Mathematical Problems in Engineering
Volume 2019 (2019), Article ID 9272751, 12 pages
https://doi.org/10.1155/2019/9272751

Research Article

Study on Equivalent Viscous Damping Coefficient of Sucker Rod Based on the Principle of Equal Friction Loss

Qin Li, Bo Chen, Zhiqiang Huang, Haipin Tang, Gang Li, and Lei He

School of Mechanical Engineering, Southwest Petroleum University, Chengdu, China

Correspondence should be addressed to Bo Chen; 714093521@qq.com

Received 24 October 2018; Revised 28 February 2019; Accepted 20 March 2019; Published 15 April 2019

Academic Editor: Andrés Sáez

Copyright © 2019 Qin Li et al. 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.

Abstract.

Equivalent viscous damping coefficient is an important parameter of wave equation for sucker rod string. In this paper, based on the principle of equal friction loss, when the viscous energy consumption and the local damping energy consumption are taken into account, effects of equivalent viscous damping coefficients are obtained. Through deducing energy consumption equation of oil and energy consumption equation of the coupling, theoretical formula for equivalent damping coefficient of sucker rods is received. Results show that the smaller the K is (K is the ratio of sectional area of tubing to sucker rod), the larger the proportion of damping coefficient caused by viscous energy consumption in the equivalent damping coefficient of sucker rod system is. When K< 0.095, the proportion of damping coefficient caused by viscous energy consumption is more than 90%. Reducing the sudden change of cross-section area at sucker rod coupling has remarkable effect on reducing damping force of the sucker rod system. The research provides a theoretical basis for the application and design of sucker rod and tubing.

1. Instruction

Sucker rod equipment is widely used in artificial lift wells [1–3]. Its failure modes are various, such as pump leakage, pump blockage, sucker rod facture, sucker rod eccentric wear, and so on. In order to accurately predict and judge the working condition of oil wells, the sucker rod string wave equation is regularly used to characterize the sucker rod pumping system. The wave equation contains viscous damping coefficient. The magnitude of viscous damping coefficient has a great influence on the results of prediction and diagnosis [4–7].

Since the 1960s, many researchers have carried out the study of equivalent viscous damping coefficient [8]. Now, there are many methods to determine the equivalent viscous damping coefficient, such as experiential algorithm, deduction formula of hypothetical conditions, calculated by surface dynamometer cards, etc. [9–12]. S.G.Gibbs considered that the nonviscous damping force is negligible. Assuming that the suspension point motion is a simple harmonic motion, the average velocity of the rod is expressed by the root mean square value of the instantaneous velocity of the sucker rod, and the dissipated work in one cycle of the rod string is equal to the dissipated work by the equivalent viscous damping. Based on these assumptions, the formula of the equivalent viscous damping coefficient is derived [13–15]. The formula of sucker rod damping force on the condition of laminar flow (Re<2300) is derived by A.M.Pearvillej, but the formula can only be applied to laminar flow in Poiseuille flow [16]. Based on the principle of equivalent method, the formula of dimensionless equivalent viscous damping coefficient is derived by Rubio D [17]. Zhang Qi used the energy consumption of the upstroke to replace the downstroke energy consumption. By calculating the friction loss caused by the viscous resistance of the sucker rod string in a cycle, the damping coefficient formula suited for various flow patterns is derived based on the principle of equal friction loss [18]. Using the curve method, M.J.Basition proposed that the intersection of the water power/damping coefficient and pump power/damping coefficient curves is the viscous damping coefficient of the sucker rod. Thus, the equivalent viscous damping coefficient is obtained [19]. Based on the Gibbs formula, Everitt, T.A. deduced the formula of viscous damping coefficient by cyclic iteration method. This method can be applied to any material sucker rod, but Gibbs damping coefficient formula can only be applied to steel sucker rod [20]. On the basis of the sucker rod string wave equation, Sun Renyuan et al. proposed the equivalent viscous damping coefficient formula which was related to the actual pump dynamometer cards by using the numerical integration method and established the corresponding iterative algorithm to calculate the equivalent viscous damping coefficient [21]. I.Steliga and Dong-Yu Wang proposed that the sucker rod dynamic model including the influences of rod-fluid-tubing viscous friction and rod-tubing Coulomb friction is developed. And then, a method for calculating vibration damping of sucker rod string based on indicator diagram is proposed. The periodic variation of vibration damping coefficient is analyzed with surface dynamometer cards and pump dynamometer cards. However, this method can only be used to analyze the dynamometer cards of a specific oil well [22, 23].

All the above studies are aimed at the specific well conditions, and the viscous damping coefficients are calculated when the size of sucker rod and tubing are unchanged. Unfortunately, the energy consumption of sucker rod coupling and rod guides in the process of pumping is not considered. The calculation model needs to be optimized. On the basis of Gibbs formula and Zhang Qi formula, this paper assumes that the fluid is Couette flow in a circular pipe and considers the energy consumption of coupling and rod guides. Based on the principle of equal friction loss, the equivalent viscous damping coefficient of sucker rod is derived. And the influence of sucker rod and tubing size on the equivalent viscous damping coefficient is analyzed, which provides a theoretical basis for sucker rod and tubing matching application.

2. Dynamic Equations of Sucker Rod String

Dynamic differential equation of sucker rod string (Figure 1) with viscous damping coefficient [14] is as follows:

Figure 1: The diagram of system and microelement of sucker rod string.

where is the displacement of the sucker rod node; is the distance between the node and the wellhead; is the run duration of sucker rod.

The suspension point displacement function and load function expressed by Fourier series are used as boundary conditions:

where , , , and are Fourier coefficient.

Combining (1)-(3), the displacement function of sucker rod at any depth of x section can be given by

3. The Principle of Equal Frictional Loss

When the wave equation is used to solve the dynamics of sucker rod string, the damping term is included in the equation. Damping of sucker rod string system is a combination of many factors, such as viscosity, temperature, and flow pattern of oil, so it is difficult to solve the real damping of the system. In general, equivalent damping coefficient is used to replace the real damping. The substituted condition is that the frictional loss done by the viscous damping term in the wave equation is equal to the energy loss in the actual pumping well during a period of motion, and the viscous damping coefficient is called the equivalent viscous damping coefficient. This described the principle of equal frictional loss [13].

where is the frictional loss of sucker rod string during a period of motion and is the energy consumption in actual pumping wells.

Without considering the Coulomb friction of single-stage rod vertical well, the actual energy consumption includes the viscous energy consumption in the up stroke and down stroke and the local viscous energy consumption of the oil passing through the sucker rod coupling in the actual operation of sucker rod.

Combining (5) and (6), the equivalent viscous damping coefficient is deduced:

4. Viscous Energy Consumption along the Tubing of Oil

Within a running cycle (Figure 3) of the sucker rod string, the oil moves up with the sucker rod and the direction of net flow is the same as that of the sucker rod during the up stroke. The sucker rod moves downward, but the direction of net flow of oil is upward. Then, the average velocity of oil is opposite to the direction of sucker rod movement on the occasion of the down stroke. Therefore, when calculating the viscous energy consumption along the tubing, the viscous energy consumption of the upstroke and the downstroke should be calculated, respectively, according to the net flow rate of oil.

4.1. Couette Flow of Circular Tube

In the process of pumping, the tubing is always in a static state and the sucker rod is in a moving state. Therefore, the oil flow can be regarded as Couette flow when analyzing the flow of oil in the tubing-rod string annulus [24].

The momentum equation of incompressible fluid with constant physical properties in cylindrical-coordinates system (Figure 2) can be expressed as

Figure 2: Sucker rod string in cylindrical-coordinate system.

(a)

(b)

Figure 3: Velocity distribution of crude along section. (a) Upstroke and (b) downstroke.

The function of the energy consumption along the tubing can be expressed as

where if , then , , and . If , then .

To solve the above equations, the oil is regarded as steady one-way parallel flow along the x-axis, which is uniform in the direction of flow and axisymmetric in the axial direction.

Substituting the above boundary conditions equation (10), the momentum equation (8) can be simplified to

where is a function of x and .

Define , is the baric gradient of fluid flow except gravity. And .

The momentum equation (11) can be further simplified to

Substituting the above boundary conditions equation (10), the energy consumption function along the tubing can be obtained:

By integrating the momentum equation (13), the oil velocity equation can be obtained:

Substitute the boundary conditions: . The coefficient and can be obtained:

Cross-section flow in X direction is as follows:

According to (17), the cross-section flow in the X direction is the vector sum of differential pressure flow and shear flow. The first half of the formula is differential pressure flow, and the second half is shear flow.

According to (13)-(16) and (18), the equation of energy dissipation per time per length of oil can be derived.

4.2. Viscous Energy Consumption of the Upstroke

The direction of oil movement is the same as that of the sucker rod in the upstroke; at the same time the sucker rod and the oil should be regarded as an integral whole in consideration of the viscous energy consumption. The viscous energy consumption is caused by the work loss by the oil shear force and the hydraulic loss along the oil flow. The actual flow rate of the oil pumping system is equal to the volume of the liquid discharged by the pump per time. When calculating the viscous energy consumption, the flow rate should be considered as the actual flow rate of the oil pumping system.

Without considering the elastic deformation of the sucker rod, the volume of the liquid discharged from the upstroke per time can be expressed as

where is the radius of the downhole pump plunger.

According to the continuity equation of oil flow, the cross-section flow rate in the X direction is equal to the volume of liquid discharged by the pump per time. Combine (17) and (20). P can be given by

On the upstroke (0 -), according to (19) and (21), the viscous energy consumption along the oil flow can be given by

4.3. Viscous Energy Consumption of the Downstroke

The inlet valve of defueling pump is closed and the outlet valve is opened during downstroke, at the same time the sucker rod enters the tubing and discharges corresponding volume of oil. Therefore, without considering leakage, the actual output flow of the pumping system is equal to the volume of the sucker rod entering the tubing per time.

The volume of the sucker rod entering the tubing in per time can be expressed as

Combine (17) and (24). P can be given by

On the downstroke (- T), according to (18) and (25), the viscous energy consumption along the tubing can be given by

5. Local Viscous Energy Consumption of Oil

Without considering the eccentricity of the sucker rod, the annulus area between sucker rod and tubing is small at the coupling since diameter of the coupling is larger than the sucker rod. After the oil passing through the coupling, the flow regime is changed and local resistance is lost. Similarly, local resistance loss will also occur at position of rod guides.

5.1. Local Viscous Energy Consumption at Couplings

Calculation formula of local damping force at coupling can be given by [25]

where is the radius of coupling; is the average velocity of oil passing through coupling; is the dimensionless coefficient which is defined as

While on the upstroke, is equal to 1 when is larger than 0; on the downstroke, is equal to -1 when is less than 0.

Local resistance pressure drop can be defined as shown below:

Local viscous energy consumption at coupling:

On the upstroke, according to the continuity equation, the relationship between the velocity of oil () and the rod speed () can be obtained:

According to (28)-(33), the local viscous energy consumption of upstroke at coupling can be given by

On the downstroke, the relationship between the velocity of oil () and the rod speed () can be obtained:

According to (28)-(32) and (35), the local viscous energy consumption of downstroke at coupling can be given by

5.2. Local Viscous Energy Consumption at Rod Guides

Friction caused by the resistance along rod guides can be expressed as [26]

Friction caused by local hydraulic loss at rod guides can be expressed as

According to (37) and (38), the calculation formula of local damping force at rod guides can be given by

where is the length of rod guides; is the number of rod guides; is the average velocity of oil passing through rod guides; is the dimensionless coefficient which is defined as

is the equivalent length of rod guides.

is the local resistance coefficient of rod guides; is the resistance coefficient along the rod guides; is the equivalent diameter of rod guides.

where is the flow surface between rod guides and tubing; is the wet circumference of flow surface between rod guides and tubing.

Local resistance pressure drop can be defined as shown below:

Local viscous energy consumption at rod guides is as follows:

On the upstroke, according to the continuity equation, the relationship between the velocity of oil () and the rod speed () can be obtained:

According to (37)-(45), the local viscous energy consumption of upstroke at rod guides can be given by

On the downstroke, the relationship between the velocity of oil () and the rod speed () can be obtained:

According to (37)-(44) and (47), the local viscous energy consumption of downstroke at rod guides can be given by

6. Equivalent Viscous Damping Coefficient

6.1. Theoretical Calculation

During the actual movement of the sucker rod, the energy consumption includes the resistance consumption along the sucker rod and the local energy consumption, which can be, respectively, expressed by (23), (26), (34), (36), (46), and (48). These energy consumption equations all contain the velocity of sucker rod. When calculating the equivalent viscous damping coefficient, it is necessary to simplify the term of velocity in the energy consumption equation at the final calculation of the equivalent viscous damping coefficient.

According to (1)-(4), the velocity equation of pumping rod can be obtained by Fourier series expansion:

The first half of (49) represents the suspension velocity; the second half represents the wave velocity; and are the Fourier coefficient.

The wave velocity is a periodic function and is far less than the suspension velocity. Therefore, the influence of wave velocity can be neglected in calculating energy consumption.

In the motion period of the sucker rod, the upstroke speed and downstroke speed can be regarded as equal, and (51) can be simplified to

The velocity of integral terms in (34) and (36) can be approximated to

The velocity of integral terms in (46) and (48) can be approximated to

where is the length of per sucker rod.

Substituting (23), (26), (34), (36), (46), (48), and (50)-(54) into (7), the viscous damping coefficient can be given by

Equation (55) can be decomposed into

is the equivalent damping coefficient caused by the viscous energy consumption in the process of sucker rod movement, is the equivalent viscous damping coefficient caused by the coupling energy consumption in the process of sucker rod movement, and is the equivalent viscous damping coefficient caused by the rod guides energy consumption in the process of sucker rod movement. The equivalent damping coefficient of the sucker rod system is equal to the linear superposition of the three parts.

The equivalent damping coefficient of the sucker rod can be calculated by (55). According to the actual measure of downhole pump dynamometer card and the surface dynamometer card, the actual equivalent damping coefficient of the sucker rod can be estimated. Next, the relevant parameters of oil wells in Xinjiang Karamay Oilfield are taken into (55) and Zhang Qi formula to estimate the equivalent damping coefficient of sucker rods. Compared with the measured equivalent damping coefficient of sucker rods, the results are shown in Table 1.

Table 1: Main parameters and calculated results of .

/(N•s/m²)
Pump setting depth/m
well depth/m

/mm
/mm
/mm

8
16
25.3
0.033
1148
1239
0.3845
0.4085
0.3477

9.5
16
25.3
0.028
1415
1504
0.3604
0.3807
0.2984

9.5
16
25.3
0.022
1836
1963
0.3221
0.3689
0.2345

9.5
19
31
0.029
1168
1253
0.3708
0.4605
0.3091

9.5
19
31
0.023
1724
1804
0.3369
0.3653
0.2451

Notes: is the value calculated by measured parameters; is the value calculated by (55); is the value calculated by Zhang Qi formula.

In this paper, the energy consumption of coupling and rod guides is considered. The predicted value of the equivalent damping coefficient derived from this method is larger than that predicted by Zhang Qi formula and is closer to the calculated value of the measured parameters (Table 1).

6.2. Application and Regulation Analysis

The theoretical formula of equivalent damping coefficient is showed in (55). The main factors affecting the equivalent damping coefficient are the radius of sucker rod, the radius of tubing, and oil viscosity. When calculating the equivalent damping coefficient, the oil well parameters (Table 2) of Xinjiang Karamay Oilfield are referred. The radius of sucker rod is regarded as the independent variable under different tubing radius. The equivalent damping coefficient caused by the viscous energy consumption along with the sucker rod movement, the local energy consumption, and the sucker rod system is calculated, respectively.

Table 2: Parameters in field application.

/ mm
/ mm
/ mm
/ (kg/m³)
/ (N•s/m²)

6.5-9.5
20.5
16
7850
0.020

6.5-11.5
25.3
19
7850
0.020

6.5-11.5
31
22
7850
0.020

8-14.5
38
28.5
7850
0.020

9.5-14.5
44.2
35
7850
0.020

11-14.5
50.3
41.5
7850
0.020

In Figure 4, the equivalent damping coefficient of the sucker rod system is between 0.01 and 0.281. When the tubing size is fixed, the equivalent damping coefficient of the sucker rod system and the equivalent damping coefficient caused by the viscous energy consumption along the sucker rod system decrease with the increasing of the radius of the sucker rod. Subsequently, the reduction rate of equivalent damping coefficient decreases gradually. The equivalent damping coefficient caused by coupling energy consumption raises with the increasing of sucker rod radius, and the rate is gradually raised. The equivalent damping coefficient caused by rod guides energy consumption is between 0.00042 and 0.0060. The rod guides have little effect on the equivalent damping coefficient. The larger the radius of the sucker rod, the smaller the influence of the rod guide. In practical application, this phenomenon is usually manifested as follows: due to the large downhole load in deep well and heavy oil well, it is necessary to select large size sucker rod in order to meet the strength, which results in the decrease of annulus area between tubing and sucker rod. The velocity of oil is quickened when the oil is passing through the coupling and the rod guide; the sudden change of the sectional area in coupling and rod guides increases the influence on flow state of oil and the energy consumption of coupling increases rapidly under certain conditions of oil well production. Therefore, it is necessary to ensure that there is sufficient annulus area between sucker rod and tubing and select sucker rod with smaller size when strength is sufficient in the design and matching of sucker rod and tubing.

(a) r₁= 20.5 mm

(b) r₁= 25.3 mm

(c) r₁= 31 mm

(d) r₁= 38 mm

(e) r₁= 44.2 mm

(f) r₁= 50.3 mm

Figure 4: Relationship between damping coefficient and radius of sucker rod. (a) r₁= 20.5 mm, (b) r₁= 25.3 mm, (c) r₁= 31 mm, (d) r₁= 38 mm, (e) r₁= 44.2 mm, and (f) r₁= 50.3 mm.

Compared with Figures 4(a)–4(f), the ratio of equivalent damping coefficient caused by coupling energy consumption to equivalent damping coefficient of sucker rod system decreases gradually with the increasing of radius of the tubing. The equivalent damping coefficient of sucker rod system is mainly produced by viscous energy consumption along the tubing. When the radius of the tubing increases to a value, the equivalent damping coefficient caused by the energy consumption of the coupling can be neglected. With the increase of the radius of tubing, the effect of rod guides on equivalent damping coefficient increases gradually, but the increase is not obvious. The proportion of equivalent damping coefficient caused by rod guides to the equivalent damping coefficient of sucker rod system is less than 4%. At the scene of the oil field, the main reason is that the annulus area between the tubing and the sucker rod amplifies, and the sudden change of the sectional area in sucker rod coupling weakens the influence on flow state of oil with the increasing of the tubing radius. Therefore, during the design and manufacture of sucker rod, reducing the sudden change of cross-section area at sucker rod coupling has remarkable effect on reducing damping force on the basis of satisfying the strength of sucker rod coupling.

In order to more accurately analyze the proportion of equivalent damping coefficient caused by viscous energy consumption in the total equivalent damping coefficient of sucker rod system, the proportional coefficient is introduced; K represents the ratio of area of cross-section in the sucker rod and tubing.

The smaller the ratio k of sectional area of tubing to sucker rod is (Figure 5), the larger the damping coefficient caused by viscous energy consumption in the sucker rod system is. For , the damping coefficient caused by viscous energy consumption in the sucker rod system accounts for more than 90% of the equivalent damping coefficient. In the pumping field, the larger the annulus area between the tubing and the sucker rod is, the smaller the damping of the sucker rod system by coupling energy consumption is. In slim hole oil well, the tubing size is small, and coupling energy consumption is an important part of energy consumption of sucker rod system. Therefore, to calculate the equivalent damping coefficient of sucker rod system, the local damping at the coupling should be considered. However, for the larger size of oil tube and smaller size of sucker rod, the damping of sucker rod system is mainly caused by viscous energy consumption. So, the influence of coupling and rod guides can be neglected for the sake of simplified calculation.

Figure 5: Relationship between equivalent damping coefficient along the tubing and proportional coefficient K.

7. Conclusions

(1) The function of energy consumption along the sucker rod stroke is derived when taking the fluid in the tubing as Couette flow, and the viscous energy consumption along the sucker rod downstroke and upstroke is deduced. Considering the influence of sucker rod coupling and rod guides, the function of the local energy consumption is derived under the condition of oil passing through the coupling and rod guides.

(2) Based on the principle of equal friction loss, the theoretical formula of equivalent damping coefficient of sucker rod system is deduced by considering the viscous energy consumption along the sucker rod and the local energy consumption of the coupling and rod guides. The effect of equivalent damping coefficient on sucker rod system is analyzed combined with the parameters in field application. The results show that, with the increase of the radius of rod, the annulus area of sucker rod and tubing, the equivalent damping coefficient, the equivalent damping coefficient caused by viscous energy consumption, and the equivalent damping coefficient caused by rod guides energy consumption all decrease; on the contrary, the equivalent damping coefficient caused by coupling energy consumption increases. During the design and matching of sucker rod and tubing, it is helpful to reduce the energy consumption of coupling by selecting the smaller sucker rod with sufficient strength.

(3) With the increase of the radius of tubing, the ratio of the equivalent damping coefficient caused by local viscous energy consumption to the equivalent damping coefficient of the sucker rod system decreases gradually. The equivalent damping coefficient of the sucker rod system is mainly produced by the viscous energy consumption along the sucker rod. The smaller the ratio k of sectional area of tubing to sucker rod is, the larger the damping coefficient caused by viscous energy consumption in the sucker rod system is. For , the damping coefficient caused by viscous energy consumption in the sucker rod system accounts for more than 90% of the equivalent damping coefficient. In the design and manufacture of sucker rod, reducing the sudden change of cross-section area of sucker rod coupling has a remarkable effect on reducing damping force.

Nomenclature

: | Displacement of the sucker rod node (m)
: | Distance between the node and the wellhead (m)
: | Equivalent viscous damping coefficient
: | Average flow velocity of oil before and after rod guides (m/s)
: | Equivalent diameter of rod guides (m)
: | Wet circumference of flow surface between rod guides and tubing (m)
: | Local viscous energy consumption at rod guides (N·m)
: | Total energy consumption (N·m)
: | Vertical depth (m)
: | Viscous coefficient of oil (Pa·s)
: | Length of per sucker rod
: | Ratio of radius of tubing to sucker rod
: | Viscous energy consumption along upstroke (N·m)
: | Viscous energy consumption along downstroke (N·m)
: | Coupling energy consumption along upstroke (N·m)
: | Upstroke time (s)
: | Radius of sucker rod (m)
: | Gravity acceleration (m/)
: | Radius of the pump plunger (m)
: | Ratio of sectional area of tubing to sucker rod
: | Length of rod guides (m)
: | Flow surface between rod guides and tubing ()
: | Number of rod guides
: | Local resistance pressure drop at rod guides (Pa)
: | Frictional work of sucker rod string (N·m)
: | Velocity of oil at coupling (m/s)
: | Cross-section flow (/s)
: | Period of the sucker rod motion (s)
: | Speed of sucker rod (m/s)
: | Time (s)
: | Local viscous energy consumption of upstroke at rod guides (N·m)
: | Local viscous energy consumption of downstroke at rod guides (N·m)
: | Coupling energy consumption along downstroke (N·m)
: | Density of the rod string (Kg/)
: | Radius of tubing (m)
: | Density of the fluid (Kg/).

Data Availability

No data were used to support this study.

Conflicts of Interest

The authors declare that they have no conflicts of interest.

Acknowledgments

The authors acknowledge the financial support by Mianyang Saien New Energy Technology Co., Ltd.

References

D. J. Schafer and J. W. Jennings, An Investigation of Analytical and Numerical Sucker Rod Pumping Mathematical Models, Texas A & M University, 1987.

P. A. Lollback, G. Y. Wang, and S. S. Rahman, “An alternative approach to the analysis of sucker-rod dynamics in vertical and deviated wells,” Journal of Petroleum Science and Engineering, vol. 17, no. 3-4, pp. 313–320, 1997.

I. N. Shardakov and I. N. Wasserman, “Numerical modelling of longitudinal vibrations of a sucker rod string,” Journal of Sound and Vibration, vol. 329, no. 3, pp. 317–327, 2010.

J. Xu, A New Approach to the Analysis of Deviated Rod-Pumped Wells, Society of Petroleum Engineers Richardson Tx, 1994.

L. Zifeng, “Yanshan University. Research advances and debates on tubular mechanics in oil and gas wells,” Journal of Petroleum Science & Engineering, 2016.

K. Palka and J. A. Czyz, “Optimizing downhole fluid production of sucker-rod pumps with variable motor speed,” SPE Production and Operations, vol. 24, no. 2, pp. 346–352, 2009.

C. H. Liu, “Sucker rod string design of the pumping systems,” Ingenieria e Investigacion, vol. 35, no. 2, pp. 6–14, 2015.

G. D. Reges, L. Schnitman, R. Reis, and F. Mota, “A new approach to diagnosis of Sucker Rod Pump Systems by analyzing segments of downhole dynamometer cards,” in Proceedings of the 2015 SPE Artificial Lift Conference - Latin America and Caribbean, pp. 414–426, Brazil, May 2015.

L.-M. Lao and H. Zhou, “Application and effect of buoyancy on sucker rod string dynamics,” Journal of Petroleum Science and Engineering, vol. 146, pp. 264–271, 2016.

M. Xing and S. Dong, “An improved longitudinal vibration model and dynamic characteristic of sucker rod string,” Journal of Vibroengineering, vol. 16, no. 7, pp. 3432–3448, 2014.

K. Li, X. Gao, Z. Tian, and Z. Qiu, “Using the curve moment and the PSO-SVM method to diagnose downhole conditions of a sucker rod pumping unit,” Petroleum Science, vol. 10, no. 1, pp. 73–80, 2013.

S. Miska, “98/00858 a simple model for computer-aided optimization and design of sucker-rod pumping systems,” Fuel & Energy Abstracts, vol. 39, no. 3, pp. 303–312, 1997.

S. Gibbs and A. Neely, “Computer diagnosis of down-hole conditions in sucker rod pumping wells,” Journal of Petroleum Technology, vol. 18, no. 01, pp. 91–98, 2013.

S. Gibbs, “Predicting the behavior of sucker-rod pumping systems,” Journal of Petroleum Technology, vol. 15, no. 07, pp. 769–778, 2013.

S. G. Gibbs, “Method of determining sucker rod pump performance,” US, US3343409, 1967.

S. D. L. Lekia and R. D. Evans, “A coupled rod and fluid dynamic model for predicting the behavior of sucker-rod pumping systems - part 1: model theory and solution methodology,” SPE Production and Facilities, vol. 10, no. 1, pp. 26–33, 1995.

D. Rubio and L. San Andres, “Structural stiffness, dry friction coefficient, and equivalent viscous damping in a bump-type foil gas bearing,” Journal of Engineering for Gas Turbines and Power, vol. 129, no. 2, pp. 737–746, 2007.

Q. Zhang, “Pumping well diagnostic technique and its application,” Journal of the University of Petroleum China, 1984 (Chinese).

M. J. Bastian, A two equation method for calculating down-hole dynomometer cards with a stady of damping effects [M.S. Thesis], Texas A & M University, Colleges Station, TX, USA, 1989.

T. A. Everitt and J. W. Jennings, “Improved finite-difference calculation of downhole dynamometer cards for sucker-rod pumps,” SPE Production Engineering, vol. 7, no. 1, pp. 121–127, 1992.

R. Sun Y, Y. Zhang F, K. Fan et al., “A new model and calculating method for pump dynamograph diagnosis of sucker rod pumping systems,” Applied Mathematics & Mechanics, vol. 35, no. 4, pp. 423–431, 2014.

D. Wang and H. Liu, “Dynamic Modeling and Analysis of Sucker Rod Pumping System in a Directional Well,” in Mechanism and Machine Science, vol. 408 of Lecture Notes in Electrical Engineering, pp. 1115–1127, Springer Singapore, Singapore, 2017.

I. Steliga, J. Grydzhuk, and A. Dzhus, “An experimental and theoretical method of calculating the damping ratio of the sucker rod column oscillation,” EasternEuropean Journal of Enterprise Technologies, vol. 2, no. 7, pp. 20–25, 2016.

W. G. Zhou and Z. He, Viscous Fluid Mechanics , National Defense Industry Press, 2013 (Chinese).

D. Doty R and Z. Schmidt, “Improved model for sucker rod pumping,” Society of Petroleum Engineers AIME, vol. 23, no. 1, pp. 33–41, 1983.

L. X. Du, Lifting System and Simulation Optimization of High-Angle Pumping Wells , Yanshan University, 2014 (Chinese).