Well drilling pipeline strength analysis method and system
By establishing a three-dimensional model and using finite element analysis methods, the problem of insufficient stress analysis in the design of the drilling pipeline system was solved, rapid verification and structural optimization were achieved, and the safety and efficiency of the drilling platform were improved.
Patent Information
- Application Number
- CN202510833052.5
- Authority / Receiving Office
- CN · China
- Patent Type
- Applications(China)
- Current Assignee / Owner
- Filing Date
- 2025-06-20
- Publication Date
- 2025-09-23
AI Technical Summary
The existing drilling pipeline system design lacks rapid stress analysis, resulting in long design verification time and the inability to achieve structural vibration control and stiffness optimization.
By adopting the methods of 3D model establishment, finite element model reconstruction, static analysis, modal analysis and dynamic spectrum analysis, stress analysis of the drilling pipeline system is carried out through finite element software, the support reaction forces of flanges and pipeline supports are output, and post-processing is performed to optimize the structure.
It enables the rapid establishment of pipeline stress analysis models, analysis of the static strength, modal and dynamic response of the pipeline system, optimization of the vibration control and stiffness of the structure, and ensuring the stability and reliability of the system.
Smart Images
Figure CN120688323A_ABST
Abstract
Description
Technical Field
[0001] The present invention relates to the technical field of drilling platform pipeline stress analysis, and in particular to a drilling pipeline strength analysis method and system thereof. Background Art
[0002] The drilling pipeline system is the heart of the entire drilling platform. To overcome resistance and maintain pressure balance downhole, the system's design pressure reaches as high as 15,000 PSI (pounds per square inch). The drilling pipeline system includes multiple systems, including the high-pressure mud system, high-pressure cement system, hydraulic system, choke and kill manifold, and nitrogen system. High-pressure mud pumps and cement pumps are among the most critical equipment. As the core of the drilling platform, such high pressures could paralyze operations or even cause a disaster if an accident occurs.
[0003] With the continuous increase in drilling depth and the continuous promotion of high-pressure jetting technology, drilling pipeline systems have become increasingly high-performance, high-stress systems. Therefore, it is necessary to conduct rapid and effective stress analysis of drilling pipeline systems to obtain reasonable pipeline layout and optimized support and hanger structures. In the past, drilling pipeline system design was mostly based on experience or reference to existing designs. New designs took a lot of time and effort to verify, resulting in a longer system development cycle.
[0004] Therefore, there is a need for a drilling pipeline strength analysis method and system that can quickly analyze pipeline stress, achieve structural vibration control and stiffness optimization. Summary of the Invention
[0005] The present invention aims to solve the defects of existing pipelines such as lack of stress analysis and long design verification time, and provides a drilling pipeline strength analysis method and system that can quickly analyze pipeline stress, realize structural vibration control and stiffness optimization.
[0006] The drilling pipe strength analysis method of the present invention comprises the following steps: S1. Establish a three-dimensional model of the drilling pipeline system; S2. Post-processing the three-dimensional model to extract three-dimensional model information of the drilling pipeline system; S3, assembling the three-dimensional model information; S4, reconstruct the finite element model for stress analysis; S5. Based on the preset finite element analysis factors, the finite element model is subjected to static analysis, modal analysis, and dynamic spectrum analysis. By analyzing the static strength, modal, and dynamic response of the drilling pipeline system, the natural frequency and vibration mode of the drilling pipeline system are obtained; and finally, the support reaction force of the flange and pipeline support is output for post-processing.
[0007] Furthermore: In S3, the verification methods used in the assembly process include coordinate comparison method, geometric topology inspection method and visual overlay method.
[0008] Further: in S5, if the static strength meets the preset requirements, modal analysis is performed; if the static strength does not meet the preset requirements, the finite element model is modified; if the dynamic strength meets the preset requirements, the flange and support reaction forces are output; if the dynamic strength does not meet the preset requirements, the finite element model is modified again.
[0009] Further: in S5, the static analysis includes calculating cold stress and hot stress, the calculation of the cold stress includes the axial stress caused by gravity and pressure; the calculation of the hot stress includes the stress generated by the action of displacement load.
[0010] Furthermore: the calculation formula of the cold stress is: (1); in: is the cold stress; F is the axial force generated by the continuous load; A is the cross-sectional area of the pipe; P is the design pressure; is the average diameter; t is the wall thickness of the tube; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by the continuous load, is the out-of-plane bending moment generated by the continuous load; Z is the bending section modulus, It is the basic allowable stress of the material at the operating temperature.
[0011] Furthermore: the calculation formula of the thermal stress is: (2); in: is thermal stress; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by thermal expansion load, is the out-of-plane bending moment caused by thermal expansion load; is the torque caused by thermal expansion load; Z is the bending section modulus; f is the reduction coefficient of pipeline displacement stress range, is the allowable stress of thermal stress, It is the basic allowable stress of the material at the installation temperature.
[0012] Further: in S5, the modal analysis includes: Modal analysis parameter setting: define material properties and boundary conditions in the finite element software, and set the mass matrix type; Solve the characteristic equation: The characteristic equation is: (3); Where [K] is the stiffness matrix, [MA] is the mass matrix, ω is the natural angular frequency, and {ϕ} is the mode shape vector; Result extraction: The software outputs the first N natural frequencies and corresponding vibration mode cloud diagrams, and displays the displacement distribution of each vibration mode through visualization tools.
[0013] Further: in S5, the dynamic spectrum analysis includes: Load definition sets the dynamic load type according to the actual working conditions and inputs the load spectrum; Parameter configuration: Set the time step, damping coefficient and load combination in the finite element module, and select the dynamic analysis method; Solving and post-processing: After performing the dynamic analysis, the stress time history curve, displacement response spectrum, and maximum dynamic stress value of the target node are extracted, and strength verification is performed.
[0014] The drilling pipeline strength analysis system of the present invention includes a three-dimensional model building module, a model information reading module, an assembly module and a finite element analysis module; The three-dimensional model building module is used to build a three-dimensional model of the drilling pipeline system to be analyzed; The model information reading module is used to extract the three-dimensional model information of the drilling pipeline system; The assembly module is used to assemble the read single pipeline and transmit it to the finite element analysis module; The finite element analysis module is used to reconstruct the three-dimensional model and perform static, modal and dynamic stress analysis.
[0015] The beneficial effects of the present invention are: The present invention provides a drilling pipeline strength analysis method and system. This system and method can rapidly establish a pipeline stress analysis model, analyze the static strength, modal, and dynamic response of the pipeline system, and obtain the system's natural frequency and mode shape, thereby achieving structural vibration control and stiffness optimization. Furthermore, based on the static analysis results, the overall deformation and stress of the system can be determined, verifying the stiffness and strength of the entire system. Furthermore, dynamic stress analysis can be performed on different systems to calculate their responses to transient or harmonic loads. Ultimately, the support reaction forces of the flange and pipeline support are output for post-processing and further strength verification of related accessories. BRIEF DESCRIPTION OF THE DRAWINGS
[0016] Figure 1 It is a flow chart of the drilling pipe strength analysis method; Figure 2 This is a flow chart of the drilling pipeline strength analysis method, taking the high-pressure mud pipeline of a certain type of drilling platform as an example; Figure 3 This is the vibration mode diagram of the pipeline at the first-order natural frequency of 6.3123Hz; Figure 4 This is the vibration mode diagram of the pipeline at the second-order natural frequency of 6.3895Hz; Figure 5 This is the vibration mode diagram of the pipeline at the third-order natural frequency of 6.4137 Hz; Figure 6 It is a schematic diagram of the force-time curve of the relief valve; Figure 7 This is a schematic diagram of using mass blocks and springs to simulate the simplest piping system. DETAILED DESCRIPTION
[0017] The following are only preferred specific embodiments of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or replacements that can be easily thought of by a person skilled in the art within the technical scope disclosed by the present invention should be included in the scope of protection of the present invention. The embodiments described below are only used to explain the present invention and cannot be interpreted as limiting the present invention. The scope of protection of the present invention should be based on the scope of protection of the claims. The embodiments of the present invention are described in detail below. In order to facilitate the description of the present invention and simplify the description, the technical terms used in the description of the present invention should be interpreted broadly, including but not limited to conventional replacement schemes not mentioned in this application, and also including direct implementation and indirect implementation.
[0018] Example 1 Combine Figure 1-Figure 7 This embodiment describes a drilling pipe strength analysis method disclosed in this embodiment, including the following steps: S1. Build a 3D model of the drilling pipeline system; use the API interface of 3D modeling software (such as CATIA, TRIBON) to access the model's geometric database through programming (such as Visual Basic) to identify components such as steel pipes, hoses, elbows, flanges, etc. in the pipeline system; Figure 1 shown.
[0019] S2. Post-process the 3D model to extract the 3D model information of the drilling pipeline system; extract relevant data based on the 3D model information of the drilling pipeline system, such as the spatial axis, outer diameter, wall thickness, starting point coordinates, and end point coordinates of the pipeline. The key parameters extracted for each component include: Steel pipe / hose: spatial axis (starting and ending point coordinates), outer diameter, wall thickness, material properties; Elbow: radius, start / end point coordinates; Flange: model, weight, sealing ring parameters; Valves / reducers / tees: connection location, size differences, weight; Pipe clamp / support: center point coordinates, material information.
[0020] The extracted 3D model information is then stored in a preset format (such as XML or CSV) to ensure data structure and facilitate subsequent assembly and analysis module calls.
[0021] S3, assembling the three-dimensional model information to form an assembled drilling pipeline system; To ensure the consistency between the assembly model and the original 3D model, the following verification methods are used in the assembly process: Coordinate comparison method: Compare the coordinates of the key nodes of the assembled model with the coordinates derived from the original model item by item. The error must be less than the set threshold (such as 0.1mm).
[0022] Geometric topology checking method: Use the geometric verification tools of the finite element analysis module (such as CATIA) to check the continuity of the pipeline, the matching of the connection points and the rationality of the support structure.
[0023] Visual overlay method: The assembly model and the original model are superimposed and displayed in 3D software, and the difference areas are distinguished by color, and the key parts and difference areas are manually reviewed.
[0024] S4. Reconstruct the finite element model for stress analysis. After the drilling pipeline system is assembled, use a special pipeline stress analysis software such as CAESARII to read the model data and reconstruct the finite element model for stress analysis. Figure 2 shown.
[0025] S5. Based on pre-set finite element analysis factors, the finite element model is subjected to static, modal, and dynamic spectrum analysis. By analyzing the static strength, modal, and dynamic response of the pipeline system, the natural frequency and mode shape of the drilling pipeline system are determined. By controlling the natural frequency of the drilling pipeline system, resonance events can be avoided, the system's dynamic response can be reduced, and the system's stability and reliability can be improved. By analyzing the mode shape, the modal form and vibration amplitude information of the drilling pipeline system can be obtained, thereby obtaining a force analysis of the drilling pipeline system. Finally, the support reaction forces of the flange and pipeline support are output for post-processing and further strength verification of related accessories.
[0026] If the static strength meets the preset requirements, modal analysis is performed; if the static strength does not meet the preset requirements, the finite element model is modified. If the dynamic strength meets the preset requirements, the flange and support reaction forces are output. If the dynamic strength does not meet the preset requirements, the finite element model is modified again. After the static and dynamic strength of the system meet the requirements, the pipeline accessories, such as flanges and supports, need to be designed, so the design loads need to be provided.
[0027] The static analysis includes calculation of cold stress and thermal stress. The cold stress mainly calculates the axial stress caused by gravity and pressure, and requires that it does not exceed : The cold stress is calculated using the following formula: (1); in: is the cold stress; F is the axial force generated by the continuous load; A is the cross-sectional area of the pipe; P is the design pressure; is the average diameter; t is the wall thickness of the tube; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by the continuous load, is the out-of-plane bending moment generated by the continuous load; Z is the bending section modulus, It is the basic allowable stress of the material at the hot operating temperature, which is taken as 345MPa here.
[0028] Thermal stress is generated by displacement loads such as thermal expansion, contraction, and additional displacement at endpoints. It is not directly balanced by external forces but is instead necessary to satisfy displacement constraints or the continuous deformation requirements of the pipeline itself. Thermal stress is self-limiting, meaning that local yielding or a small amount of deformation can satisfy the displacement constraints or the continuous deformation requirements, thus preventing further deformation. Generally speaking, as long as repeated loading is not applied, thermal stress will not cause pipeline damage. In other words, thermal stress primarily causes fatigue damage.
[0029] Thermal stress is calculated using the following formula: (2); in: is thermal stress; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by thermal expansion load, is the out-of-plane bending moment caused by thermal expansion load; is the torque caused by thermal expansion load; Z is the bending section modulus; f is the pipeline displacement stress range reduction factor. The design life of the platform is 20 years, and the maximum number of cycles is 7000. In this example, it is taken as 1.0. is the allowable stress of thermal stress, here we take , is the basic allowable stress of the material at the installation temperature, which is taken as 345MPa here.
[0030] The modal analysis includes: (1) Modal analysis parameter settings: Define material properties (elastic modulus, Poisson's ratio, density), boundary conditions (fixed support points), and set the mass matrix type (such as lumped mass matrix) in the finite element software.
[0031] (2) Solve the characteristic equation: Modal analysis is based on solving the following characteristic equation: (3); Where [K] is the stiffness matrix, [MA] is the mass matrix, ω is the natural angular frequency, and {ϕ} is the mode shape vector.
[0032] (3) Result extraction: The software outputs the first N natural frequencies (such as the first three 6.3123Hz, 6.3895Hz, 6.4137Hz) and the corresponding vibration mode cloud diagrams, and displays the displacement distribution of each vibration mode through visualization tools; Figure 3-Figure 5 shown.
[0033] When performing modal analysis, the mass point spacing needs to be reset. The concentrated mass spacing is determined according to the following formula: (4); Where: L is the distance between two consecutive concentrated masses; D is the outer diameter of the pipe; t is the wall thickness of the pipe; and w is the weight of the pipe per unit length.
[0034] The friction stiffness coefficient is set to 0, the cutoff frequency is 50Hz, and the maximum frequency order is set to 5. The calculation found that the natural frequencies of the first three orders are 6.3123Hz, 6.3895Hz and 6.4137Hz. Figure 3-Figure 5 , respectively showing the simulated vibration mode diagrams of the pipeline at the first three frequencies. Figure 3 At a frequency of 6.3123 Hz, it can be seen that the vibration amplitude of node 2710 in the Z direction is relatively large. Figure 4 At a frequency of 6.3895 Hz, it can be seen that the vibration amplitude of node 9130 in the Y direction is relatively large. Figure 5At a frequency of 6.4137 Hz, it can be seen that node 13120 has a relatively large vibration amplitude in the X direction. The green part represents the connector or valve.
[0035] After completing static and modal analysis, the load magnitude for the high-pressure mud system is calculated using existing formulas. This calculation is then applied to the corresponding elbow for analysis using specialized software such as CAESAR II. Dynamic analysis of the relief valve assembly is performed using existing dynamic analysis formulas. The calculated value is then applied to the corresponding position in the pipeline. The relief load magnitude is calculated based on the relief device parameters, and a spectrum and force group are generated. Combined operating conditions are then used for calculation to obtain dynamic stress analysis results.
[0036] The dynamic spectrum analysis includes: (1) Load definition Set the dynamic load type (such as transient impact, harmonic excitation) according to the actual working conditions, input the load spectrum (such as Figure 6 force-time curve or frequency-amplitude curve of the relief valve shown).
[0037] (2) Parameter configuration; In the finite element module, set the time step, damping coefficient (such as Rayleigh damping), load combination method (such as SRSS or CQC method), and select the dynamic analysis method (such as harmonic response analysis or transient dynamics analysis).
[0038] (3) Solution and post-processing; After performing the dynamic analysis, the stress time history curves, displacement response spectra, and maximum dynamic stress values of key nodes were extracted, and strength verification was performed in accordance with the ASME B31.3-2004 Process Piping Code.
[0039] Harmonic Response Analysis Example: For the harmonic load F(t)=F0sin(2πft), the system response is solved in the frequency domain: (5); Where [C] is the damping matrix and {X} is the displacement response vector.
[0040] The specific process of obtaining the natural frequency and vibration mode of the drilling pipeline system by analyzing the static strength, modal and dynamic response of the pipeline system is as follows: like Figure 7 As shown in the figure, the simplest piping system is simulated using mass blocks and springs, which are decomposed into two independent degrees of freedom oscillators whose vibration modes are periodic function 1 and periodic function 2. Figure 7 As shown. By appropriate system mass distribution and stiffness coefficients, the independent equations of dynamic motion can be written as functions of each independent periodic displacement:
[0041]
[0042] in: is the system mass of periodic function 1, ; is the system mass of periodic function 2; ; For mass block The acceleration of displacement with respect to time; For mass block The acceleration of displacement with respect to time; is the system stiffness coefficient of periodic function 1, ; is the system stiffness coefficient of periodic function 2, ; For mass block The displacement of with respect to time; For mass block The displacement of with respect to time; For mass block External loads; For mass block External loads; is the system load of periodic function 1 relative to time, ; is the system load of periodic function 2 relative to time, .
[0043] Using the above formula, solve the natural frequencies and normalized forms of all N vibration modes in the system.
[0044] Determine the constant that multiplies each modal response arrive These constants are the magnitudes of the external loads. The dynamic load coefficients are functions of the frequency of each mode that fits the DLF curve for the external loads and the contribution of each modal. Multiplying each vibration frequency by its coefficient yields the contribution of each individual modal. The sum of the individual modal responses yields the response of the entire system.
[0045]
[0046] in: is the equivalent static load vector generated by mode i; is the frequency The dynamic load factor of the oscillator; is the positive mass change form of mode i; is the system mass matrix; {F} is the external load vector.
[0047] Example 2 This embodiment is explained in conjunction with Example 1. This embodiment discloses a drilling pipeline strength analysis method. Taking the high-pressure mud pipeline of a certain type of drilling platform as an example, the specific implementation method of the present invention is further described in detail in conjunction with the accompanying drawings.
[0048] like Figure 2 As shown, the drilling pipeline strength analysis method described in this embodiment, that is, the process of CATIA data extraction → XML formatting → CAESAR II interface import, has the following specific steps: S1. Create a 3D model of the drilling pipeline high-pressure mud system. The pipeline system includes 16 steel pipes, three sections of flexible hose, three high-pressure mud pumps, and several elbows, flanges, valves, reducers, tees, and pipe clamps. Based on the principles and layout of the high-pressure mud system and the mud pump installation requirements, a complete 3D model was created in CATIA software, and the properties of the pipeline accessories were set.
[0049] S2. Post-process the 3D model, using the extraction module to extract 3D model information for the high-pressure slurry pipeline system. The outer diameters of the steel pipes are 168.3mm and 88.9mm, with wall thicknesses of 15.2mm and 21.9mm, respectively. The steel pipe material is A519 AISI 4130, the hose material is nitrile rubber, and the pipe clamps and supports are Q235. The elbows are 90-degree elbows according to ASME specifications, and the flanges are API standard butt weld joints with seals. The pressure is 10,000 PSI. Launch CATIA API, initialize the CATIA application, ensure CATIA is launched, and obtain a reference to the CATIA application. Open or reference an existing assembly document, iterate through all subassemblies in the assembly, extract geometric parameters, and access each component's geometry (such as shape and dimensions). If specific geometric information is required, access the part's Part document and further manipulate its features or shapes. Extract attribute parameters and access component parameters or user properties.
[0050] S3. Assemble the extracted 3D model information: The second step obtains information for each pipeline. Therefore, after all extraction is complete, all 16 pipelines must be assembled. This assembly is performed entirely according to the relative coordinates within the 3D model. To format the XML, you first need to define the XML structure, determine the root element and subelements, and define the tag name and possible attributes for each element. Then, fill in the data fields, adding the required data to the corresponding XML elements. The XML structure is written to a file to generate the XML document.
[0051] S4. Reconstruct the finite element model for stress analysis: Import the assembled model obtained in step 3 into the finite element analysis module to obtain a finite element 3D model suitable for analysis. Use the CAESAR II interface to import, read and parse the XML file, extract the required data fields, perform data mapping and conversion, map the data in the XML file to the format of the CAESAR II input file, perform necessary unit conversions or format adjustments, and generate the CAESAR II input file. Based on the mapped data, generate an input file that conforms to the CAESAR II format, ensuring that the file structure is correct and that the field order and format meet CAESAR II requirements. Import the generated input file into CAESAR II for verification, check that the model has loaded correctly, make any necessary adjustments, and complete the import.
[0052] S5. In the finite element analysis module, set the analysis reference standard to ASME B31.3, the design maximum temperature to 120°C, the minimum temperature to -29°C, and the operating temperature to 21.1°C. The design pressure is 10,000 PSI, and the accelerations in the X, Y, and Z directions are ax = 2.185 m / s², ay = 2.999 m / s², and az = 3.258 m / s², respectively. The pipe material is A519 AISI 4130, with a corrosion allowance of 3 mm, an elastic modulus E of 210,000 MPa, a medium density of 2200 kg / m³, and a Poisson's ratio of 0.3. Then, perform static, modal, and dynamic analyses on the finite element model.
[0053] Transient loads include discharge loads and water hammer loads. The water hammer load calculation formula is as follows:
[0054]
[0055] in: is the maximum value of the instantaneous load, ΔP is the interaction pressure in the pipeline ( - ),Depend on Figure 1 It can be seen that it is 500PSI (3.45MPa).
[0056] A is the internal cross-sectional area of the mud pipe; Q is the phase shift of the pressure peak between elbow a and elbow b; is the natural frequency of the mud pump; The time required for the pressure pulsation peak to move from elbow a to elbow b; =Len / c; Len is the straight pipe length between elbow a and elbow b; c is the speed of sound in the liquid; The calculated water hammer load is applied to the corresponding elbows in the pipeline, and then professional pipeline stress analysis software such as CAESARII is used to perform stress analysis and obtain the response.
[0057] Flanges: This is achieved using the WRC297, SIFS, and FLANGES submenus in CAESAR II software, using CNODES constraints and imposed forces or displacements. WRC297 is used to calculate local stresses at the interface between pipes and equipment; SIFS (Stress Intensification Factors) is used to assess stress concentrations at piping components (such as elbows and tees); the FLANGES submenu is used to perform stress analysis at pipe flange connections.
[0058] Support reaction force: achieved by reasonably setting constraints of six degrees of freedom.
[0059] Relevant components include flange strength and the strength of the supporting structure.
[0060] The flange strength can be checked using the following formula: ; ; in: is the total pressure, comparable to the allowable value of the American Flange Standard ASME B16.5, in pounds per square inch; P is the system design pressure in pounds per square inch; is the equivalent pressure produced by the pipe load in pounds per square inch; F is the axial force exerted by the pipe on the flange, in pounds; M is the bending moment of the pipe acting on the flange in inch-pounds; G is the diameter of the gasket to which the load acts, in inches; The strength of the supporting structure can be modeled and analyzed using finite element software such as Abaqus.
[0061] The Joukowsky equation is used to calculate the discharge load, where the pressure wave can be calculated as follows:
[0062] in The pressure increase caused by the instant opening of the valve; For the density of mud, 2200kg / m3 is used; is the speed of sound in the liquid, and its value can be calculated by the following formula:
[0063] is the bulk modulus of the mud, which is 2158 MPa. is the elastic modulus of the pipe, usually 204~287 MPa; is the average diameter of the pipe, 88.9 mm is used; For the wall thickness of the pipe, 15.24mm is used.
[0064] Reaction force of relief valve It can be calculated using the following formula:
[0065] is the dynamic amplification factor, A is the cross-sectional area of the pipeline, The flow rate of the liquid changes.
[0066] According to the opening and closing settings of the relief valve and the nodes of the pipeline, input the spectrum load of the force. For example: In the Y direction, point 210 is -1311 lbforceset#1; In the Y direction, point 310 is -1311 lb forceset #1; In the Y direction, point 410 is -1311 lbforceset#1; There will be a single dynamic load case containing force set #1.
[0067] Example 3 This embodiment is described in conjunction with Examples 1 and 2. This embodiment discloses a drilling pipe strength analysis system, which includes a three-dimensional model building module, a model information reading module, an assembly module, and a finite element analysis module. The three-dimensional model building module is used to build a three-dimensional model of the drilling pipeline system to be analyzed; The model information reading module is used to extract the three-dimensional model information of the drilling pipeline system; The assembly module is used to assemble the read single pipeline and transmit it to the finite element analysis module; The finite element analysis module is used to reconstruct the three-dimensional model and perform static, modal and dynamic stress analysis, which can be implemented using CAESARII, ANSYS, etc.
Claims
1. A drilling pipeline strength analysis method, characterized in that: The steps include: S1. Establish a three-dimensional model of the drilling pipeline system; S2. Post-processing the three-dimensional model to extract three-dimensional model information of the drilling pipeline system; S3, assembling the three-dimensional model information; S4, reconstruct the finite element model for stress analysis; S5. Based on the preset finite element analysis factors, the finite element model is subjected to static analysis, modal analysis, and dynamic spectrum analysis. By analyzing the static strength, modal, and dynamic response of the drilling pipeline system, the natural frequency and vibration mode of the drilling pipeline system are obtained; and finally, the support reaction force of the flange and pipeline support is output for post-processing.
2. A drilling pipe strength analysis method according to claim 1, characterized in that: In S3, the verification methods used in the assembly process include coordinate comparison, geometric topology checking, and visual overlay.
3. A drilling pipeline strength analysis method according to claim 1, characterized in that: In S5, if the static strength meets the preset requirements, modal analysis is performed; if the static strength does not meet the preset requirements, the finite element model is modified; if the dynamic strength meets the preset requirements, the flange and support reaction forces are output; if the dynamic strength does not meet the preset requirements, the finite element model is modified again.
4. A drilling pipe strength analysis method according to claim 1, characterized in that: In S5, the static analysis includes calculating cold stress and hot stress. The calculation of the cold stress includes the axial stress caused by gravity and pressure; the calculation of the hot stress includes the stress generated by the action of the displacement load.
5. A drilling pipe strength analysis method according to claim 4, characterized in that: The calculation formula of the cold stress is: （1）； in: is the cold stress; F is the axial force generated by the continuous load; A is the cross-sectional area of the pipe; P is the design pressure; is the average diameter; t is the wall thickness of the tube; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by the continuous load, is the out-of-plane bending moment generated by the continuous load; Z is the bending section modulus, It is the basic allowable stress of the material at the operating temperature.
6. A drilling pipe strength analysis method according to claim 4, characterized in that: The calculation formula of the thermal stress is: （2）； in: is thermal stress; is the stress intensification factor in the plane, is the out-of-plane stress intensification factor; is the in-plane bending moment caused by thermal expansion load, is the out-of-plane bending moment caused by thermal expansion load; is the torque caused by thermal expansion load; Z is the bending section modulus; f is the reduction coefficient of pipeline displacement stress range, is the allowable stress of thermal stress, It is the basic allowable stress of the material at the installation temperature.
7. A drilling pipeline strength analysis method according to claim 1, characterized in that: In S5, the modal analysis includes: Modal analysis parameter setting: define material properties and boundary conditions in the finite element software, and set the mass matrix type; Solve the characteristic equation: The characteristic equation is: （3）； Where [K] is the stiffness matrix, [MA] is the mass matrix, ω is the natural angular frequency, and {ϕ} is the mode shape vector; Result extraction: The software outputs the first N natural frequencies and corresponding vibration mode cloud diagrams, and displays the displacement distribution of each vibration mode through visualization tools.
8. A drilling pipeline strength analysis method according to claim 1, characterized in that: In S5, the dynamic spectrum analysis includes: Load definition sets the dynamic load type according to the actual working conditions and inputs the load spectrum; Parameter configuration: Set the time step, damping coefficient and load combination in the finite element module, and select the dynamic analysis method; Solving and post-processing: After performing the dynamic analysis, the stress time history curve, displacement response spectrum, and maximum dynamic stress value of the target node are extracted, and strength verification is performed.
9. A drilling pipeline strength analysis system, characterized in that: It includes 3D model building module, model information reading module, assembly module and finite element analysis module; The three-dimensional model building module is used to build a three-dimensional model of the drilling pipeline system to be analyzed; The model information reading module is used to extract the three-dimensional model information of the drilling pipeline system; The assembly module is used to assemble the read single pipeline and transmit it to the finite element analysis module; The finite element analysis module is used to reconstruct the three-dimensional model and perform static, modal and dynamic stress analysis.