A method, system, and medium for the equivalent reduction of the dynamics of an oil pumping unit's indicator diagram.

Abstract

This invention relates to the field of pumping unit operating condition analysis technology, and particularly to a method, system, and medium for the dynamic equivalent reconstruction of a pumping unit dynamometer diagram. The method includes: acquiring the suspension point load sequence, polished rod displacement sequence, and production regime parameters of the pumping unit, and time-aligning them to generate original dynamometer diagram data; extracting characteristic parameters of the dynamometer diagram based on the original dynamometer diagram data and production regime parameters; decomposing the suspension point load sequence into static load, inertial load, and friction load according to the dynamic relationship of the sucker rod string, and equivalently correcting them; performing phase correction based on load propagation characteristics to obtain a phase-aligned load sequence; determining the dynamic load residual based on the phase-aligned load sequence; using the dynamic load residual compensation to obtain an equivalent load sequence and an equivalent displacement sequence; and constructing an equivalent dynamometer diagram. This invention effectively solves the problem in existing dynamometer diagram operating condition identification where dynamic interference caused by changes in production regime parameters is difficult to accurately distinguish from actual downhole anomaly responses.

Description

Technical Field

[0001] This invention relates to the field of oil pumping unit operating condition analysis technology, and in particular to a method, system and medium for the dynamic equivalent reduction of an oil pumping unit indicator diagram. Background Technology

[0002] Pumping wells are a common oil production method in rod-pumped oilfield systems, and their operating status is usually analyzed using dynamometer cards. Dynamometer cards characterize the force changes and load transfer characteristics of the sucker rod string during reciprocating motion by relating the suspension point load to the polished rod displacement. They are an important basis for judging the downhole pump condition, equipment operating status, and production anomalies.

[0003] In existing technologies, pumping unit condition identification often employs dynamometer diagram geometric morphology analysis, template matching, feature parameter recognition, or image-based intelligent recognition methods. These methods compare the dynamometer diagram contour, load amplitude, area changes, and local distortion features to determine downhole conditions. However, in actual production, production parameters such as stroke count, stroke depth, and pump run-down depth are adjusted according to production needs. These parameter changes alter the dynamic response of the sucker rod string and fluid column, causing amplitude variations, phase shifts, and morphological distortions in the dynamometer diagram. Existing methods typically rely directly on the original dynamometer diagram for identification, making it difficult to distinguish between normal dynamic responses caused by these parameter adjustments and actual abnormal downhole responses. This can easily lead to misjudgments of operating conditions, affecting the accuracy and reliability of pumping unit condition analysis.

[0004] The information disclosed in this background section is intended only to enhance the understanding of the general background of this disclosure and should not be construed as an admission or in any way implying that the information constitutes prior art known to those skilled in the art. Summary of the Invention

[0005] This invention provides a method, system, and medium for the dynamic equivalent restoration of the indicator diagram of an oil pumping unit, which can effectively solve the problems in the background art.

[0006] To achieve the above objectives, the technical solution adopted by the present invention is as follows: A method for the dynamic equivalent reduction of an oil pumping unit indicator diagram, the method comprising: The suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit are obtained, and the suspension point load sequence and polished rod displacement sequence are time-aligned to generate the original dynamometer diagram data. Based on the original dynamometer diagram data and the production system parameters, extract the dynamometer diagram feature parameters, and determine the difference in dynamometer diagram response between the current operating condition and the baseline operating condition based on the dynamometer diagram feature parameters; Based on the dynamic relationship of the sucker rod string, the suspension point load sequence is decomposed into static load components, inertial load components, and friction load components, and the static load components, inertial load components, and friction load components are equivalently corrected based on the production system parameters and the reference operating conditions. Based on the load propagation characteristics in the sucker rod string, the phase correction is performed on the equivalently corrected suspension point load sequence to obtain a phase-aligned load sequence corresponding to the reference working condition. Based on the phase-aligned load sequence and the equivalently corrected static load component, inertial load component, and friction load component, determine the dynamic load residual between the current working condition and the reference working condition; The phase-aligned load sequence is compensated using the dynamic load residual to obtain an equivalent load sequence, and the polished rod displacement sequence is corrected according to the elastic deformation relationship of the sucker rod string to obtain an equivalent displacement sequence. An equivalent dynamometer diagram is constructed using the equivalent displacement sequence and the equivalent load sequence to eliminate the influence of changes in the production system parameters on the amplitude, phase, and shape of the dynamometer diagram.

[0007] Further, the original indicator diagram data is generated, including: Real-time acquisition of the suspension point load sequence and the polished rod displacement sequence corresponding to the dynamometer diagram of the pumping unit; The production system parameters of the pumping unit are acquired synchronously, including the current stroke, current stroke length, and current pump depth. The suspension point load sequence and the optical rod displacement sequence are time-aligned to establish a correspondence between the suspension point load sequence and the optical rod displacement sequence under a unified time reference. The original indicator diagram data is determined based on the time-aligned suspension point load sequence and the rod displacement sequence.

[0008] Further, determining the difference in dynamometer response between the current operating condition and the reference operating condition based on the dynamometer characteristic parameters includes: Extract the dynamometer area, maximum load, minimum load, and load amplitude from the original dynamometer data; The current stroke, current stroke length, and current pump depth are extracted based on the production system parameters. The feature vector for the current moment is constructed based on the suspension point load sequence, the rod displacement sequence, the dynamometer area, the maximum load, the minimum load, the load amplitude, the current stroke, the current stroke length, and the current pump depth. The dynamometer response characteristics under varying production system parameters are characterized by the feature vector, and the difference in dynamometer response between the current operating condition and the baseline operating condition is determined.

[0009] Furthermore, based on the production system parameters and the baseline operating conditions, equivalent corrections are made to the static load component, the inertial load component, and the friction load component, including: Based on the dynamic mechanism of the sucker rod string, the suspension point load sequence is represented as the superposition of the static load component, the inertial load component, and the friction load component; The static load component, the inertial load component, and the friction load component are solved using the regularized least squares method. A regularization term is introduced into the regularized least squares method to constrain the variation patterns of the static load component, the inertial load component, and the friction load component. The regularization term makes the static load component relatively stable near the top dead center and bottom dead center, makes the inertial load component have the same phase characteristics as the system acceleration change, and makes the friction load component change in opposite directions during the upstroke and downstroke.

[0010] Furthermore, the static load component is equivalently corrected, including: The static load component is determined based on the weight of the sucker rod string and the liquid column load. The static load correction factor is determined based on the changes in the production system parameters relative to the baseline operating condition. The static load correction factor is used to standardize the liquid column load; The corrected static load component is determined based on the weight of the sucker rod string and the benchmarked liquid column load. The static load correction factor characterizes the influence of stroke frequency, pump depth, and fluid distribution variations on the liquid column load.

[0011] Furthermore, the inertial load components are equivalently corrected, including: Without considering the influence of higher-order elastic vibrations of the rod and column, the suspension point motion corresponding to the suspension point load sequence is approximated as simple harmonic motion; The inertial load components are established based on the inertial motion of the sucker rod string and the inertial motion of the following fluid column; A state operator is introduced to characterize the influence of the opening and closing states of the moving valve on the inertial motion of the liquid column; When the traveling valve is closed during the upstroke, the state operator characterizes the liquid column's participation in inertial motion along with the rod column; When the traveling valve opens during the downstroke, the state operator characterizes that the liquid column does not participate in inertial motion with the rod column; The inertial load component of the following liquid column is determined based on the state operator, the liquid column acceleration correction coefficient, and the suspension point motion acceleration function; The inertial load component is determined based on the inertial load component of the sucker rod string and the inertial load component of the following fluid column; The inertial load correction coefficient is determined based on the current stroke, the current stroke length, the current pump depth, the reference stroke, the reference stroke, the reference pump depth, and the coupling correction function. The inertial load components are normalized and corrected using the inertial load correction coefficient to obtain the corrected inertial load components. The coupling correction function is determined based on the offset of the stroke relative to the reference stroke, the offset of the stroke length relative to the reference stroke, and the offset of the lower pump depth relative to the reference lower pump depth. The second-order coupling coefficients in the coupling correction function are used to characterize the second-order coupling effects between stroke-stroke, stroke-down pump depth, and stroke-down pump depth, respectively.

[0012] Furthermore, the friction load component is equivalently corrected, including: The friction load components are established based on the lateral contact force between the rod and the tubing, the combined friction coefficient, the viscous drag coefficient, the inertial drag coefficient, and the rod's movement speed. The product of the comprehensive friction coefficient and the lateral contact force is determined as the contact friction term between the rod and the tubing; The product of the viscous resistance coefficient and the velocity of the rod is determined as the viscous resistance term; The inertial drag coefficient and the square of the rod's velocity are defined as the inertial drag term; The corrected friction load component is determined based on the contact friction term, the viscous resistance term, and the inertial resistance term.

[0013] Further, determining the dynamic load residual, the equivalent load sequence, the equivalent displacement sequence, and the equivalent indicator diagram based on the phase-aligned load sequence includes: The theoretical time delay interval for load signal propagation is determined based on the stress wave propagation velocity in the sucker rod string and the pump depth. A local search interval is constructed within the theoretical time delay interval, centered on the reference propagation delay; The optimal time delay parameter is determined by maximizing the cross-correlation function within the local search interval. The search process for the optimal delay parameter is constrained by the maximum allowable step size; The phase-aligned load sequence is obtained by performing phase correction on the suspension point load sequence based on the optimal time delay parameter. Under normalized phase variables, the dynamic load residual is calculated based on the inertial load component and the friction load component of the current working condition and the reference working condition; The phase-aligned load sequence is compensated using the dynamic load residual, and the static load reference is restored to obtain the equivalent load sequence; Based on the elastic modulus of the rod material, the cross-sectional area of ​​the rod, and the resonant frequency of the rod, elastic deformation compensation is performed on the displacement sequence of the optical rod to obtain the equivalent displacement sequence. The equivalent dynamometer diagram is constructed with the equivalent displacement sequence as the horizontal axis and the equivalent load sequence as the vertical axis.

[0014] A dynamic equivalent reduction system for the indicator diagram of an oil pumping unit, the system comprising: The data acquisition and alignment module acquires the suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit, and performs time alignment between the suspension point load sequence and the polished rod displacement sequence to generate the original dynamometer data. The feature extraction and analysis module extracts dynamometer feature parameters from the original dynamometer diagram data and production system parameters, and determines the difference in dynamometer diagram response between the current operating condition and the baseline operating condition based on the dynamometer diagram feature parameters. The load decomposition correction module decomposes the suspension point load sequence into static load components, inertial load components, and friction load components based on the dynamic relationship of the sucker rod string, and performs equivalent corrections on the static load components, inertial load components, and friction load components based on production system parameters and benchmark operating conditions. The phase correction and alignment module performs phase correction on the equivalent correction of the suspension point load sequence based on the load propagation characteristics in the sucker rod string, so as to obtain a phase-aligned load sequence corresponding to the reference working condition. The dynamic residual determination module determines the dynamic load residual between the current working condition and the reference working condition based on the phase-aligned load sequence and the equivalent corrected static load components, inertial load components, and friction load components. The load-displacement reconstruction module compensates the phase-aligned load sequence using dynamic load residuals to obtain an equivalent load sequence, and corrects the polished rod displacement sequence based on the elastic deformation relationship of the sucker rod string to obtain an equivalent displacement sequence. The equivalent dynamometer construction module constructs an equivalent dynamometer diagram using equivalent displacement sequences and equivalent load sequences to eliminate the influence of changes in production regime parameters on the amplitude, phase, and shape of the dynamometer diagram.

[0015] A computer-readable storage medium storing a computer program, the computer program including program instructions, which, when executed by a processor, can implement the aforementioned method for the dynamic equivalent restoration of the pumping unit indicator diagram.

[0016] The technical solution of this invention can achieve the following technical effects: By collecting and aligning pumping unit dynamometer data and production regime parameters, load decomposition, equivalent correction, phase correction, and residual compensation are performed based on the dynamic relationship of the sucker rod string. Simultaneously, the displacement sequence is corrected to construct an equivalent dynamometer, thereby achieving the dynamic equivalent restoration of the dynamometer under the influence of changes in production regime. This effectively solves the problem of difficulty in accurately distinguishing the dynamic interference caused by changes in production regime parameters from the actual downhole abnormal response in existing dynamometer condition identification.

[0017] The above description is only an overview of the technical solution of this application. In order to better understand the technical means of this application and to implement it in accordance with the contents of the specification, and to make the above and other objects, features and advantages of this application more obvious and understandable, the following are specific embodiments of this application. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments recorded in the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 This is a flowchart illustrating a method for the dynamic equivalent reduction of a pumping unit's indicator diagram. Figure 2 This is a schematic diagram of the physical component decomposition of the suspension load; Figure 3 A comparison diagram showing the equivalent restoration of stroke-stroke adjustment; Figure 4 This is a comparison chart showing the equivalent restoration of stroke-stroke-pump depth adjustment. Detailed Implementation

[0020] The technical solutions of the present invention will be clearly and completely described below with reference to the accompanying drawings of the embodiments of the present invention. Obviously, the described embodiments are only some embodiments of the present invention, and not all embodiments.

[0021] Unless otherwise defined, all technical and scientific terms used herein have the same meaning as commonly understood by one of ordinary skill in the art to which this invention pertains. The terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to be limiting of the invention. The term "and / or" as used herein includes any and all combinations of one or more of the associated listed items.

[0022] Example 1; like Figure 1 As shown, this application provides a method for the dynamic equivalent reduction of the indicator diagram of an oil pumping unit, the method comprising: S10: Obtain the suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit, and time-align the suspension point load sequence and polished rod displacement sequence to generate the original indicator diagram data; S20: Extract dynamometer diagram characteristic parameters based on the original dynamometer diagram data and production system parameters, and determine the difference in dynamometer diagram response between the current working condition and the baseline working condition based on the dynamometer diagram characteristic parameters; S30: Based on the dynamic relationship of the sucker rod string, the suspension point load sequence is decomposed into static load components, inertial load components and friction load components, and the static load components, inertial load components and friction load components are equivalently corrected based on the production system parameters and the benchmark working conditions. S40: Based on the load propagation characteristics in the sucker rod string, the phase of the equivalent modified suspension point load sequence is corrected to obtain a phase-aligned load sequence corresponding to the reference condition. S50: Determine the dynamic load residual between the current working condition and the reference working condition based on the phase-aligned load sequence and the equivalent corrected static load component, inertial load component and friction load component. S60: The phase-aligned load sequence is compensated using the dynamic load residual to obtain the equivalent load sequence, and the polished rod displacement sequence is corrected according to the elastic deformation relationship of the sucker rod string to obtain the equivalent displacement sequence. S70: Construct an equivalent dynamometer diagram using equivalent displacement and equivalent load sequences to eliminate the influence of changes in production regime parameters on the amplitude, phase, and shape of the dynamometer diagram.

[0023] Specifically, during the operation of the pumping unit well, the suspension point load signal and the polished rod displacement signal are first collected, and the current production regime parameters of the pumping unit well are obtained simultaneously. The production regime parameters include stroke count, stroke length and pump depth. Then, the suspension point load signal and the polished rod displacement signal are time-aligned with a unified time base so that the suspension point load value and the polished rod displacement value at the same sampling time correspond to each other, thereby generating the original dynamometer data under the current operating conditions. After obtaining the original dynamometer card data, characteristic parameters of the dynamometer card that can characterize the shape of the dynamometer card and load changes are extracted. The characteristic parameters of the dynamometer card include the dynamometer card area, maximum load, minimum load and load amplitude. The characteristic parameters of the dynamometer card are used together with the current production system parameters to characterize the dynamometer card response state of the current working condition. At the same time, the dynamometer card under the stable production system or the preset standard state is selected as the benchmark working condition, thereby determining the response difference of the current working condition relative to the benchmark working condition. Furthermore, based on the force mechanism of the sucker rod string during reciprocating motion, the suspension point load sequence is decomposed into static load components, inertial load components, and friction load components. The static load component is used to characterize the influence of the sucker rod string's own weight and the liquid column load, the inertial load component is used to characterize the inertial response caused by the acceleration changes of the sucker rod string and the following liquid column, and the friction load component is used to characterize the contact friction between the rod string and the tubing and the influence of liquid resistance. Then, based on the changes in production system parameters relative to the baseline operating conditions, the static load component, inertial load component, and friction load component are respectively equivalently corrected to reduce the load response deviation caused by changes in stroke frequency, stroke length, and pump depth. After completing the equivalent correction of the load components, the phase correction of the suspension point load sequence is performed based on the load propagation characteristics in the sucker rod string. Specifically, the time delay search range can be determined according to the time delay effect caused by the propagation of stress waves in the rod string, and the optimal time delay parameter of the current working condition relative to the reference working condition can be determined by cross-correlation matching. Then, the phase alignment of the suspension point load sequence is performed using the optimal time delay parameter to obtain the phase-aligned load sequence corresponding to the reference working condition. Subsequently, under a unified phase coordinate system, the inertial load components and friction load components under the current working condition, after equivalent correction, are compared with the corresponding load components under the reference working condition to determine the dynamic load residual between the current working condition and the reference working condition. The dynamic load residual is used to characterize the dynamic load difference that still exists after the production system parameters change, and serves as the basis for subsequent load compensation. Furthermore, the phase-aligned load sequence is compensated using the dynamic load residual to obtain an equivalent load sequence, so that the load response under the current working condition is restored to an equivalent physical reference consistent with the reference working condition; at the same time, the rod displacement sequence is corrected according to the elastic deformation relationship generated by the sucker rod string under dynamic load to obtain an equivalent displacement sequence, so as to compensate for the displacement distortion caused by the elastic elongation of the rod string. Finally, an equivalent dynamometer diagram is constructed with the equivalent displacement sequence as the horizontal axis and the equivalent load sequence as the vertical axis. The equivalent dynamometer diagram is used to characterize the downhole operating conditions after eliminating the influence of changes in production system parameters, thereby reducing the interference of parameter adjustment factors on the amplitude, phase and shape of the dynamometer diagram, and improving the accuracy and reliability of pumping unit well operating condition identification.

[0024] The technical solution of this invention collects and aligns pumping unit dynamometer diagram data and production regime parameters. Based on the dynamic relationship of the sucker rod string, load decomposition, equivalent correction, phase correction, and residual compensation are performed, and the displacement sequence is simultaneously corrected to construct an equivalent dynamometer diagram. This achieves the dynamic equivalent restoration of the dynamometer diagram under the influence of changes in production regime, effectively solving the problem that it is difficult to accurately distinguish between the dynamic interference caused by changes in production regime parameters and the actual downhole abnormal response in the existing dynamometer diagram operating condition identification.

[0025] Furthermore, generating the original indicator diagram data includes: Real-time acquisition of the suspension point load sequence and polished rod displacement sequence corresponding to the dynamometer diagram of the pumping unit; Simultaneously acquire the production system parameters of the pumping unit, including the current stroke, current stroke length, and current pump depth; Time alignment processing is performed on the suspension point load sequence and the rod displacement sequence to establish a correspondence between the suspension point load sequence and the rod displacement sequence under a unified time reference; The original indicator diagram data is determined based on the time-aligned suspension point load sequence and the rod displacement sequence.

[0026] Furthermore, determining the difference in dynamometer response between the current operating condition and the baseline operating condition based on dynamometer characteristic parameters includes: Extract the dynamometer area, maximum load, minimum load, and load amplitude from the original dynamometer data; Extract the current stroke, current stroke length, and current pump depth based on the production system parameters; Construct the feature vector for the current moment based on the suspension point load sequence, the rod displacement sequence, the dynamometer area, the maximum load, the minimum load, the load amplitude, the current stroke, the current stroke length, and the current pump depth; The dynamometer response characteristics under varying production parameters are characterized by eigenvectors, and the difference in dynamometer response between the current operating condition and the baseline operating condition is determined.

[0027] As a preferred embodiment of the above, the raw data of the pumping unit's indicator diagram are acquired in real time, including the suspension point load sequence. With the displacement sequence of the light rod Simultaneously acquire production system parameters, including stroke count. Stroke length Pump depth Parameters such as these are recorded, and their changes over time are also recorded. The acquired dynamometer card data is time-aligned to establish a correspondence between the suspension point load sequence and the rod displacement sequence under a unified time reference; and statistical characteristic parameters of the dynamometer card are extracted to construct a time-series mapping. eigenvectors : ; in, For suspension point load; For the displacement of the smooth rod; The area of ​​the work diagram; and These are the maximum load and the minimum load, respectively; This refers to the load amplitude. For the current stroke; This represents the current stroke length. This is the current pump depth; Based on the eigenvector characterization of the response characteristics of the indicator diagram under the condition of changes in production system parameters, input data is provided for the equivalent reconstruction of step dynamics.

[0028] Furthermore, based on production system parameters and baseline operating conditions, equivalent corrections are made to the static load components, inertial load components, and friction load components, including: Based on the dynamic mechanism of the sucker rod string, the suspension point load sequence is represented as the superposition of static load components, inertial load components, and friction load components; The static load component, inertial load component, and friction load component are solved using the regularized least squares method. A regularization term is introduced into the regularized least squares method to constrain the variation of static load components, inertial load components, and friction load components. The regularization term makes the static load component relatively stable near the top dead center and bottom dead center, makes the inertial load component have the same phase characteristics as the system acceleration change, and makes the friction load component change in opposite directions during the upstroke and downstroke.

[0029] As a preferred embodiment of the above, based on the dynamic mechanism of the sucker rod string, the suspension point load is decomposed and equivalently corrected; the measured suspension point load is expressed as a superposition of static load, inertial load, and friction load: ; in, This is the static load component; This is the inertial load component; The load components are frictional. Based on the load decomposition form, a regularized least squares method is used to solve for each load component to improve the stability and noise resistance of the load decomposition process. ; in, For the first Each sampling time, This represents the number of sampling points; Let the load component vector be the one to be determined. is the regularization coefficient, with a value range of (0.001, 0.1). The regularization term is constructed in conjunction with the dynamic characteristics of the sucker rod string to constrain the variation law of each load component, so that the decomposition result satisfies the following physical characteristics: the static load exhibits relatively stable changes near the top dead center and the bottom dead center; the inertial load has consistent phase characteristics with the system acceleration change; and the friction load exhibits opposite trends in direction during the upstroke and downstroke.

[0030] Furthermore, equivalent corrections are made to the static load components, including: The static load component is determined based on the weight of the sucker rod string and the liquid column load. The static load correction factor is determined based on the changes in production system parameters relative to the baseline operating condition. The liquid column load is benchmarked using a static load correction factor; The corrected static load component is determined based on the weight of the sucker rod string and the standardized liquid column load. The influence of stroke frequency, pump depth, and fluid distribution variation on liquid column load is characterized by static load correction factor.

[0031] As a preferred embodiment of the above, the static load is mainly composed of the weight of the sucker rod string. and liquid column load Composition; To mitigate the impact of changes in production system parameters on the load response of the indicator diagram, the static load component is equivalently corrected; A static load correction model is constructed to standardize the liquid column load; its expression is as follows: ; in, This is the corrected static load component; This is the static load correction factor, which characterizes the influence of stroke frequency, pump depth, and fluid distribution variations on the liquid column load.

[0032] Furthermore, equivalent corrections are made to the inertial load components, including: Without considering the influence of higher-order elastic vibrations of the rod and column, the suspension point motion corresponding to the suspension point load sequence is approximated as simple harmonic motion; The inertial load components are established based on the inertial motion of the sucker rod string and the inertial motion of the following fluid column; A state operator is introduced to characterize the influence of the opening and closing states of the moving valve on the inertial motion of the liquid column; When the traveling valve closes during the upstroke, the state operator characterizes the inertial motion of the liquid column along with the rod column. When the traveling valve opens during the downstroke, the state operator characterizes that the liquid column does not participate in inertial motion with the rod column; The inertial load components of the following liquid column are determined based on the state operator, the liquid column acceleration correction coefficient, and the suspension point motion acceleration function. The inertial load components are determined based on the inertial load components of the sucker rod string and the inertial load components of the following fluid column; The inertial load correction factor is determined based on the current stroke, current stroke length, current pump depth, reference stroke, reference stroke, reference pump depth, and coupling correction function. The inertial load components are normalized and corrected using inertial load correction factors to obtain the corrected inertial load components. The coupling correction function is determined based on the offset of the stroke relative to the reference stroke, the offset of the stroke length relative to the reference stroke, and the offset of the lower pump depth relative to the reference lower pump depth. The second-order coupling coefficients in the coupling correction function are used to characterize the second-order coupling effects between stroke and stroke, stroke and pump depth, and stroke and pump depth, respectively.

[0033] As a preferred embodiment of the above, the inertial load component consists of the inertial forces of the sucker rod string and the following fluid column. Without considering the influence of the elastic higher-order vibration of the rod string, the motion of the suspension point is approximated as simple harmonic motion. Based on the working mechanism of the oil pump, a state operator is introduced. This is used to describe the effect of the moving valve's opening and closing state on the liquid column's participation in inertial motion. Its value is: during the upstroke, the moving valve is closed, and the liquid column moves with the rod. During the downstroke, the traveling valve opens, and the liquid column does not move with the rod. ; Based on the above conditions, the physical model of the inertial load components is as follows: ; in, This represents the inertial load component of the sucker rod string; The inertial load component of the following liquid column; This is the correction factor for the liquid column acceleration; Let be the acceleration function of the suspension point motion; The weight of the sucker rod string; For liquid column load; It is the acceleration due to gravity; To achieve equivalent mapping of inertial loads under different production systems, the inertial load components are normalized and corrected, and their expression is as follows: ; in, The corrected inertial load components; This is the inertial load correction factor; Inertial load correction factor This is a function of production system parameters, used to characterize the coupled effect of variations in stroke count, stroke length, and pump depth on the inertial response. Its expression is: ; in, As the baseline stroke; The reference stroke; The reference depth for pumping; This is a coupling correction function; This is the current pump depth; For the current stroke; For the current stroke; This represents the offset of the current stroke relative to the reference stroke. This represents the offset of the current stroke relative to the reference stroke. This represents the offset of the current pump depth relative to the reference pump depth. To accurately describe the second-order coupling effect of multidimensional parameters, a coupling correction function is introduced: ; in, , , This represents the offset of each parameter relative to the baseline operating condition; , , These are second-order coupling coefficients, used to characterize the second-order coupling effects between stroke-stroke, stroke-down pump depth, and stroke-down pump depth, respectively.

[0034] Furthermore, equivalent corrections are made to the friction load components, including: The friction load components are established based on the lateral contact force between the rod and the tubing, the comprehensive friction coefficient, the viscous resistance coefficient, the inertial resistance coefficient, and the rod's movement speed. The product of the overall friction coefficient and the lateral contact force is determined as the contact friction term between the rod and the tubing; The product of the viscous drag coefficient and the velocity of the rod is defined as the viscous drag term; The inertial drag coefficient and the square of the rod's velocity are defined as the inertial drag term; The corrected friction load components are determined based on the contact friction term, viscous resistance term, and inertial resistance term.

[0035] As a preferred embodiment of the above, the frictional load mainly consists of the contact friction between the rod and the oil pipe and the resistance between the liquid and the pipe wall, and its expression is: ; in, This refers to the lateral contact force between the rod and the tubing; The comprehensive friction coefficient; The coefficient of viscous drag is ; Let be the inertial drag coefficient; Let be the velocity of the rod / column.

[0036] Furthermore, the dynamic load residuals, equivalent load sequences, equivalent displacement sequences, and equivalent indicator diagrams are determined based on the phase-aligned load sequences, including: The theoretical time delay interval for load signal propagation is determined based on the stress wave propagation velocity in the sucker rod string and the pump depth. A local search interval is constructed within the theoretical time delay interval, centered on the reference propagation delay; The optimal time delay parameter is determined by maximizing the cross-correlation function within the local search interval; The process of searching for the optimal time delay parameter by constraining the maximum allowable step size; Phase correction is performed on the suspension point load sequence based on the optimal time delay parameters to obtain the phase-aligned load sequence; Under normalized phase variables, the dynamic load residuals are calculated based on the inertial load components and friction load components of the current working condition and the reference working condition. The phase-aligned load sequence is compensated using the dynamic load residual, and the static load reference is restored to obtain the equivalent load sequence. Based on the elastic modulus of the rod material, the cross-sectional area of ​​the rod, and the resonant frequency of the rod, elastic deformation compensation is performed on the displacement sequence of the smooth rod to obtain the equivalent displacement sequence. An equivalent dynamometer diagram is constructed with the equivalent displacement sequence as the horizontal axis and the equivalent load sequence as the vertical axis.

[0037] As a preferred embodiment of the above, under the change of production system parameters, the load response of the indicator diagram will show changes in amplitude, phase and shape, and it is necessary to perform time delay correction and residual compensation. Based on the time delay characteristics of stress wave propagation in the sucker rod string, a load signal phase correction model is constructed to constrain the propagation time delay of the measured load sequence. Its theoretical time delay interval is defined as: ; in, This is the lower bound for latency search; This is the upper limit for latency search; The velocity of stress wave propagation in the rod / column; This is the current pump depth; To improve the stability of time delay estimation, a local contraction strategy is introduced based on the theoretical time delay interval to reference the time delay. Construct the search range around the center: ; in, Reference propagation delay.

[0038] Within the search interval, the optimal time delay parameter is determined by maximizing the cross-correlation function. To suppress mismatches caused by noise interference, a step size constraint is introduced during the time-delay search process: ; in, The maximum allowable step size is preferably 0.1s; Through the above processing, the phase alignment of the measured load sequence on the time axis is achieved.

[0039] Based on the phase correction, and using the established inertial load model and friction load model, the current working condition is calculated. Compared with the benchmark condition The difference in dynamic loads under a unified phase coordinate system. Its expression is: ; in, For normalized phase variables; and These represent the inertial load component and the frictional load component, respectively.

[0040] After completing the load decomposition, phase correction and dynamic load residual calculation, the load sequence and displacement sequence are equivalently reconstructed to eliminate the influence of changes in production system parameters on the dynamometer card and realize the characterization of the dynamometer card under different working conditions. Based on the phase-aligned measured load sequence, an equivalent load sequence is constructed using the dynamic residual compensation method, and its expression is: ; in, Equivalent load sequence; The measured load is after phase correction; This represents the dynamic load residual between the current operating condition and the reference operating condition. This refers to the static load component or static load reference value corresponding to the current operating condition. This refers to the static load component or the static load value under the reference working condition after equivalent correction. By compensating for the dynamic load residuals and restoring the static load reference, the dynamic disturbance components caused by changes in stroke, stroke and pump depth can be effectively removed.

[0041] To address the elastic elongation effect of sucker rod strings under dynamic loads, a displacement correction model is constructed based on the mechanical properties of the rod string, and the original displacement sequence is modified accordingly. After correction, the equivalent displacement sequence is obtained, and its expression is: ; in, This is an equivalent displacement sequence; The elastic modulus of the rod / column material; The cross-sectional area of ​​the rod / column; The resonant frequency of the rod / column; Through the above corrections, displacement distortion caused by elastic deformation of the rod is compensated, and the displacement axis and load axis are synchronously normalized under a unified physical reference.

[0042] With equivalent displacement sequence For the horizontal axis, the equivalent load sequence Using the vertical axis, an equivalent dynamometer diagram is constructed to characterize the downhole operating conditions after eliminating the influence of production system parameters.

[0043] This scheme takes the equivalent restoration of the dynamometer card as its core. Through the decomposition of suspension load and compensation for dynamic load residuals, it corrects the amplitude, phase and shape distortion of the dynamometer card caused by changes in production system parameters, and realizes a unified equivalent representation of the dynamometer card under different operating conditions. This eliminates the interference of changes in stroke, pump depth and pumping depth on downhole condition identification, and improves the accuracy and reliability of condition identification.

[0044] Example 2; Based on the same inventive concept as the method for equivalent dynamic reduction of a pumping unit indicator diagram in the foregoing embodiments, the present invention also provides a system for equivalent dynamic reduction of a pumping unit indicator diagram, the system comprising: The data acquisition and alignment module acquires the suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit, and performs time alignment between the suspension point load sequence and the polished rod displacement sequence to generate the original dynamometer data. The feature extraction and analysis module extracts dynamometer feature parameters from the original dynamometer diagram data and production system parameters, and determines the difference in dynamometer diagram response between the current operating condition and the baseline operating condition based on the dynamometer diagram feature parameters. The load decomposition correction module decomposes the suspension point load sequence into static load components, inertial load components, and friction load components based on the dynamic relationship of the sucker rod string, and performs equivalent corrections on the static load components, inertial load components, and friction load components based on production system parameters and benchmark operating conditions. The phase correction and alignment module performs phase correction on the equivalent correction of the suspension point load sequence based on the load propagation characteristics in the sucker rod string, so as to obtain a phase-aligned load sequence corresponding to the reference working condition. The dynamic residual determination module determines the dynamic load residual between the current working condition and the reference working condition based on the phase-aligned load sequence and the equivalent corrected static load components, inertial load components, and friction load components. The load-displacement reconstruction module compensates the phase-aligned load sequence using dynamic load residuals to obtain an equivalent load sequence, and corrects the polished rod displacement sequence based on the elastic deformation relationship of the sucker rod string to obtain an equivalent displacement sequence. The equivalent dynamometer construction module constructs an equivalent dynamometer diagram using equivalent displacement sequences and equivalent load sequences to eliminate the influence of changes in production regime parameters on the amplitude, phase, and shape of the dynamometer diagram.

[0045] The adjustment system described above in this invention can effectively realize a method for equivalent dynamic restoration of the indicator diagram of an oil pumping unit, and the technical effects it can achieve are as described in the above embodiments, which will not be repeated here.

[0046] Example 3; Based on the same inventive concept as the method for equivalent dynamic restoration of the indicator diagram of an oil pumping unit in the foregoing embodiments, the present invention also provides a computer-readable storage medium storing a computer program, the computer program including program instructions, which, when executed by a processor, can realize the method for equivalent dynamic restoration of the indicator diagram of an oil pumping unit.

[0047] Example 4; Based on the above embodiments of this scheme, in one specific embodiment, the continuous production data of well A in a certain well group is selected as the analysis object. During the production parameter adjustment process of this well, the number of strokes... and stroke The pump depth increases synchronously. This remains unchanged, constituting a typical two-parameter adjustment scenario. First, the dynamometer card data of the pumping unit is collected and processed, and a baseline operating condition is constructed. Timing and operating conditions after parameter adjustment The eigenvector at time step 1.

[0048] Baseline operating conditions : Strike =3.0 rpm, stroke =3.0m, pump depth =1500m. Measured maximum load =71.85kN, minimum load =46.92kN, dynamometer area =158.12 kN·m.

[0049] Operating conditions after parameter adjustment : Strike =4.5rpm, stroke =4.5m, pump depth =1500m. Measured maximum load =90.63kN, minimum load =51.28kN, dynamometer area =200.45kN·m.

[0050] The load decomposition process is performed on the dynamometer diagram under the adjusted parameters. For example... Figure 2 As shown, the suspension point load is decomposed into static load components. Inertial load components and friction load component .

[0051] The Tikhonov regularization algorithm is used to solve for the load components, and the regularization coefficient is taken as follows: =0.05. The results show that the static load increased from 67.88kN to 68.15kN, the inertial load increased from 3.97kN to 21.48kN, and the friction load increased from 0 to 1.00kN.

[0052] Equivalent corrections were applied to each load component. Since the pump depth remained unchanged, the static load correction primarily considered the impact of stroke variation on the liquid column state, and the static load correction coefficient was calculated. =0.959, corresponding to static load correction amount =-2.80kN.

[0053] Inertial load correction uses a coupled correction function Calculations were performed, and the results were obtained. =1.0375, inertial load correction factor =3.502, corresponding to the inertial load correction amount =+9.91kN.

[0054] The friction load resistance model is modified, and the friction load correction amount is calculated. =+0.021kN.

[0055] Phase correction and residual calculation are performed on the load signal. Since the pump depth remains unchanged, the load propagation time delay remains constant, and the phase correction amount is taken. =0.

[0056] Under a unified phase coordinate system, the dynamic load residual is calculated to be: .

[0057] The load and displacement sequences are processed to be equivalent. Based on dynamic residual compensation, the load sequence is corrected to obtain the equivalent load sequence.

[0058] Based on this, and combined with the displacement correction results, an equivalent dynamometer diagram is constructed. The reconstructed equivalent maximum load is... 77.90kN, which is close to the maximum load of 71.85kN under the reference working condition.

[0059] like Figure 3 As shown, the equivalent indicator diagram shape is basically consistent with the reference indicator diagram, indicating that through load decomposition and dynamic residual compensation, the influence of stroke and stroke variation on the indicator diagram shape is effectively reduced, and a unified representation of the indicator diagram under different working conditions is achieved.

[0060] Example 5; Based on the above embodiments of this scheme, in a specific embodiment, in order to further verify the applicability of the method of the present invention under conditions of multiple parameter changes, dynamometer data of well B in a certain well group before and after the adjustment of the production system are selected for analysis.

[0061] Baseline operating conditions Operating conditions after parameter adjustment The production system parameters and indicator diagram characteristic parameters are as follows: Baseline operating conditions : Strike =2.5rpm, stroke =3.0m, pump depth =1650m, maximum load =68.52kN, minimum load =44.18kN, work area =145.28kN·m, active power 17.80kW, power factor 0.30.

[0062] Operating conditions after parameter adjustment : Strike =4.5rpm, stroke =4.0m, pump depth =1950m, maximum load =98.75kN, minimum load =52.63kN, dynamometer area =235.80kN·m, active power 38.50kW, power factor 0.35.

[0063] The comparison shows that after parameter adjustment, the load response and morphological characteristics of the indicator diagram changed significantly under the combined effects of changes in stroke count, stroke, and pump depth. This indicates that the adjustment of the production system has interfered with the original indicator diagram identification results.

[0064] The load was decomposed from the dynamometer diagram under the adjusted parameters to obtain the static load components. Inertial load components and friction load component .

[0065] The decomposition results show that with the changes in production system parameters, the static load, inertial load, and friction load all change to varying degrees. Specifically, the static load increases from 62.35 kN to 74.82 kN, the inertial load increases from 6.17 kN to 23.16 kN, and the friction load increases from approximately 0 kN to 0.77 kN.

[0066] Corrections were made for static load, inertial load, and friction load respectively, to obtain the static load correction factor. =1.167, static load correction =+10.41kN; Inertial load correction factor =4.654, inertial load correction amount =+22.58kN; Friction load correction amount =+0.024kN.

[0067] Since the pump depth changes in this embodiment, further phase correction is required. The optimal time delay parameters are calculated. The optimal time delay is determined using the cross-correlation method. =0.206s.

[0068] Under a unified phase coordinate system, the dynamic load residual is calculated to be: An equivalent load sequence is constructed based on the residual compensation results, and an equivalent dynamometer diagram is obtained by combining the displacement correction results.

[0069] like Figure 4 As shown, the equivalent restored indicator diagram is basically consistent with the reference working condition indicator diagram in terms of overall outline, load variation trend and key feature position, indicating that the method of the present invention can still effectively eliminate the influence of changes in production system parameters on the indicator diagram under the condition of changes in stroke, stroke and pump depth.

[0070] This embodiment shows that the method of the present invention is not only applicable to single or dual parameter variation scenarios, but also applicable to the equivalent restoration of indicator diagrams under multi-parameter coupled variation conditions.

[0071] Although this application has been described in conjunction with specific features and embodiments, it is obvious that various modifications and combinations can be made thereto without departing from the spirit and scope of this application. Accordingly, this specification and drawings are merely exemplary illustrations of the application as defined herein, and are to be considered as covering any and all modifications, variations, combinations, or equivalents within the scope of this application. Clearly, those skilled in the art can make various alterations and modifications to this application without departing from its scope. Thus, if such modifications and modifications fall within the scope of this application and its equivalents, this application intends to include such modifications and modifications.

Claims

1. A method for the dynamic equivalent reduction of an oil pumping unit's indicator diagram, characterized in that, The method includes: The suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit are obtained, and the suspension point load sequence and polished rod displacement sequence are time-aligned to generate the original indicator diagram data. Based on the original dynamometer diagram data and the production system parameters, extract the dynamometer diagram feature parameters, and determine the difference in dynamometer diagram response between the current operating condition and the baseline operating condition based on the dynamometer diagram feature parameters; Based on the dynamic relationship of the sucker rod string, the suspension point load sequence is decomposed into static load components, inertial load components, and friction load components, and the static load components, inertial load components, and friction load components are equivalently corrected based on the production system parameters and the reference operating conditions. Based on the load propagation characteristics in the sucker rod string, the phase correction is performed on the equivalently corrected suspension point load sequence to obtain a phase-aligned load sequence corresponding to the reference working condition. Based on the phase-aligned load sequence and the equivalently corrected static load component, inertial load component, and friction load component, determine the dynamic load residual between the current working condition and the reference working condition; The phase-aligned load sequence is compensated using the dynamic load residual to obtain an equivalent load sequence, and the polished rod displacement sequence is corrected according to the elastic deformation relationship of the sucker rod string to obtain an equivalent displacement sequence. An equivalent dynamometer diagram is constructed using the equivalent displacement sequence and the equivalent load sequence to eliminate the influence of changes in the production system parameters on the amplitude, phase, and shape of the dynamometer diagram.

2. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 1, characterized in that, Generate raw indicator diagram data, including: Real-time acquisition of the suspension point load sequence and the polished rod displacement sequence corresponding to the dynamometer diagram of the pumping unit; The production system parameters of the pumping unit are acquired synchronously, including the current stroke, current stroke length, and current pump depth. The suspension point load sequence and the optical rod displacement sequence are time-aligned to establish a correspondence between the suspension point load sequence and the optical rod displacement sequence under a unified time reference. The original indicator diagram data is determined based on the time-aligned suspension point load sequence and the rod displacement sequence.

3. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 2, characterized in that, Determining the difference in dynamometer response between the current operating condition and the baseline operating condition based on the dynamometer characteristic parameters includes: Extract the dynamometer area, maximum load, minimum load, and load amplitude from the original dynamometer data; The current stroke, current stroke length, and current pump depth are extracted based on the production system parameters. The feature vector for the current moment is constructed based on the suspension point load sequence, the rod displacement sequence, the dynamometer area, the maximum load, the minimum load, the load amplitude, the current stroke, the current stroke length, and the current pump depth. The dynamometer response characteristics under varying production system parameters are characterized by the feature vector, and the difference in dynamometer response between the current operating condition and the baseline operating condition is determined.

4. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 1, characterized in that, Based on the production system parameters and the baseline operating conditions, the static load component, the inertial load component, and the friction load component are equivalently corrected, including: Based on the dynamic mechanism of the sucker rod string, the suspension point load sequence is represented as the superposition of the static load component, the inertial load component, and the friction load component; The static load component, the inertial load component, and the friction load component are solved using the regularized least squares method. A regularization term is introduced into the regularized least squares method to constrain the variation patterns of the static load component, the inertial load component, and the friction load component. The regularization term makes the static load component relatively stable near the top dead center and bottom dead center, makes the inertial load component have the same phase characteristics as the system acceleration change, and makes the friction load component change in opposite directions during the upstroke and downstroke.

5. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 4, characterized in that, The equivalent correction to the static load component includes: The static load component is determined based on the weight of the sucker rod string and the liquid column load. The static load correction factor is determined based on the changes in the production system parameters relative to the baseline operating condition. The static load correction factor is used to standardize the liquid column load; The corrected static load component is determined based on the weight of the sucker rod string and the benchmarked liquid column load. The static load correction factor characterizes the influence of stroke frequency, pump depth, and fluid distribution variations on the liquid column load.

6. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 4, characterized in that, Equivalent corrections to the inertial load components include: Without considering the influence of higher-order elastic vibrations of the rod and column, the suspension point motion corresponding to the suspension point load sequence is approximated as simple harmonic motion; The inertial load components are established based on the inertial motion of the sucker rod string and the inertial motion of the following fluid column; A state operator is introduced to characterize the influence of the opening and closing states of the moving valve on the inertial motion of the liquid column; When the traveling valve is closed during the upstroke, the state operator characterizes the liquid column's participation in inertial motion along with the rod column; When the traveling valve opens during the downstroke, the state operator characterizes that the liquid column does not participate in inertial motion with the rod column; The inertial load component of the following liquid column is determined based on the state operator, the liquid column acceleration correction coefficient, and the suspension point motion acceleration function; The inertial load component is determined based on the inertial load component of the sucker rod string and the inertial load component of the following fluid column; The inertial load correction coefficient is determined based on the current stroke, the current stroke length, the current pump depth, the reference stroke, the reference stroke, the reference pump depth, and the coupling correction function. The inertial load components are normalized and corrected using the inertial load correction coefficient to obtain the corrected inertial load components. The coupling correction function is determined based on the offset of the stroke relative to the reference stroke, the offset of the stroke length relative to the reference stroke, and the offset of the lower pump depth relative to the reference lower pump depth. The second-order coupling coefficients in the coupling correction function are used to characterize the second-order coupling effects between stroke-stroke, stroke-down pump depth, and stroke-down pump depth, respectively.

7. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 4, characterized in that, The equivalent correction to the friction load component includes: The friction load components are established based on the lateral contact force between the rod and the tubing, the combined friction coefficient, the viscous drag coefficient, the inertial drag coefficient, and the rod's movement speed. The product of the comprehensive friction coefficient and the lateral contact force is determined as the contact friction term between the rod and the tubing; The product of the viscous resistance coefficient and the velocity of the rod is determined as the viscous resistance term; The inertial drag coefficient and the square of the rod's velocity are defined as the inertial drag term; The corrected friction load component is determined based on the contact friction term, the viscous resistance term, and the inertial resistance term.

8. The method for equivalent dynamic reduction of the indicator diagram of an oil pumping unit according to claim 1, characterized in that, Determining the dynamic load residual, the equivalent load sequence, the equivalent displacement sequence, and the equivalent indicator diagram based on the phase-aligned load sequence includes: The theoretical time delay interval for load signal propagation is determined based on the stress wave propagation velocity in the sucker rod string and the pump depth. A local search interval is constructed within the theoretical time delay interval, centered on the reference propagation delay; The optimal time delay parameter is determined by maximizing the cross-correlation function within the local search interval. The search process for the optimal delay parameter is constrained by the maximum allowable step size; The phase-aligned load sequence is obtained by performing phase correction on the suspension point load sequence based on the optimal time delay parameter. Under normalized phase variables, the dynamic load residual is calculated based on the inertial load component and the friction load component of the current working condition and the reference working condition; The phase-aligned load sequence is compensated using the dynamic load residual, and the static load reference is restored to obtain the equivalent load sequence; Based on the elastic modulus of the rod material, the cross-sectional area of ​​the rod, and the resonant frequency of the rod, elastic deformation compensation is performed on the displacement sequence of the optical rod to obtain the equivalent displacement sequence. The equivalent dynamometer diagram is constructed with the equivalent displacement sequence as the horizontal axis and the equivalent load sequence as the vertical axis.

9. A dynamic equivalent reduction system for the indicator diagram of an oil pumping unit, characterized in that, The system includes: The data acquisition and alignment module acquires the suspension point load sequence, polished rod displacement sequence, and production system parameters of the pumping unit, and performs time alignment between the suspension point load sequence and the polished rod displacement sequence to generate the original dynamometer data. The feature extraction and analysis module extracts dynamometer feature parameters from the original dynamometer diagram data and production system parameters, and determines the difference in dynamometer diagram response between the current operating condition and the baseline operating condition based on the dynamometer diagram feature parameters. The load decomposition correction module decomposes the suspension point load sequence into static load components, inertial load components, and friction load components based on the dynamic relationship of the sucker rod string, and performs equivalent corrections on the static load components, inertial load components, and friction load components based on production system parameters and benchmark operating conditions. The phase correction and alignment module performs phase correction on the equivalent correction of the suspension point load sequence based on the load propagation characteristics in the sucker rod string, so as to obtain a phase-aligned load sequence corresponding to the reference working condition. The dynamic residual determination module determines the dynamic load residual between the current working condition and the reference working condition based on the phase-aligned load sequence and the equivalent corrected static load components, inertial load components, and friction load components. The load-displacement reconstruction module compensates the phase-aligned load sequence using dynamic load residuals to obtain an equivalent load sequence, and corrects the polished rod displacement sequence based on the elastic deformation relationship of the sucker rod string to obtain an equivalent displacement sequence. The equivalent dynamometer construction module constructs an equivalent dynamometer diagram using equivalent displacement sequences and equivalent load sequences to eliminate the influence of changes in production regime parameters on the amplitude, phase, and shape of the dynamometer diagram.

10. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores a computer program, which includes program instructions that, when executed by a processor, can implement the method for equivalent dynamic restoration of the pumping unit indicator diagram as described in any one of claims 1-8.

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