.The calculations were performed for three ratios $$\nu$$ of velocities of the axial and circumferential motions
$$\nu = a/(\omega r_{1} ) = 100,\;2,\;0.01.$$

In spite of large variations of these ratios all of them are realistic, as this parameter determines only proportion between the axial and circumferential velocities but not their absolute values. Indeed, value $$\nu = 100$$ does not mean that the axial velocity is very large but it points that the circumferential velocity is very small, though the first one is determined by the possibility of the driving mechanism. In the case $$\nu = 0.01$$, vice versa, the DS rotation velocity is determined by the driving mechanism and axial velocity is small.

In Fig. 5, the graph of the axial component $$f_{t}^{gr} (s)$$ of the distributed gravity is shown for the planned (ideal) trajectory and case 1. In the lower end vicinity ($$s = 0$$) this force is relatively small, thereupon it grows with $$s$$ enlargement, acquiring some oscillations conditioned by the trajectory geometry distortions (curve 1). After transfer to the undistorted segment ($$s > 6000$$ m), this curve became regular. At the top point ($$s = S = 9220$$ m) this function is equal to the linear gravity $$\gamma = 310.79\,{\text{N/m}}$$ of the DS tube.
The values of the contact $$f^{cont} (s)$$ force for case 1 are outlined in Fig. 6. It has a maximum at top point $$s = S$$.
The function of the distributed axial friction force $$f_{t}^{fr} (s)$$ (Fig. 7), determining the effect of the axial motion resistance, differs from the $$f^{cont} (s)$$ function only by coefficient $$\mu$$ and sign.

Inasmuch as these forces locally depend on geometric properties of the bore-hole axis, they practically coincide in periphery zones of the trajectory for the considered cases of ideal and tortuous curves but they have noticeable distinctions in the zone of tortuosity. In contrast, internal force $$F_{t} (s)$$ and torque $$M_{t} (s)$$ are integral characteristics, so their most pronounced distinctions are concentrated at the suspension point $$s = S$$.

As is evident from Eqs. (21) for the internal axial force $$F_{t} (s)$$, its value is basically determined by balance of axial gravity force $$\gamma \,t_{z}$$ and axial friction force $$\mu \,f^{cont} {a \mathord{\left/ {\vphantom {a {\sqrt {a^{2} + (\omega \,r_{1} )^{2} } }}} \right. \kern-0pt} {\sqrt {a^{2} + (\omega \,r_{1} )^{2} } }}$$. In tripping out, these forces are added and the effect of resisting to axial motion is amplified. During tripping in operation, the external distributed forces have different signs and they are striving to neutralize each other. The graphs of this force for the tripping out operation under condition $$\nu = 100$$ are shown in Fig. 8. Curves Id, 1, and 2 correspond to the planned (ideal) trajectory and cases 1 and 2. As evident from the illustration, even the small imperfections like these cause noticeable enlargement of the $$F_{t} (s)$$ force. The torque function (Fig. 9) has analogous properties.
As may be inferred from the calculation results, the profiles of functions $$F_{t} (s)$$ and $$M_{t} (s)$$ are characterized primarily by ratio $$\nu$$ and the form of technological operation (tripping in/out and drilling). Clearly, the $$\nu$$ reduction is associated with axial velocity decrease and increase of the circumferential velocity. Therefore, it causes reduction of axial force $$F_{t} (s)$$ and enlargement of torque $$M_{t} (s)$$ (compare Fig. 8 for $$\nu = 100$$ and Figs. 10, 12 for $$\nu = 2$$ and $$\nu = 0.01$$, as well as Figs. 9, 11, 13).

These results are of immediate interest to practice because values $$F_{t} (S)$$ and $$M_{t} (S)$$ are the force and torque applied to the DS top which are required for realization of the DS lifting and rotating. With enlargement of the rotation velocity $$\omega$$ ($$\nu = {a \mathord{\left/ {\vphantom {a {(\omega \,r_{1} ) = 2}}} \right. \kern-0pt} {(\omega \,r_{1} ) = 2}}$$), the lifting force $$F_{t} (S)$$ diminishes and driving torque $$M_{t} (S)$$ increases (Figs. 10, 11).

As previously, the curves labeled Id, 1, and 2 correspond to the ideal geometry and cases 1 and 2. The possibility to regulate the forces, resisting to axial motion of the DS, by way of its concurrent rotation is underlined by the numerical calculation performed at $$\nu = {a \mathord{\left/ {\vphantom {a {(\omega \,r_{1} ) = 0.01}}} \right. \kern-0pt} {(\omega \,r_{1} ) = 0.01}}$$ (Figs. 12, 13).
Then, the DS is lifted with very small velocity $$a$$ and rotates with high angular velocity $$\omega$$. This driving regime is typified by very small components of axial friction, therefore the resistance effect is conditioned predominantly by the gravity force. Owing to this, as is shown by [7], if to ignore friction forces in a smooth curvilinear bore-hole with any geometrical outline, the axial force $$F(S)$$ acting on the DS at the suspension point is equal to the gravity force acting on a vertical DS of length $$h$$. In our case
$$F_{t}^{id} (S) = \gamma \,h = 1244.84\;{\text{kN}}.$$
(31)
The values $$F_{t}^{id} (S)$$ of this force in the bore-hole with planned (ideal) geometry and appropriate forces $$F_{t}^{im} (S)$$ in the bore-holes with tabular imperfections, as well as the values of torques $$M_{t}^{id} (S)$$ and $$M_{t}^{im} (S)$$ are presented in Table 2.
Table 2

Values of axial force $$F_{t} (S)$$ and torque $$M_{t} (S)$$ at the suspension point during the operation of tripping out with rotation

$$\nu$$

Case

$$F^{id} (S)$$ (kN)

$$F^{im} (S)$$ (kN)

$$M^{id} (S)$$ (kN m)

$$M^{im} (S)$$ (kN m)

100

1

1871.542

1966.500

0.531

0.610

2

2177.468

0.787

2

1

1797.498

1874.292

23.427

26.648

2

2045.775

33.839

0.01

1

1244.814

1245.125

47.336

49.950

2

1245.900

56.461

These data attest that the axial force required for the DS lifting can be essentially reduced through its additional rotation.

The elaborated techniques and gained results permit one to perform computer modeling of the one of critical effects accompanying the tripping out operation. So, if during the tripping out process with the prescribed ratio $$\nu = {a \mathord{\left/ {\vphantom {a {(\omega \,r_{1} )}}} \right. \kern-0pt} {(\omega \,r_{1} )}}$$ the calculated $$F_{t} (S)$$ force value required for the DS hoisting falls out the limits of its magnitude admitted by the technological conditions or conditions of strength, then the tripping out operation is not realizable. In this case, it is necessary to enlarge the DS rotation velocity or to change the operation technology. When these effects are not feasible, the DS is called to be deadly locked.

The aforesaid dead lock situation appears when the power of the rig drive device is not sufficient to overcome the gravity and resistance forces acting on the DS. Another emergency situation can occur during tripping in operation. It arises when the gravity forces cannot overcome friction forces. At this situation it is needed to overload the DS at its top point or to change the technological regime. This operation also can be simulated with the use of Eq. (21), though now, sign “+” should be chosen before the friction force.

The obtained results testify that the investigated bore-hole is rather steep and because of this the emergency situations connected with the DS sticking do not appear during simulation the tripping in operations. They were again considered at the ratio $$\nu$$ values: $$\nu$$ = 100, 2, and 0.01. Here, directions of the gravity axis component $$f_{t}^{gr} (s)$$ and friction force $$f_{t}^{fr} (s)$$ are in opposition, which is why they neutralize each other even in axial motion with very slow rotation. In Figs. 14 and 15 the $$F_{t} (s)$$ and $$M_{t} (s)$$ functions are demonstrated for tripping in operation at ratio $$\nu = 100$$. As may be seen, the tortuosity influence on these functions is not essential in this case.
The rotation velocity increase insignificantly affects the $$F_{t} (s)$$ force but leads to increase of the $$M_{t} (s)$$ function (Figs. 16, 17).
This peculiarity retains its validity also for the regime with ratio $$\nu = 0.01$$ (Figs. 18, 19).

Particular emphasis can be placed on the effect presented in Fig. 18. Here, the DS slides down slowly along its axis as $$\nu = 0.01$$. Because of this, friction force $$f_{t}^{fr} (s)$$ is small, the DS slides practically without any resistance what solver and it is prestressed only by gravity force $$f_{t}^{gr} (s)$$. Since, $$F_{t} (s)$$ is integral function of $$f_{t}^{gr} (s)$$ which has comparatively small fluctuations with tortuosity addition (Fig. 5), its profiles in Fig. 18 practically coincide.

These features can be traced also with the use of Table 3. It follows from these data that if angular velocity $$\omega$$ is large ($$\nu = 0.01$$), values $$M_{t} (S)$$ are maximum and do not practically depend on the regime of the realized operation (tripping out or in) and the tortuosity values (case 1 or 2). Comparison of data in Tables 2 and 3 suggests that in this case, the $$F_{t} (S)$$ force value tends to limit value (31).
Table 3

Values of axial force $$F_{t} (S)$$ and torque $$M_{t} (S)$$ at the suspension point during the operation of tripping in with rotation

$$\nu$$

Case

$$F^{id} (S)$$ (kN)

$$F^{im} (S)$$ (kN)

$$M^{id} (S)$$ (kN m)

$$M^{im} (S)$$ (kN m)

100

1

725.269

719.835

− 0.432

− 0.436

2

706.194

− 0.448

2

1

775.840

769.648

− 19.458

− 19.719

2

754.200

− 20.368

0.01

1

1233.549

1233.246

− 47.236

− 49.779

2

1232.489

− 56.126

At the same time, the $$M_{t} (S)$$ torque induced at the suspension point essentially depends on the angular velocity value. It is small for small $$\omega$$ values, whether the first or second regimes are realized. These peculiarities validate the conclusion that the resistance forces and torques in a curvilinear bore-hole with geometric imperfections can be regulated by the value $$\nu$$ choice.

Thus, the elaborated approach enabled us for the first time to state and solve the important applied problem associated with the computer modeling friction effects impeding dragging drill strings in real tortuous bore-holes with geometry prescribed in tabular form through the use of results of geophysical survey. The mathematic models of the tripping in/out operations and drilling are based on the scientific methods of applied mathematics (the algorithms of spline interpolation and discrete integration), differential geometry (moving trihedrons), mechanics of structures (theory of curvilinear flexible rods), and theoretical mechanics (contact constraints and frictional interactions). With using the worked models and created software, it became possible to pioneer the solution of the multiparametric problems of simulating the resistance forces, generated by the elastic, gravitational, contact, and frictional influences. The states when the axial force, produced by the driving mechanism at the DS top, cannot overcome these resistance forces or the DS tube strength is not sufficient to bear the necessary internal axial forces are equivalent to dead locks.

The developed software is more universal in comparison with other known computer products because it allowed us to take into account and vary the parameters of the DS length and bending stiffness, the bore-hole curvature and its 3D tortuosity, the technological regimes (tripping in/out and drilling) and ways of their realization (axial motion and sliding with rotation). But the most important feature of the elaborabed approach is that it is suitable for its application to real field conditions when the bore-hole trajectory is prescribed in tabular form by the data of geophysical measurements.

## 4 Conclusions

1. 1.

With the use of the nonlinear theory of curvilinear elastic rods, the 3D stiff-string drag and torque model for computer analysis of contact and friction distributed forces generated during tripping in and out operations in drilling deep directed bore-holes is elaborated.

2. 2.

It is assumed that the trajectory of the bore-hole axis line (though continuous in reality) is set in a discrete (tabular) form by the values of its coordinates at separate points found by the methods of the bore-hole navigation. Transition to the analytic form of the geometry prescription is performed on the basis of the 3D cubic spline interpolation method.

3. 3.

The numerical analysis shows that the external distributed contact and resistance (frictional) forces and moments generated during the drilling operations performance essentially depend on the bore-hole axis tortuosity and they can be regulated by a special choice of the ratio between the velocities of the drill string dragging and rotation.

4. 4.

The elaborated techniques can be applied to the computer identification of distributed forces combinations impeding drill string movabilily and, by doing so, increasing energy consumption, intensifying the DS wear, and overloading its structural elements. It gives also the possibility to recognize the dead lock situations when the rig engine power is not sufficient to break through the generated force drag.

## Notes

### Conflict of interest

On behalf of all authors, the corresponding author states that there is no conflict of interest.

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