Spring energy storage seal ring wear characteristic calculation method, system and device

Abstract

This invention discloses a method, system, and apparatus for calculating the wear characteristics of a spring-storage seal ring, comprising: S1: establishing a hybrid lubrication numerical model of the spring-storage seal to obtain a hybrid lubrication factor; S2: deforming a simple adhesive wear model based on the hybrid lubrication factor to obtain a wear calculation formula suitable for the spring-storage seal ring; S3: establishing a finite element model of the seal ring and the liquid slip ring based on the wear calculation formula, the geometric parameters and material properties of the spring-storage seal ring; S4: simulating the finite element model and plotting a wear displacement trend diagram; S5: analyzing the failure performance of the seal ring based on the wear displacement trend diagram and evaluation criteria to obtain the wear resistance performance level of the seal ring. This method for calculating the wear characteristics of a spring-storage seal ring achieves a closed-loop analysis from theoretical modeling to simulation verification, overcoming the problem that traditional empirical methods are difficult to accurately predict the wear behavior of seal rings under complex working conditions.

Description

Technical Field

[0001] This invention belongs to the field of seal performance calculation, and in particular relates to a method, system and device for calculating the wear characteristics of a spring energy storage seal ring. Background Technology

[0002] Wear of the spring accumulator seal is a significant factor leading to reduced or lost sealing performance. After a period of operation, the spring accumulator seal within a liquid slip ring typically wears down. The wear behavior of its inner lining material is highly complex and directly impacts the reliability and lifespan of the equipment. This wear not only affects the seal's service life but can also lead to leakage in the sealing system. Currently, researchers have conducted extensive wear studies on the sealing performance of accumulator spring seals based on basic wear calculation models. However, seal wear is influenced by many factors, including the hardness of the jacket material, the sliding distance, and operating conditions.

[0003] Therefore, it is necessary to comprehensively consider various factors, dynamically analyze the wear process of the spring-storage seal ring in the liquid slip ring, and design a practical research method for the wear characteristics of the seal ring by combining numerical models and finite element simulation. Based on this, a more scientific evaluation standard for wear resistance performance should be proposed to achieve an overall assessment of the sealing failure performance of the spring-storage seal ring. Summary of the Invention

[0004] To address the technical problem mentioned in the background art that the wear of spring energy storage seals not only affects the service life of the seals but may also lead to leakage in the sealing system, a method, system, and device for calculating the wear characteristics of spring energy storage seals are provided.

[0005] To achieve the above objectives, the specific technical solution of the spring energy storage sealing ring wear characteristic calculation method, system, and device of the present invention is as follows: A method for calculating the wear characteristics of a spring energy storage seal ring includes: S1: Establish a numerical model of hybrid lubrication for spring-energy-storing seals and obtain the hybrid lubrication factor; S2: Based on the aforementioned mixed lubrication factor, the simple adhesive wear model is modified to obtain a wear calculation formula suitable for spring energy storage seals; S3: Based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage seal ring, establish a finite element model of the seal ring and the liquid slip ring; S4: Simulate the finite element model and plot the wear displacement trend. S5: Based on the wear displacement change trend diagram and in conjunction with the evaluation criteria, analyze the failure performance of the sealing ring to obtain the wear resistance performance level of the sealing ring.

[0006] Further, step S1 includes: S11: The macroscopic contact pressure in the contact area is calculated based on the general average Reynolds equation with flow factor; S12: The rough peak contact pressure is obtained by solving the general average Reynolds equation using the finite difference method; S13: Calculate the mixed lubrication factor, where the lubrication factor is the ratio of the rough peak contact pressure to the macroscopic contact pressure of the contact area.

[0007] Further, step S11 includes: S111: Establishing a numerical model for mixed lubrication: Establish a Cartesian coordinate system: the X direction is the axial direction of the seal ring, the Y direction is the circumferential direction of the seal ring, and the Z direction is the oil film thickness direction. List the general average Reynolds equation with a flow factor: .

[0008] in, This refers to the dimensionless axial displacement of the sealing ring. The fluid pressure-flow factor in the axial direction of the sealing ring. The thickness is a dimensionless oil film. It is a dimensionless viscosity-pressure coefficient. For normal load, The cavitation index, For general variables, The period ratio, This refers to the dimensionless circumferential displacement of the sealing ring. The circumferential fluid pressure-flow factor of the sealing ring. The dimensionless circumferential linear velocity of the rotating axis. The dimensionless average oil film thickness; This refers to the fluid shear flow factor; S112: Set boundary conditions based on the cavitation region: , , in, For fluid pressure, For air-side pressure, For oil-side pressure, For dimensionless fluid density, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location; S113: Define dimensionless variables based on the cavitation region: in, For the axial displacement of the sealing ring, The length of one period in the X direction. This refers to the circumferential displacement of the sealing ring. The length of one period in the Y direction. For oil film thickness, The root mean square roughness of the sealing ring surface. The viscosity-pressure coefficient, The average oil film thickness, For fluid density, For reference fluid density, The rotational speed is the speed of the axis. For the viscosity of the sealing fluid; S114: Initial oil film thickness is obtained by linear regression fitting. Calculate the macroscopic contact pressure in the contact area. : in, The first linear coefficient, The second linear coefficient, The third linear coefficient, As the first intermediate quantity, The elastic modulus of the sealing ring material. It is Poisson's ratio.

[0009] Further, step S12 includes: S121: Assuming the sealing ring surface follows a Gaussian distribution, calculate the dimensionless average oil film thickness. in, It is the error function; S122: The contact pressure of the rough peak The expression is: in, For rough peak density, The radius of the spherical convex body is... It is the peak height of the sealing surface roughness. The probability density function of the distribution.

[0010] Further, step S2 includes: S21: Using the aforementioned hybrid lubrication factor to correct the Archard wear model, a deformed model is obtained: in, For the sealing ring Total wear of each node It is a mixed lubricating agent. The standard wear coefficient, For the sealing ring The wear depth of each node per unit time Δt For the sealing ring The radius of each node, For the first Contact stress at each node within Δt For the first The relative slip increment of each node within Δt The node ordinal number; S22: In finite element calculations, the time of each incremental step is... The wear calculation formula applicable to spring energy storage seals is obtained by modifying the deformation model: in, For the first The node at the th Total wear depth per increment step For the first The node at the th Contact stress in each incremental step, For the first The node at the th The relative slip of each incremental step, For the first The node at the th The wear depth per unit time Δt in each increment step, where n is the total number of increment steps. This is the increment step sequence number. .

[0011] Further, step S3 includes: performing material property empowerment, mesh generation, contact definition, boundary conditions and load application steps in the software Abaqus to obtain the mechanical response of the sealing ring under end-face sealing conditions, and obtain the finite element model.

[0012] Further, step S4 includes: S41: Perform contact stress analysis on the finite element model; S42: Obtain the node information of the finite element model; S43: Calculate the wear depth of the finite element model; S44: Adaptively update the wear node coordinates based on the ALE mesh; S45: Determine whether the wear time has been reached. If it has been reached, proceed to step S47. If it has not been reached, proceed to step S46. S46: Recalculate the contact stress and proceed to step S42; S47: Draw a trend diagram of wear displacement change based on the calculation results.

[0013] Further, step S5 includes: S51: Based on the wear displacement change trend diagram, the peak contact stress and the wear amount in 10 hours are obtained; S52: The wear resistance performance evaluation score of the sealing ring is obtained based on the peak contact stress and the wear amount over 10 hours; S53: Determine the wear resistance level of the sealing ring based on the wear resistance performance evaluation score.

[0014] A system for calculating the wear characteristics of a spring-storage seal ring, used to execute the above-mentioned method for calculating the wear characteristics of a spring-storage seal ring, includes: Hybrid lubrication factor calculation module: used to establish a hybrid lubrication numerical model for spring energy storage seals and obtain the hybrid lubrication factor; Model correction module: used to deform the simple adhesive wear model according to the mixed lubrication factor to obtain a wear calculation formula suitable for spring energy storage seals; Simulation module: used to establish finite element models of the sealing ring and the liquid slip ring based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage sealing ring; Calculation and plotting module: used to simulate the finite element model and plot the wear displacement trend. Result judgment module: used to analyze the failure performance of the sealing ring based on the wear displacement change trend diagram and evaluation criteria, and obtain the wear resistance performance level of the sealing ring.

[0015] An electronic device includes a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that the processor executes the computer program to implement the steps of the above-described method for calculating the wear characteristics of a spring energy storage seal.

[0016] The method for calculating the wear characteristics of spring-storage seals in this invention has the following advantages: It achieves a closed-loop analysis from theoretical modeling to simulation verification, overcoming the problem that traditional empirical methods or single experimental methods are insufficient to accurately predict the wear behavior of seals under complex operating conditions. By introducing a "hybrid lubrication factor" as a key bridge, the fluid lubrication state is coupled with the solid contact state, significantly improving the accuracy of wear prediction. The method is universally applicable, enabling rapid evaluation of spring-storage seals with different structural dimensions, material combinations, and operating conditions, providing a scientific basis for product design optimization. It supports nonlinear dynamic wear process simulation, reflecting the evolution of contact stress redistribution and wear accumulation during long-term service. Attached Figure Description

[0017] Figure 1 This is a flowchart of a method for calculating the wear characteristics of a spring energy storage seal ring provided by the present invention; Figure 2 This is a schematic diagram of a two-dimensional model of a spring-loaded energy storage sealing ring. Figure 3 This is a schematic diagram of the Abaqus wear subroutine co-simulation process; Figure 4 This is a graph showing the wear displacement variation trend according to an embodiment of the present invention; Figure 5 This is a structural block diagram of a spring energy storage sealing ring wear characteristic calculation system provided by the present invention; Figure 6 This is a schematic diagram of the structure of the electronic device provided by the present invention.

[0018] Explanation of markings in the diagram: 1. Plastic jacket; 2. Energy storage spring; 3. External components; 101. Mixed lubrication factor calculation module; 102. Model correction module; 103. Simulation module; 104. Calculation and plotting module; 105. Result judgment module; 810. Processor; 820. Communication interface; 830. Memory; 840. Communication bus. Detailed Implementation

[0019] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0020] In the description of this invention, it should be noted that the terms "center," "upper," "lower," "left," "right," "vertical," "horizontal," "inner," and "outer," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. They are used only for the convenience of describing the invention and for simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation. Therefore, they should not be construed as limitations on the invention. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance. The terms "first position" and "second position" refer to two different positions.

[0021] In the description of this invention, it should be noted that, unless otherwise explicitly specified and limited, the terms "installation," "connection," and "linking" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral connection; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; and they can refer to the internal connection of two components. Those skilled in the art can understand the specific meaning of the above terms in this invention based on the specific circumstances. Furthermore, the technical features involved in the different embodiments of this invention described below can be combined with each other as long as they do not conflict with each other.

[0022] Those skilled in the art will understand that although some embodiments herein include certain features included in other embodiments but not others, combinations of features from different embodiments are intended to be within the scope of the invention and form different embodiments. For example, in the claims, any of the claimed embodiments can be used in any combination.

[0023] The following is a reference to the appendix. Figure 1 To be continued Figure 6 This invention describes a method, system, and apparatus for calculating the wear characteristics of a spring energy storage seal ring.

[0024] Figure 1 A flowchart of a method for calculating the wear characteristics of a spring energy storage seal ring provided by the present invention includes: S1: Establish a numerical model of hybrid lubrication for spring-energy-storing seals and obtain the hybrid lubrication factor; S2: Based on the aforementioned mixed lubrication factor, the simple adhesive wear model is modified to obtain a wear calculation formula suitable for spring energy storage seals; S3: Based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage seal ring, establish a finite element model of the seal ring and the liquid slip ring; S4: Simulate the finite element model and plot the wear displacement trend. S5: Based on the wear displacement change trend diagram and in conjunction with the evaluation criteria, analyze the failure performance of the sealing ring to obtain the wear resistance performance level of the sealing ring.

[0025] This method for calculating the wear characteristics of spring-storage seals achieves a closed-loop analysis from theoretical modeling to simulation verification, overcoming the difficulty of accurately predicting seal wear behavior under complex operating conditions using traditional empirical or single experimental methods. By introducing a "hybrid lubrication factor" as a key bridge, coupling the fluid lubrication state with the solid contact state, the accuracy of wear prediction is significantly improved. The method is universally applicable, enabling rapid evaluation of spring-storage seals with different structural dimensions, material combinations, and operating conditions, providing a scientific basis for product design optimization. It supports nonlinear dynamic wear process simulation, reflecting the evolution of contact stress redistribution and wear accumulation during long-term service.

[0026] Specifically, step S1 includes: S11: The macroscopic contact pressure in the contact area is calculated based on the general average Reynolds equation with flow factor.

[0027] Establish a numerical model for hybrid lubrication: Establish a Cartesian coordinate system: the X direction is the axial direction of the seal ring, the Y direction is the circumferential direction of the seal ring, and the Z direction is the oil film thickness direction. List the general average Reynolds equation with a flow factor: in, This refers to the dimensionless axial displacement of the sealing ring. The fluid pressure-flow factor in the axial direction of the sealing ring. The thickness is a dimensionless oil film. It is a dimensionless viscosity-pressure coefficient. For normal load, For general variables, The period ratio, This refers to the dimensionless circumferential displacement of the sealing ring. The circumferential fluid pressure-flow factor of the sealing ring. The dimensionless circumferential linear velocity of the rotating axis. The dimensionless average oil film thickness; This refers to the fluid shear flow factor; Boundary conditions are set based on the cavitation region: , , in, For fluid pressure, For air-side pressure, For oil-side pressure, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location; In this embodiment of the invention, , , The calculation formula is: Define the dimensionless variable based on the cavitation region: in, For the axial displacement of the sealing ring, The length of one period in the X direction. This refers to the circumferential displacement of the sealing ring. The length of one period in the Y direction. For oil film thickness, The root mean square roughness of the sealing ring surface. The viscosity-pressure coefficient, The average oil film thickness, For dimensionless fluid density, For fluid density, For reference fluid density, The rotational speed is the speed of the axis. For the viscosity of the sealing fluid; Assuming the seal surface follows a Gaussian distribution, the dimensionless true average oil film thickness... for: in, Let be the error function, wherein the Gaussian error function is used in the embodiments of the present invention.

[0028] Assuming the initial oil film thickness is Linear regression can be used to fit the result: .

[0029] In the embodiments of the present invention: in, The first linear coefficient, The second linear coefficient, The third linear coefficient, As the first intermediate quantity, The elastic modulus of the sealing ring material. It is Poisson's ratio.

[0030] Understandably, dimensionless processing eliminates unit differences, improving algorithm stability and convergence speed. Setting reasonable cavitation boundary conditions (such as pressure continuity and density transition) more realistically reflects the process of oil film rupture and reformation at the sealing end face, avoiding errors caused by spurious high-pressure zones. Linear regression fitting of the initial oil film thickness solves the problem of uncertain initial conditions, accelerates numerical iteration convergence, and improves computational efficiency. Multivariate collaborative definition makes the model highly adaptable, applicable to sealing performance analysis under various speed, load, and temperature conditions.

[0031] S12: The rough peak contact pressure is obtained by solving the general average Reynolds equation using the finite difference method; This paper employs the finite difference method to solve the Reynolds equation. The contact region is discretized into a 20×20 grid, and the difference equation is solved using the relaxation iteration method. The oil film pressure at each grid node can be calculated from the pressures of its four adjacent nodes. The oil film pressure across the entire solution region is then iteratively updated based on boundary conditions. This process is repeated several times until the oil film pressure meets the convergence accuracy. At this point, the iteration terminates, and the final oil film pressure is output. .

[0032] relative accuracy Convergence criterion: in, Let m be the oil film pressure of the m-th network with network number (l, q), where m is the iteration number, l is the horizontal node number of the grid, and q is the vertical node number of the grid.

[0033] After solving the Reynolds equations for fluid flow, the pump suction rate can be calculated using the following equation. Pump suction rate per unit length of sealed area The calculation formula is: After dimensionless processing, we get: in, This is the dimensionless pump suction rate per unit length.

[0034] In the GW model, all contact roughness peaks are considered to have the same radius. A collection of spherical convex bodies, the height of which follows a Gaussian distribution, the rough peaks contact pressure The expression is: in, For rough peak density, The radius of the spherical convex body is... It is the peak height of the sealing surface roughness. The probability density function of the distribution.

[0035] It should be noted that the Gaussian distribution assumption aligns with the statistical regularities of the actual morphology of most machined surfaces, enhancing the model's realistic representativeness. The classic Greenwood-Williamson (GW) model is used to estimate the contact pressure at rough peaks, balancing computational efficiency and physical accuracy. An error function erf() is introduced to describe the probability integral within the oil film gap, enabling the statistical capture of the collective contact behavior of numerous micro-protrusions and avoiding the enormous computational overhead of modeling each one individually. This provides a concise and effective mathematical tool for quantifying "micro-contact forces" under mixed lubrication conditions.

[0036] S13: Calculate the mixed lubrication factor, where the lubrication factor is the ratio of the rough peak contact pressure to the macroscopic contact pressure of the contact area. The formula is: .

[0037] Specifically, step S2 includes: The stress values ​​at various points on the spring storage seal and the wear depth of the contact surface are closely related to the physical state during the wear process. The stress value changes with the wear depth at each point on the contact surface, thus causing changes in the wear degree of the guide rail contact surface. Therefore, the original Arcard model is no longer applicable to the dynamic wear process of the spring storage seal. To address this, assuming that the contact stress remains constant during the wear history per unit time, the wear region at the lip is discretized, and the lubrication factor is calculated using S1. This reflects the lubrication characteristics of the sealed area. The final formula is as follows: in, For the sealing ring Total wear of each node It is a mixed lubricating agent. The standard wear coefficient, For the sealing ring The wear depth of each node per unit time Δt For the sealing ring The radius of each node, For the first Contact stress at each node within Δt For the first The relative slip increment of each node within Δt The node ordinal number; Specifically, in finite element calculations, the time for each increment step is... The wear calculation formula applicable to spring energy storage seals is obtained by modifying the deformation model: in, For the first The node at the th Total wear depth per increment step For the first The node at the th Contact stress in each incremental step, For the first The node at the th The relative slip of each incremental step, For the first The node at the th The wear depth per unit time Δt in each increment step, where n is the total number of increment steps. This is the increment step sequence number. .

[0038] Understandably, the classic Archard wear model has been adapted by introducing a "hybrid lubrication factor" as a weighting coefficient to dynamically adjust the contribution ratio of the dry friction component, making the model applicable to partial lubrication and even boundary lubrication conditions. Wear depth is correlated with node-level contact stress and relative slip, and wear is gradually accumulated in incremental steps of the finite element method, achieving dynamic evolution simulation in the time domain. The formula is easily embedded into commercial software (such as Abaqus) secondary development interfaces, supporting multi-node, multi-step parallel computation, significantly improving engineering practicality. It can accurately identify local high-wear-risk areas (such as edge stress concentration areas), guiding structural optimization design.

[0039] After the wear calculation model is built in S2, the mechanical response of the sealing ring under end-face sealing conditions is obtained by performing steps such as material property empowerment, mesh generation, contact definition, boundary conditions and load application in Abaqus.

[0040] The energy storage spring sealing ring under static sealing conditions consists of a plastic jacket 1 and an energy storage spring 2, and its two-dimensional model is as follows: Figure 2 As shown, Figure 2 It also includes external component 3, and the structural parameters and dimensions of the energy storage spring sealing ring are shown in Table 1: Table 1 Structural parameters and dimensions of the energy storage spring sealing ring The inner lip is defined as the side of the sealing ring closer to the fixed end, and the outer lip is defined as the side closer to the rotating end. The sealing function is mainly borne by the outer lip. The sealing jacket is made of PTFE material, and the spring is made of stainless steel.

[0041] Regarding material properties, the sealing jacket is made of polytetrafluoroethylene (PTFE), which has a low coefficient of friction and self-lubricating properties, with an elastic modulus of 700 MPa and a Poisson's ratio of 0.48. The spring is made of stainless steel, with an elastic modulus E of 210 GPa and a Poisson's ratio of 0.3. The elastic modulus of the inner and outer rings of the fluid slip ring is much greater than that of the sealing ring material, and they are analyzed as equivalent to rigid bodies.

[0042] In terms of mesh generation, the C3D8R element with hourglass control enhancement is used for the mesh of each component. The approximate global size of the mesh is set to 0.1, with a total of 19625 elements. The element shape is a regular hexahedron, and the neutral axis algorithm is used to minimize mesh transition.

[0043] Regarding the contact definition, the contact algorithm of this method adopts the penalty function method (i.e., the Penalty function), the friction coefficient is selected as 0.02, and the contact surface is set as "face-to-face contact" and limited slip. The upper wall of the slip ring, the lower wall of the slip ring, and the contact surface between the slip ring and the root of the sealing ring are the "master surfaces", while the upper and lower lips of the sealing ring and the contact surface at the root of the sealing ring are the "secondary surfaces". The normal contact attribute is selected as "hard contact", and penetration between surfaces is prohibited.

[0044] Regarding boundary conditions and loading, a tie constraint is applied between the spring end face and the jacket, a full constraint is applied to the lower wall of the slip ring, and the upper wall of the slip ring is constrained in the X and Z directions. In the first analysis step, a displacement load of 0.2 mm is applied in the Y direction to complete the pre-compression and simulate the sealing ring assembly process. Then, a medium pressure of 20 MPa is applied to simulate the medium working condition of the sealing ring. Finally, an arc displacement about the y-axis is applied to the lower wall of the slip ring to simulate the sliding of the rotating end of the slip ring.

[0045] Specifically, step S4 includes: The contact stress of the nodes in the outer lip wear area was calculated based on the finite element model to obtain the contact stress of the nodes in the outer lip wear area under different running times. The changes in contact stress of the nodes in the outer lip wear area were calculated after running for 0 min, 30 min, 1 h, 2 h, 4 h, 6 h, 8 h, and 10 h.

[0046] By combining wear calculation formulas and secondary development of the Umeshmotion subroutine, and relying on ALE adaptive mesh technology, a dynamic simulation process of wear is realized. The wear amount of the spring energy storage seal ring within a fixed time period is calculated.

[0047] Abaqus defines node movement within an adaptive mesh domain using the Umeshmotion subroutine. The magnitude of this node movement is controlled by the wear calculation formula. This method utilizes Fortran and Visual Studio to write the subroutines. It defines matrices and constants using DIMENSION, extracts node information by calling the CALLGETVRMAVGATNODE program, identifies nodes on wear boundaries using the GETVRN statement, and defines the correct wear direction to prevent mesh distortion. Wear parameters are also set. The specific subroutine is as follows: Figure 3 As shown, it includes: S41: Perform contact stress analysis on the finite element model; S42: Obtain the node information of the finite element model; S43: Calculate the wear depth of the finite element model; S44: Adaptively update the wear node coordinates based on the ALE mesh; S45: Determine whether the wear time has been reached. If it has been reached, proceed to step S47. If it has not been reached, proceed to step S46. S46: Recalculate the contact stress and proceed to step S42; S47: Draw a trend diagram of wear displacement change based on the calculation results.

[0048] In ALE adaptive mesh control, select "Conventional Smoothing Algorithm," set the volume to 1, the original configuration projection to 0.5, the initial characteristic angle to 30°, and the transition characteristic angle to 30°. In the ALE adaptive mesh domain, set the frequency to 1 and the number of scans per increment to 3. In the ALE adaptive mesh constraints, set the outer lip as the wear boundary, the wear occurs in analysis step 2, and the motion to user-defined. When creating a new calculation task, select the user subroutine file in "General Settings."

[0049] The calculated contact stress results are written into the subroutine Umeshmotion to calculate the positional offset of the sealing ring surface nodes due to wear. Then, the ALE adaptive meshing technology in Abaqus is used to automatically re-divide the mesh elements on the nodes with positional offsets. After the incremental step ends, the contact stress in the wear area is recalculated. On this basis, the wear amount is recalculated, the wear node position is offset, the mesh is re-divided, and finally the wear time is reached, realizing the simulation of the wear of the sealing ring during the working process in the finite element method.

[0050] In Abaqus results files, ODB type files can store values ​​representing the wear rate variation process. By creating ODB variable outputs in the visualization module of the finite element simulation, selecting the slip CRISP and equivalent contact stress CPRESS, choosing the nodes to be analyzed based on node numbers, and finally exporting the entire process data to an Excel file using a Python script, a wear displacement variation trend graph can be plotted. The results are as follows... Figure 4 As shown.

[0051] Specifically, step S5 includes: S51: Based on the wear displacement change trend diagram, the peak contact stress and the wear amount in 10 hours are obtained; S52: The wear resistance performance evaluation score of the sealing ring is obtained based on the peak contact stress and the wear amount over 10 hours; S53: Determine the wear resistance level of the sealing ring based on the wear resistance performance evaluation score.

[0052] As the operating time of the sealing ring increases, the sealing ring jacket material gradually wears down, causing slight peeling or deformation on the surface of the contact area. This reduces the flatness of the bearing surface, leading to increased contact stress. Increased contact stress, in turn, increases wear. Therefore, the magnitude of the contact stress after a period of wear is an important standard for evaluating the material's wear resistance. Based on the above analysis and wear simulation results, this method uses the peak contact stress and wear amount after 10 hours of material wear as the standard to establish a sealing ring wear resistance evaluation system, as shown in Table 2. Table 2 presents the wear resistance performance scoring criteria: Table 2. Scoring Criteria for Wear Resistance Performance Define the wear resistance performance evaluation score for the seal: M = m1 + m2 In the formula: M is the evaluation score for the wear resistance performance of the sealing ring; m1 is the peak contact stress score of the sealing ring lip; m2 is the 10-hour wear score of the sealing ring. The wear resistance performance level of the sealing ring is evaluated by the value of M, and the evaluation criteria are shown in Table 3. Table 3 Evaluation Criteria for Wear Resistance Taking the sealing ring used in this method as an example, after the finite element analysis, the peak contact stress is 56.795 MPa and the wear is 0.04318. Then m1 is 2, m2 is 4, M=2+4=6, and the wear resistance performance level of the sealing ring under this parameter combination is level2.

[0053] like Figure 5 As shown below, a spring energy storage seal wear characteristic calculation device provided by the present invention will be described. The spring energy storage seal wear characteristic calculation device described below and the spring energy storage seal wear characteristic calculation method described above can be referred to in correspondence.

[0054] Hybrid lubrication factor calculation module 101: used to establish a hybrid lubrication numerical model of the spring energy storage seal and obtain the hybrid lubrication factor; Model correction module 102: used to deform the simple adhesive wear model according to the mixed lubrication factor to obtain a wear calculation formula suitable for spring energy storage seal ring; Simulation module 103: used to establish a finite element model of the sealing ring and the liquid slip ring based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage sealing ring; Calculation and plotting module 104: used to simulate the finite element model and plot the wear displacement change trend diagram; Result judgment module 105: is used to analyze the failure performance of the sealing ring based on the wear displacement change trend diagram and in combination with the evaluation criteria, and obtain the wear resistance performance level of the sealing ring.

[0055] Figure 6 An example is a schematic diagram of the physical structure of an electronic device, such as... Figure 6As shown, the electronic device may include: a processor 810, a communication interface 820, a memory 830, and a communication bus 840, wherein the processor 810, the communication interface 820, and the memory 830 communicate with each other via the communication bus 840. The processor 810 can call logical instructions in the memory 830 to execute a method for calculating the wear characteristics of a spring-loaded sealing ring, the method including: S1: Establish a numerical model of hybrid lubrication for spring-energy-storing seals and obtain the hybrid lubrication factor; S2: Based on the aforementioned mixed lubrication factor, the simple adhesive wear model is modified to obtain a wear calculation formula suitable for spring energy storage seals; S3: Based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage seal ring, establish a finite element model of the seal ring and the liquid slip ring; S4: Simulate the finite element model and plot the wear displacement trend. S5: Based on the wear displacement change trend diagram and in conjunction with the evaluation criteria, analyze the failure performance of the sealing ring to obtain the wear resistance performance level of the sealing ring.

[0056] Furthermore, the logical instructions in the aforementioned memory 830 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, or the part that contributes to the prior art, or a part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0057] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate. The components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs. Those skilled in the art can understand and implement this without any creative effort.

[0058] Through the above description of the embodiments, those skilled in the art can clearly understand that each embodiment can be implemented by means of software plus necessary general-purpose hardware platforms, and of course, it can also be implemented by hardware. Based on this understanding, the above technical solutions, in essence or the part that contributes to the prior art, can be embodied in the form of a software product. This computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute the methods described in the various embodiments or some parts of the embodiments.

[0059] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

[0060] It should be noted that the embodiments of this disclosure can be implemented using hardware, software, or a combination of both. The hardware portion can be implemented using dedicated logic; the software portion can be stored in memory and executed by a suitable instruction execution system, such as a microprocessor or dedicated-design hardware. Those skilled in the art will understand that the above-described devices and methods can be implemented using computer-executable instructions and / or included in processor control code, for example, such code provided on a programmable memory or a data carrier such as an optical or electronic signal carrier.

[0061] Furthermore, although the operation of the methods of this disclosure is described in a specific order in the accompanying drawings, this does not require or imply that these operations must be performed in that specific order, or that all the operations shown must be performed to achieve the desired result. Rather, the steps depicted in the flowcharts may be performed in a different order. Additionally or alternatively, certain steps may be omitted, multiple steps may be combined into one step, and / or one step may be broken down into multiple steps. It should also be noted that the features and functions of two or more devices according to this disclosure may be embodied in one device. Conversely, the features and functions of one device described above may be further divided and embodied by multiple devices.

[0062] While this disclosure has been described with reference to several specific embodiments, it should be understood that this disclosure is not limited to the specific embodiments disclosed. This disclosure is intended to cover various modifications and equivalent arrangements included within the spirit and scope of the appended claims.

Claims

1. A method of calculating spring-energized seal wear characteristics, characterized by, include: S1: Establish a numerical model of hybrid lubrication for spring-energy-storing seals and obtain the hybrid lubrication factor; S2: Based on the aforementioned mixed lubrication factor, the simple adhesive wear model is modified to obtain a wear calculation formula suitable for spring energy storage seals; S3: Based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage seal ring, establish a finite element model of the seal ring and the liquid slip ring; S4: Simulate the finite element model and plot the wear displacement trend. S5: Based on the wear displacement change trend diagram and in conjunction with the evaluation criteria, analyze the failure performance of the sealing ring to obtain the wear resistance performance level of the sealing ring.

2. The spring-energized seal wear characteristic calculation method of claim 1, wherein, Step S1 includes: S11: The macroscopic contact pressure in the contact area is calculated based on the general average Reynolds equation with flow factor; S12: The rough peak contact pressure is obtained by solving the general average Reynolds equation using the finite difference method; S13: Calculate the mixed lubrication factor, where the lubrication factor is the ratio of the rough peak contact pressure to the macroscopic contact pressure of the contact area.

3. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 2, characterized in that, Step S11 includes: S111: Establishing a numerical model for mixed lubrication: Establish a Cartesian coordinate system: the X direction is the axial direction of the seal ring, the Y direction is the circumferential direction of the seal ring, and the Z direction is the oil film thickness direction. List the general average Reynolds equation with a flow factor: ； in, This refers to the dimensionless axial displacement of the sealing ring. The fluid pressure-flow factor in the axial direction of the sealing ring. The thickness is a dimensionless oil film. It is a dimensionless viscosity-pressure coefficient. For normal load, The cavitation index, For general variables, The period ratio, This refers to the dimensionless circumferential displacement of the sealing ring. The circumferential fluid pressure-flow factor of the sealing ring. The dimensionless circumferential linear velocity of the rotating axis. The dimensionless average oil film thickness; This refers to the fluid shear flow factor; S112: Set boundary conditions based on the cavitation region: ， ， in, For fluid pressure, For air-side pressure, For oil-side pressure, For dimensionless fluid density, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location, for Liquid pressure at the location; S113: Define dimensionless variables based on the cavitation region: in, For the axial displacement of the sealing ring, The length of one period in the X direction. This refers to the circumferential displacement of the sealing ring. The length of one period in the Y direction. For oil film thickness, The root mean square roughness of the sealing ring surface. The viscosity-pressure coefficient, The average oil film thickness, For fluid density, For reference fluid density, The rotational speed is the speed of the axis. For the viscosity of the sealing fluid; S114: Initial oil film thickness is obtained by linear regression fitting. Calculate the macroscopic contact pressure in the contact area. : in, The first linear coefficient, The second linear coefficient, The third linear coefficient, As the first intermediate quantity, The elastic modulus of the sealing ring material. It is Poisson's ratio.

4. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 3, characterized in that, Step S12 includes: S121: Assuming the sealing ring surface follows a Gaussian distribution, calculate the dimensionless average oil film thickness. in, It is the error function; S122: Contact pressure of the rough peak The expression is: in, For rough peak density, The radius of the spherical convex body is... It is the peak height of the sealing surface roughness. The probability density function of the distribution.

5. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 1, characterized in that, Step S2 includes: S21: Using the aforementioned hybrid lubrication factor to correct the Archard wear model, a deformed model is obtained: in, For the sealing ring Total wear of each node It is a mixed lubricating agent. The standard wear coefficient, For the sealing ring The wear depth of each node per unit time Δt For the sealing ring The radius of each node, For the first Contact stress at each node within Δt For the first The relative slip increment of each node within Δt The node ordinal number; S22: In finite element calculations, the time of each incremental step is... The wear calculation formula applicable to spring energy storage seals is obtained by modifying the deformation model: in, For the first The node at the th Total wear depth per increment step For the first The node at the th Contact stress in each incremental step, For the first The node at the th The relative slip of each incremental step, For the first The node at the th The wear depth per unit time Δt in each increment step, where n is the total number of increment steps. This is the increment step sequence number. .

6. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 1, characterized in that, Step S3 includes: performing material property empowerment, mesh generation, contact definition, boundary conditions and load application steps in the software Abaqus to obtain the mechanical response of the sealing ring under end face sealing conditions, and obtain the finite element model.

7. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 1, characterized in that, Step S4 includes: S41: Perform contact stress analysis on the finite element model; S42: Obtain the node information of the finite element model; S43: Calculate the wear depth of the finite element model; S44: Adaptively update the wear node coordinates based on the ALE mesh; S45: Determine whether the wear time has been reached. If it has been reached, proceed to step S47. If it has not been reached, proceed to step S46. S46: Recalculate the contact stress and proceed to step S42; S47: Draw a trend diagram of wear displacement change based on the calculation results.

8. The method for calculating the wear characteristics of a spring energy storage seal ring according to claim 1, characterized in that, Step S5 includes: S51: Based on the wear displacement change trend diagram, the peak contact stress and the wear amount in 10 hours are obtained; S52: The wear resistance performance evaluation score of the sealing ring is obtained based on the peak contact stress and the wear amount over 10 hours; S53: Determine the wear resistance level of the sealing ring based on the wear resistance performance evaluation score.

9. A system for calculating the wear characteristics of a spring-storage seal ring, used to execute the method for calculating the wear characteristics of a spring-storage seal ring as described in any one of claims 1 to 8, characterized in that, include: Hybrid lubrication factor calculation module: used to establish a hybrid lubrication numerical model for spring energy storage seals and obtain the hybrid lubrication factor; Model correction module: used to deform the simple adhesive wear model according to the hybrid lubrication factor to obtain a wear calculation formula suitable for spring energy storage seals; Simulation module: used to establish finite element models of the sealing ring and the liquid slip ring based on the wear calculation formula, the geometric parameters and material properties of the spring energy storage sealing ring; Calculation and plotting module: used to simulate the finite element model and plot the wear displacement trend. Result judgment module: used to analyze the failure performance of the sealing ring based on the wear displacement change trend diagram and evaluation criteria, and obtain the wear resistance performance level of the sealing ring.

10. An electronic device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the method for calculating the wear characteristics of a spring energy storage seal ring as described in any one of claims 1 to 8.

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