CN116522547A - Modeling method and system for load transfer model of pumping unit lifting system - Google Patents
Modeling method and system for load transfer model of pumping unit lifting system Download PDFInfo
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Abstract
The invention belongs to the technical field of oilfield oil extraction engineering, and particularly relates to a modeling method and a system for a load transfer model of an oil pumping unit lifting system. The modeling method comprises the following steps: establishing a four-bar linkage sub-model and a sucker rod system sub-model; integrating the four-bar linkage sub-model and the sucker rod system sub-model to form a load transfer model; determining the load pulse transmission characteristics of the load transfer model under different conditions; and comprehensively evaluating the load transfer model to obtain a final load transfer model. The invention fully understands the coupling relation between the self-vibration characteristic of the long rod and the load signal, deeply recognizes the amplitude-frequency response characteristic of the transmitted load, and provides theoretical support and guidance for setting core parameters and formulating transmission strategies in the field application of the shaft wireless communication method based on the sucker rod load pulse.
Description
Technical Field
The invention belongs to the technical field of oilfield oil extraction engineering, and particularly relates to a modeling method and a system for a load transfer model of an oil pumping unit lifting system.
Background
The mechanical lifting mode is adopted for 99% of oil extraction wells in the oil field in China, wherein the proportion of the oil pumping well is over 85%, and the lifting intellectualization is advanced in recent years. At present, the primary Internet of things mode mainly comprising ground indicator diagrams is applied to more than 6 ten thousand wells in oil fields such as Changqing, north China, hong Kong, xinjiang and the like, so that the functions of automatic collection of the ground indicator diagrams, background diagnostic analysis, production of the ground indicator diagrams and the like are realized, and a data basis is provided for diagnosis and metering of the pumping unit well. However, the current lifting internet of things data is mainly obtained on the ground in a manual or automatic mode, including stroke, stroke frequency, suspension point load, suspension point displacement, current, voltage, motor frequency and the like, so that an underground working condition diagnosis and production calculation prediction model is established, and the accuracy of the current lifting internet of things data is required to be verified due to lack of underground measured data comparison and verification. The intelligent adjustment of the oil pumping unit 'one well one strategy' cannot be realized, and a large gap exists between the intelligent lifting target of the oil pumping unit 'no human intervention'.
For this reason, around the urgent need of uploading the downhole data of the rod-pumped well, a wireless wellbore communication method based on the load pulse of the rod-pumped well is proposed, and defining the transmission characteristic of the load signal in the whole lifting system of the rod-pumped well is a key for realizing the wireless communication of the load pulse. Aiming at the load transmission problem of a pumping rod lifting system, gibbs et al propose a pumping rod one-dimensional wave equation considering viscous resistance, and combine wave equation solving with computer data processing to establish a computer numerical vibration evolution method. However, the working environment of the actual site needs to comprehensively consider the influences of factors such as well depth, well deviation, well fluid property, pump diameter, sucker rod centralizer and the like on the load transmission characteristics, and an ultra-long distance sucker rod load transmission model needs to be established urgently; traditional low-dimensional theoretical model schemes are limited by boundary conditions and simplification of transfer models, and cannot completely simulate and reproduce the load wave transfer process of a lifting system.
Disclosure of Invention
The invention provides a modeling method of a load transfer model of a pumping unit lifting system, aiming at the problems, comprising the following steps:
establishing a four-bar linkage sub-model and a sucker rod system sub-model;
integrating the four-bar linkage sub-model and the sucker rod system sub-model to form a load transfer model;
determining the load pulse transmission characteristics of the load transfer model under different conditions;
and comprehensively evaluating the load transfer model to obtain a final load transfer model.
Preferably, the building of the four-bar linkage sub-model includes:
determining a maximum included angle and a minimum included angle between the rear arm of the walking beam and the base rod;
determining a suspension displacement transfer parameter of the pumping unit;
and determining the selective point moving speed and the acceleration of the pumping unit.
Preferably, the building the four-bar linkage sub-model further comprises:
and determining a suspension displacement boundary condition, and taking the suspension displacement boundary condition as an upper forced displacement boundary condition of the sucker rod system submodel.
Preferably, the establishing the sucker rod system submodel comprises:
establishing a vibration differential equation set of the whole longitudinal and transverse directions of the sucker rod, and obtaining section parameters of any section positions of each level of sucker rod;
quantitatively analyzing the transmission characteristics of the pumping unit lifting system according to the section parameters;
and constructing a micro-element body of the sucker rod by combining a quantitative analysis result, and determining the distribution force type and form of the sucker rod to obtain a sub-model of the sucker rod system.
Preferably, the cross-sectional parameters include load, displacement, velocity, acceleration.
Preferably, the building the sucker rod system submodel further comprises:
the sucker rod system sub-model is calibrated and validated using field test data.
Preferably, said calibrating and validating the sucker rod system sub-model using field test data comprises:
extracting damping coefficient, natural frequency, damping ratio, sliding friction resistance and vibration inertia coefficient of the sucker rod high-frequency vibration, calibrating model parameters by a calculation method of load-time curve characteristic parameters in combination with field actual measurement load data, obtaining equivalent rigidity, equivalent density, coupling friction coefficient and damping friction coefficient, and determining model parameters of a sucker rod subsystem model.
Preferably, the evaluation basis for performing comprehensive evaluation on the load transfer model includes: transmission signal attenuation amplitude, transmission signal identification difficulty and transmission delay.
The invention also provides a modeling system of the load transfer model of the pumping unit lifting system, which comprises a modeling module, an integration module, a characteristic determination module and an evaluation module;
the modeling module is used for building a four-bar linkage sub-model and a sucker rod system sub-model;
the integration module is used for integrating the four-bar mechanism sub-model and the sucker rod system sub-model to form a load transmission model;
the characteristic determining module is used for determining the load pulse transmission characteristics of the load transfer model under different conditions;
the evaluation module is used for comprehensively evaluating the load transfer model to obtain a final load transfer model.
Preferably, the modeling module is configured to build a four-bar linkage sub-model, including:
determining a maximum included angle and a minimum included angle between the rear arm of the walking beam and the base rod;
determining a suspension displacement transfer parameter of the pumping unit;
and determining the selective point moving speed and the acceleration of the pumping unit.
Preferably, the modeling module is configured to build a sucker rod system sub-model, including:
establishing a vibration differential equation set of the whole longitudinal and transverse directions of the sucker rod, and obtaining section parameters of any section positions of each level of sucker rod;
quantitatively analyzing the transmission characteristics of the pumping unit lifting system according to the section parameters;
and constructing a micro-element body of the sucker rod by combining a quantitative analysis result, and determining the distribution force type and form of the sucker rod to obtain a sub-model of the sucker rod system.
The invention has the following beneficial effects:
(1) The invention provides a modeling method and a modeling system for a pumping unit lifting system load transfer model, which can establish the pumping unit lifting system load transfer model which is highly consistent with field working conditions and has universal applicability, and clear an energy attenuation mechanism and a main control factor in the load signal transmission process, fully understand the coupling relation between the self-vibration characteristic of a long rod and a load signal, deeply know the amplitude-frequency response characteristic of the transferred load, and provide theoretical support and guidance for setting core parameters and formulating transmission strategies in field application of a shaft wireless communication method based on pumping rod load pulse;
(2) The invention not only can guide the research and development and engineering application of the wireless communication technology of the shaft, but also can be widely applied to various applications related to the pumping unit lifting system. For example, the load transfer model under the support of underground actual measurement data and the mapping relation between the load transfer model and the driving electric parameters can optimize the intelligent lifting electric parameter working condition diagnosis and production calculation model, and the accuracy and the reliability of the intelligent lifting electric parameter working condition diagnosis and production calculation model are greatly improved; the load transfer model can simulate the contact state of the pipe rod under different working conditions, quantitatively analyze the bending deformation degree of the sucker rod, scientifically predict the abrasion position and the abrasion period, and provide theoretical basis for the design of a lifting system, the selection of downhole tools and the optimization of working system.
Additional features and advantages of the invention will be set forth in the description which follows, and in part will be obvious from the description, or may be learned by practice of the invention. The objectives and other advantages of the invention may be realized and attained by the structure particularly pointed out in the written description and claims hereof as well as the appended drawings.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the following description will briefly explain the drawings used in the embodiments or the description of the prior art, and it is obvious that the drawings in the following description are some embodiments of the present invention, and other drawings can be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 shows a schematic diagram of a modeling method of a load transfer model of a pumping unit lifting system in an embodiment of the invention;
FIG. 2 shows a kinetic theory model of a conventional beam-pumping unit;
FIG. 3 shows a long-range sucker rod theoretical model in an embodiment of the present invention;
FIG. 4 is a schematic diagram showing the pump body in the up-and-down stroke operation according to the embodiment of the present invention;
FIG. 5 shows a displacement vector diagram of a load cell during up and down strokes in an embodiment of the invention;
FIG. 6 shows a plot of ground load displacement during an up-down stroke in an embodiment of the invention;
fig. 7 is a schematic diagram illustrating a carrier signal transmission process according to an embodiment of the present invention;
FIG. 8 illustrates a schematic diagram of a sucker rod lifting system in an embodiment of the present invention;
FIG. 9 illustrates a representative segmented schematic representation of a finite element model of a sucker rod in an embodiment of the present invention;
FIG. 10 is a graphical representation of specific numerical model parameters of a sucker rod-based load transfer system in accordance with an embodiment of the present invention;
FIG. 11 shows a schematic diagram of a transmission system based on manual pump-side excitation in an embodiment of the invention;
FIG. 12 is a schematic diagram of an evaluation curve of vibration of a non-excited system according to an embodiment of the present invention;
FIG. 13 is a schematic diagram of an evaluation curve of modulation oscillation of an excitation system according to an embodiment of the present invention;
FIG. 14 illustrates a plot of the luffing load at various sucker rod lengths in an embodiment of the present invention;
FIG. 15 illustrates a plot of the suspension point load at Young's modulus for various sucker rods in an embodiment of the present invention;
FIG. 16 illustrates a plot of the lugging loads over a plurality of strokes in an embodiment of the invention;
FIG. 17 is a diagram of the lugging load at various times in an embodiment of the present invention;
FIG. 18 illustrates a plot of the suspension point load at various equivalent damping coefficients in an embodiment of the present invention;
FIG. 19 illustrates a lugging load profile at various upstroke pump loads in an embodiment of the invention;
FIG. 20 illustrates a plot of the lugging loads at various excitation load magnitudes in an embodiment of the present invention;
FIG. 21 illustrates a plot of the suspension point load at various excitation load spacings in an embodiment of the invention;
fig. 22 shows a schematic diagram of a modeling system of a load transfer model of a pumping unit lifting system according to an embodiment of the present invention.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
Based on theoretical mechanics principle and Gibbs vibration mechanics model, combining with wellhead packing friction force, in-pipe fluid damping, oil rod centralizer friction force, long rod inertia force and other acting force models, establishing a multi-degree-of-freedom dynamics theoretical model of the sucker rod under multi-factor constraint, forming a numerical model taking the constraint as a side value and an initial value condition, and realizing numerical model solving by utilizing a finite element method. And constructing a load transfer model of the complete lifting system of the pumping unit under a complex working condition by combining with a four-bar linkage dynamic model of the pumping unit. The specific contents include:
as shown in fig. 1, the invention provides a modeling method of a load transfer model of a pumping unit lifting system, which comprises the following steps:
(1) Establishing a four-bar linkage sub-model and a sucker rod system sub-model;
the traditional beam pumping unit is a typical hinge four-bar mechanism and consists of four parts of a crank, a connecting rod, a beam rear arm and a fixed rod, and a dynamics theoretical model of the traditional beam pumping unit is shown in figure 2. Because the four-bar linkage mechanism only provides displacement boundary conditions at suspension points in the wireless communication numerical model built by the invention, which is not the focus of the research focused by the invention, the four-bar linkage mechanism is described by adopting a dynamics equation under an ideal state and is drawn as the key boundary condition constraint of the sucker rod. By the triangular sine and cosine theorem, the geometrical relationship of each parameter is deduced as follows:
wherein, the liquid crystal display device comprises a liquid crystal display device,indicating rotor angular displacement>Indicating the angle of the central line of the rotating arm>Indicating the outer angle of the connecting rod cantilever->Representing the cantilever midline external angle.
The physical meaning of the parameters is shown in figure 2,representing the projection of the base bar in the horizontal direction, +.>Represents the center height of the drive motor,/-)>Indicating the rotation speed of the driving motor, +/->Indicating the rotation angle of the driving motor, & lt & gt>Represents crank radius +.>Representing crank-connecting rod angle->Indicating the length of the connecting rod>Represents the connecting rod-walking beam included angle->Represents the rotor midline>Representing the midline-transition clamp angle, +.>Represents the length of the rotor line +.>Represents the angle between the central line and the walking beam>Representing the connecting rod-midline angle>Represents the vertical angle of the rotating line->Indicating the length of the rear arm of the walking beam, < >>Indicating the length of the forearm of the walking beam,/->Indicating the height of the beam center of rotation, +.>Indicating sucker rod load>Representing the suspension point load +.>Representing the displacement of the suspension point->Indicating the suspension point velocity.
When the walking beam is respectively positioned at the bottom dead center and the top dead center, the maximum included angle between the back arm of the walking beam and the base rod can be obtainedMinimum included angle->The calculation formula is as follows:
;
;
when the displacement zero point of the pumping unit is at the upper dead point and the downward direction is positive, the displacement of the suspension point can be obtainedThe->As suspension displacement transfer parameters;
when the displacement direction of the suspension point of the pumping unit is positive, the motion speed of the suspension pointIs +.>The method comprises the following steps of:
;
wherein, the liquid crystal display device comprises a liquid crystal display device,indicating the angular velocity of the forearm of the walking beam, +.>Indicating the angular acceleration of the forearm of the walking beam.
According to the dynamics analysis, the relation between the ground suspension point load and the suspension point displacement, the suspension point speed, the suspension point acceleration and the electric signal motor power data can be clarified, the specific form of the suspension point displacement boundary condition can be determined, and the suspension point displacement boundary condition can be used as the upper forced displacement boundary condition of the long-distance sucker rod dynamics model.
(2) Integrating the four-bar linkage sub-model and the sucker rod system sub-model to form a load transfer model;
based on Gibbs three-dimensional damped wave theory equation, a differential equation set of the whole longitudinal and transverse vibration of the sucker rod is established by utilizing a balance micro-element method. According to the underground pump body load data, the load, displacement, speed, acceleration and the like at any section position of each level of sucker rod can be obtained by combining given boundaries and initial conditions and solving finite element values, and the transmission characteristics of the sucker rod pump system can be quantitatively analyzed by combining other production parameters of an oil well.
As shown in fig. 3, fig. 3 is a long-range sucker rod theoretical model, the theoretical model is composed of a motor, a beam pumping unit, a gearbox, a movable arm, a load meter, a centralizer, an oil pipe, an in-rod load sensor, a sleeve, a sucker rod and an adjustable valve, the load meter is arranged at the upper end of the sucker rod, the centralizer, the oil pipe, the in-rod load sensor, the sucker rod and the controllable valve are all positioned in the sleeve, the controllable valve is close to the bottom of the sleeve, the in-rod load sensors are two, the centralizer is used for restraining the transverse displacement of the sucker rod, the controllable valve is used for actively adjusting whether a pump cavity is communicated with an annulus, and the in-rod load sensor is used for monitoring the load transmission process in real time. The motor drives the gearbox to operate, the gearbox drives the movable arm to move, and the movable arm drives the sucker rod to move, so that the liquid suction and liquid discharge of petroleum are realized.
As shown in fig. 4, fig. 4 is a schematic diagram of the action of the pump body during the up-and-down stroke, and oil enters the cavity from the fixed valve during the up-stroke; when the oil is in the down stroke, the oil enters the movable valve and the oil pipe from the cavity.
As shown in fig. 5, fig. 5 is a graph of pump end load displacement during up and down strokes, where the abscissa represents displacement and the ordinate represents load, and the graph represents down and up strokes.
As shown in fig. 6, fig. 6 is a graph of ground load displacement during up-down stroke, wherein the abscissa represents displacement and the ordinate represents load, and the graph represents vibration generated during down-stroke and up-stroke.
As shown in fig. 7, fig. 7 shows a load wave signal transmission process, in which a load wave is converted from a clean wave to a mixed wave, and then formed into a superimposed wave.
FIG. 8 is a schematic diagram of a sucker rod lifting system under various practical condition constraints such as rod length, rod weight, rod diameter combination, well deviation, well fluid properties, pump diameter, rod centralizer, wellhead packing friction, etc., in which,indicating upper end transfer load +.>Indicating packing friction->Representing inertial force->Representing the contact normal force of the centralizer, +.>Indicating centralizer contact friction +.>Indicating centralizer diameter, +.>Indicating the axial length of the centralizer->Representing the axial length of the coupling>Indicating collar diameter->Indicating the diameter of the sucker rod>Indicating that the lower end is transmitting load,/->Indicating the acceleration of gravity>Indicating the fluid damping distribution force. According to the stress analysis, a long-range sucker rod micro-element body can be initially constructed so as to determine the main distribution force type and the specific form thereof.
The stress analysis is carried out on the infinitesimal section, the infinitesimal is subjected to combined action of upward load, downward load, infinitesimal gravity, viscous resistance of a rod wall and a coupling and friction force of a centralizer, as shown in fig. 9, packing friction force of a wellhead section is considered, pump body load is reciprocated, and a differential equation set is established based on an infinitesimal body stress balance equation:
；
wherein, the liquid crystal display device comprises a liquid crystal display device,represents the first direction of the lateral direction,/->Representing a transverse second direction，/>Indicates the axial direction>The time is represented by the time period of the day,indicating displacement(s)>Representing displacement boundary conditions, ++>Indicating the acceleration of gravity>The contact friction force is indicated as the expression,indicates the friction position +.>Indicating packing friction->Represents an initial displacement +.>Indicating the initial speed +.>Representing Young's modulus, & lt & gt>Indicating cross-sectional area->Indicating length of sucker rod>Representing the pump end load.
c is a damping coefficient, and the main influencing factors are hydrodynamic viscosity and equivalent sucker rod geometry, which can be obtained by calculating a fitting empirical formula of hydrodynamic damping and contact sliding friction damping of the sucker rod in a shaft:
；
wherein, the liquid crystal display device comprises a liquid crystal display device,representing the equivalent damping coefficient>Indicating the outer diameter of the oil pipe rod>Indicating the inner diameter of the oil pipe>Indicating the outer diameter of the rod coupling>Indicating the length of the sucker rod.
The primarily constructed dynamic numerical model can obtain basic knowledge of the dynamic characteristics of the pumping rod lifting system, and the numerical model is further calibrated and verified through a large amount of accurate field test data. Mainly comprises small-amplitude high-frequency vibration characteristics and high-amplitude low-frequency pulse signals, and utilizes the following formulas to extract parameters such as damping coefficient, natural frequency, damping ratio and the like of high-frequency vibration, the sliding friction resistance of the centralizer, the vibration inertia coefficient and the like,
；
wherein, the liquid crystal display device comprises a liquid crystal display device,representing equivalent frequency +.>Representing equivalent mass->Representing equivalent stiffness->Indicating cross-sectional area->Representing Young's modulus, & lt & gt>Indicating length of sucker rod>Indicate density,/->Represents the undamped frequency, < >>Represents the damping coefficient>Representing the amplitude ratio +_>Indicating vibration amplitude +.>Representing the equivalent dissipation force, +.>Representing damping dissipation force, ++>Indicative of frictional dissipation force->Indicating sub-friction dissipation force, < ->Representing inertial force->Representation ofAngular velocity (V/V)>Representing displacement.
According to the extraction scheme of damping parameters and friction coefficients of a damped vibration mechanics system, in combination with on-site actual measurement load data, model parameters are calibrated by utilizing a calculation method of load-time curve characteristic parameters, equivalent rigidity, equivalent density, coupling friction coefficients, damping friction coefficients and the like are obtained, specific numerical model parameters of a load transmission system mainly comprising a sucker rod are determined, as shown in figure 10,representing stroke load difference, +.>Indicating the difference in upstroke load, +.>Indicates period, & lt + & gt>Indicating the difference in downstroke load +.>Indicates upstroke interval, +.>Representing the amplitude of the first oscillation>Represents the amplitude of i times of oscillation, < >>Representing measurement intervals, the curve represents the suspension point load data.
(3) Determining the load pulse transmission characteristics of the load transfer model under different conditions;
on the basis of a numerical model of the sucker rod subjected to on-site data correction and verification, the logic diagram of the signal transmission system shown in fig. 11 is to be used, firstly, triangular wave excitation signals shown in fig. 12 and 13 are defined at the beginning point of a downstroke and are input into the numerical model, and load pulse transmission characteristics under different conditions such as various lifting system operation parameters, well condition parameters, modulation signal parameters and the like are studied, as shown in fig. 14-21.
As shown in fig. 11, the pump end is modulated and the valve port is controlled, the load of the pump end and the load of the sucker rod are analyzed to obtain the energy attenuation condition in the process from the pump end to the sucker rod, the load of the four-bar linkage (i.e. the suspension point load) is analyzed, and the stress condition of the suspension point is sampled to obtain the energy attenuation condition in the process from the sucker rod to the four-bar linkage. Further, in analyzing the pump end load and the sucker rod load, it is necessary to consider the influence of noise fluctuation, thereby improving the accuracy of analysis.
As shown in fig. 12, in the drawing,indicating downstroke load, +.>Indicating upstroke load, +.>Indicates the downstroke interval, +.>Indicates the interval between start of oscillation, +.>Indicating the amplitude of the oscillation>Representing the lower limit of the oscillation amplitude +.>Indicates period, & lt + & gt>Representing the suspension point load.
As shown in fig. 13, in the drawing,indicating downstroke load, +.>Indicating upstroke load, +.>Indicates the downstroke interval, +.>Indicates the interval between start of oscillation, +.>Indicating the amplitude of the oscillation>Representing the lower limit of the oscillation amplitude +.>Indicates period, & lt + & gt>Representing the suspension point load +.>Indicating the start of the excitation interval>Representing incentive platform interval, +.>Indicating the duration of the excitation, +.>Indicating the excitation number>Indicating the rising slope of the excitation, +.>Indicating the stimulus falling slope.
As shown in FIG. 14, four curves respectively represent the suspension point loads at various sucker rod lengths, namely 500 m, 900 m, 1200 m and 1500 m, and the increase in sucker rod length leads to an increase in load oscillation.
As shown in fig. 15, four curves in the figure respectively represent the suspension point loads under the young's modulus of various sucker rods, namely 150 GPa, 225 GPa, 300 GPa and 375 GPa, and according to the curves in the figure, the improvement of the equivalent young's modulus can obviously inhibit load oscillation.
As shown in FIG. 16, four curves represent the lugging loads at various strokes, respectively 1 m, 2 m, 4 m and 8 m, and from the curves, the increase in sucker rod stroke progressively increases the load fluctuation.
As shown in fig. 17, four curves in the figure respectively represent the suspension point loads under various stroke frequencies, namely 4.0, 2.7, 2.0 and 1.6, and according to the curves in the figure, the increase of the stroke frequency of the sucker rod greatly improves the amplitude and the frequency of load fluctuation.
As shown in FIG. 18, four curves respectively represent the suspension point loads under various equivalent damping coefficients, respectively 10N s/m 3 、25 N·s/m 3 、40 N·s/m 3 And 55N s/m 3 From the graph, it can be seen that the increase of the equivalent damping coefficient suppresses the amplitude of the oscillation fluctuation.
As shown in FIG. 19, four curves respectively represent the lugging loads at various upstroke pump loads, namely-5 kN, -2 kN, 1 kN and 4 kN, and the reduction of the upstroke load gradually suppresses the oscillation amplitude according to the curves.
As shown in fig. 20, five curves respectively represent the suspension point loads under various excitation load amplitudes, namely conventional, 1 kN, 3 kN, 5 kN and 7 kN, and according to the curves in the figure, the increase of the amplitude of the active excitation has less influence on the amplitude of the subsequent oscillation.
As shown in fig. 21, four curves respectively represent the suspension point loads at various excitation load intervals, namely 2 s, 4 s, 6 s and 8 s, and the increase of the excitation duration gradually reduces the subsequent oscillation degree according to the curves.
(4) And comprehensively evaluating the load transfer model to obtain a final load transfer model.
And evaluating signal transmission quality and accuracy based on the transmission signal attenuation amplitude, the transmission signal identification difficulty, the transmission delay and other standards to form a comprehensive evaluation result, and determining an energy attenuation mechanism and a main control factor in the load signal transmission process.
As shown in fig. 22, the invention further provides a modeling system of the load transfer model of the pumping unit lifting system, which comprises a modeling module, an integration module, a characteristic determination module and an evaluation module.
The modeling module is used for building a four-bar linkage sub-model and a sucker rod system sub-model;
the modeling module is used for building a four-bar linkage sub-model, and comprises the following components: determining a maximum included angle and a minimum included angle between the rear arm of the walking beam and the base rod; determining a suspension displacement transfer parameter of the pumping unit; determining the selective moving speed and acceleration of the pumping unit;
the modeling module is used for building a sucker rod system sub-model, and comprises the following components: establishing a vibration differential equation set of the whole longitudinal and transverse directions of the sucker rod, and obtaining section parameters of any section positions of each level of sucker rod; quantitatively analyzing the transmission characteristics of the pumping unit lifting system according to the section parameters; and constructing a micro-element body of the sucker rod by combining a quantitative analysis result, and determining the distribution force type and form of the sucker rod to obtain a sub-model of the sucker rod system.
The integration module is used for integrating the four-bar mechanism sub-model and the sucker rod system sub-model to form a load transmission model.
The characteristic determining module is used for determining the load pulse transmission characteristics of the load transfer model under different conditions.
The evaluation module is used for comprehensively evaluating the load transfer model to obtain a final load transfer model.
Those of ordinary skill in the art will appreciate that: although the invention has been described in detail with reference to the foregoing embodiments, it is to be understood that modifications may be made to the technical solutions described in the foregoing embodiments, or equivalents may be substituted for some of the technical features thereof; such modifications and substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.
Claims (11)
1. The modeling method of the load transfer model of the pumping unit lifting system is characterized by comprising the following steps of:
establishing a four-bar linkage sub-model and a sucker rod system sub-model;
integrating the four-bar linkage sub-model and the sucker rod system sub-model to form a load transfer model;
determining the load pulse transmission characteristics of the load transfer model under different conditions;
and comprehensively evaluating the load transfer model to obtain a final load transfer model.
2. The method for modeling a load transfer model of a pumping unit lifting system according to claim 1, wherein,
the building of the four-bar linkage sub-model comprises the following steps:
determining a maximum included angle and a minimum included angle between the rear arm of the walking beam and the base rod;
determining a suspension displacement transfer parameter of the pumping unit;
and determining the selective point moving speed and the acceleration of the pumping unit.
3. The method for modeling a load transfer model of a pumping unit lifting system according to claim 2, wherein,
the building of the four-bar linkage sub-model further comprises:
and determining a suspension displacement boundary condition, and taking the suspension displacement boundary condition as an upper forced displacement boundary condition of the sucker rod system submodel.
4. The method for modeling a load transfer model of a pumping unit lifting system according to claim 1, wherein,
the establishing the sucker rod system submodel comprises the following steps:
establishing a vibration differential equation set of the whole longitudinal and transverse directions of the sucker rod, and obtaining section parameters of any section positions of each level of sucker rod;
quantitatively analyzing the transmission characteristics of the pumping unit lifting system according to the section parameters;
and constructing a micro-element body of the sucker rod by combining a quantitative analysis result, and determining the distribution force type and form of the sucker rod to obtain a sub-model of the sucker rod system.
5. The method for modeling a load transfer model of a pumping unit lifting system according to claim 4, wherein,
the section parameters include load, displacement, velocity, acceleration.
6. The method for modeling a load transfer model of a pumping unit lifting system according to claim 4, wherein,
the establishing the sucker rod system sub-model further comprises:
the sucker rod system sub-model is calibrated and validated using field test data.
7. The method for modeling a load transfer model of a pumping unit lifting system according to claim 6, wherein,
the calibrating and verifying the sucker rod system sub-model using field test data includes:
extracting damping coefficient, natural frequency, damping ratio, sliding friction resistance and vibration inertia coefficient of the sucker rod high-frequency vibration, calibrating model parameters by a calculation method of load-time curve characteristic parameters in combination with field actual measurement load data, obtaining equivalent rigidity, equivalent density, coupling friction coefficient and damping friction coefficient, and determining model parameters of a sucker rod subsystem model.
8. The method for modeling a load transfer model of a pumping unit lifting system according to claim 1, wherein,
the evaluation basis for comprehensively evaluating the load transfer model comprises the following steps: transmission signal attenuation amplitude, transmission signal identification difficulty and transmission delay.
9. The modeling system of the load transfer model of the pumping unit lifting system is characterized by comprising a modeling module, an integration module, a characteristic determination module and an evaluation module;
the modeling module is used for building a four-bar linkage sub-model and a sucker rod system sub-model;
the integration module is used for integrating the four-bar mechanism sub-model and the sucker rod system sub-model to form a load transmission model;
the characteristic determining module is used for determining the load pulse transmission characteristics of the load transfer model under different conditions;
the evaluation module is used for comprehensively evaluating the load transfer model to obtain a final load transfer model.
10. The modeling system of a pumping unit lifting system load transfer model according to claim 9, wherein,
the modeling module is used for building a four-bar linkage sub-model, and comprises:
determining a maximum included angle and a minimum included angle between the rear arm of the walking beam and the base rod;
determining a suspension displacement transfer parameter of the pumping unit;
and determining the selective point moving speed and the acceleration of the pumping unit.
11. The modeling system of a pumping unit lifting system load transfer model according to claim 9, wherein,
the modeling module is used for building a sucker rod system sub-model, and comprises the following components:
establishing a vibration differential equation set of the whole longitudinal and transverse directions of the sucker rod, and obtaining section parameters of any section positions of each level of sucker rod;
quantitatively analyzing the transmission characteristics of the pumping unit lifting system according to the section parameters;
and constructing a micro-element body of the sucker rod by combining a quantitative analysis result, and determining the distribution force type and form of the sucker rod to obtain a sub-model of the sucker rod system.
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Application publication date: 20230801 |