Sliding bearing life evaluation method, system and equipment and storage medium

Abstract

The invention discloses a sliding bearing life evaluation method, system and device and a storage medium, and the method comprises the steps: solving the maximum oil film pressure and maximum shear stress under each working condition based on a fluid lubrication calculation model, carrying out the whole-cycle damage accumulation evaluation through a Miner rule, and calculating the material fatigue life of a sliding bearing; solving an axis track of the sliding bearing in each start-stop working period based on a fluid lubrication calculation model, and calculating the abrasion loss in each period by utilizing an Archard sliding abrasion model according to the axis track; on the basis of accumulation of a fluid lubrication calculation model and the abrasion loss, the bearing capacity and the bearing stability of the bearing during partial abrasion are calculated, and the abrasion life of the sliding bearing is obtained; comparing the wear life of the sliding bearing with the material fatigue life of the sliding bearing, and determining the life of the sliding bearing. The method can accurately predict the service life of the sliding bearing under the frequent start-stop working condition, and provides a scientific basis for maintenance, overhaul and replacement of equipment.

Description

Technical Field

[0001] This invention belongs to the field of sliding bearing performance testing, and relates to a method, system, equipment and storage medium for assessing the life of sliding bearings. Background Technology

[0002] Sliding bearings are characterized by high operating speed, good stability, good vibration resistance, large load capacity, low noise, and long service life. They are widely used in high-speed, high-precision, and heavy-load industrial fields, playing a vital role in ensuring the stable operation of industrial production and improving product quality.

[0003] As modern machinery develops towards greater complexity, precision, and speed, the operating conditions of sliding bearings are becoming increasingly demanding. Under fluid lubrication, the sliding journal and bearing surfaces are completely separated by lubricating oil, preventing direct contact and significantly reducing friction and wear, ensuring efficient operation and long lifespan. However, in actual operation, especially during start-up and shutdown, the lubricating oil film is not fully formed, and the lack of effective lubrication isolation between the journal and bearing surfaces makes direct contact highly likely, leading to wear. While the amount of wear during start-up and shutdown may be relatively small each time, its long-term accumulation can have a significant impact on bearing performance. Under harsh operating conditions, bearings may wear and degrade under radial loads. As operating time increases, wear accumulates, and when it reaches a certain level, the sliding bearing will be unable to function properly, resulting in the loss of some or all of its functionality. As a critical component in a mechanical system, the loss of function of the sliding bearing directly affects the safety and stability of the entire system, leading to equipment failure, production interruption, and even serious safety accidents. Therefore, predicting the lifespan of sliding bearings is of great significance for their application. Summary of the Invention

[0004] The purpose of this invention is to provide a method, system, device, and storage medium for assessing the life of sliding bearings, thereby solving the problem that existing technologies cannot accurately predict the life of sliding bearings.

[0005] To achieve the above objectives, the present invention employs the following technical solution: A method for assessing the life of a sliding bearing includes: Based on the fluid lubrication calculation model, the maximum oil film pressure and maximum shear stress under various working conditions are solved. The Miner rule is used to perform full-cycle damage accumulation assessment and calculate the material fatigue life of the sliding bearing. The shaft center trajectory of the sliding bearing in each start-stop working cycle is solved based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. Based on the fluid lubrication calculation model and the accumulation of wear, the bearing load capacity and bearing stability when partial wear occurs are calculated, and the wear life of the sliding bearing is obtained. The life of a sliding bearing is determined by comparing its wear life with its material fatigue life.

[0006] Furthermore, the total damage over the entire life cycle is represented by the total damage rate after operation over the entire life cycle. The total damage rate after operation over the entire life cycle is:

[0007] in, The total damage rate after operation over the entire life cycle. , The number of stress applications corresponding to each working condition. , This represents the number of stress applications required for failure under maximum stress in each working condition.

[0008] Furthermore, the number of stress applications required for failure under maximum stress under each working condition is:

[0009] in, For parameters related to materials, for The number of cycles required for material failure under symmetrical cyclic stress. This refers to the stress amplitude;

[0010] in, For maximum oil film pressure, This represents the maximum oil film shear stress.

[0011] Furthermore, the calculation process for the shaft center trajectory within each start-stop working cycle is as follows: Given the initial parameters at the starting point, calculate the initial oil film thickness, add it to the cumulative wear amount to obtain the actual oil film thickness, and substitute it into the transient Reynolds equation to iteratively solve for the oil film pressure; Replace the extrusion term with the velocity at that moment, calculate the oil film force from the oil film pressure, calculate the contact force based on the actual oil film thickness and bearing surface quality, and calculate the lubricating oil friction force based on the oil film pressure; Based on the oil film force, contact force, and lubricating oil friction, calculate the resultant force on the journal, substitute it into the equation of motion to obtain the acceleration, and calculate the position and velocity at the next moment.

[0012] Furthermore, the amount of wear is expressed as oil film thickness:

[0013] in, The initial oil film thickness. , This represents the relative position of the axis center at time t. These are the angular coordinates of each position in a cylindrical coordinate system. Let be the axial coordinates of each position in the cylindrical coordinate system. Where c is the number of starts and stops, and c is the radius gap. This represents the cumulative amount of wear and tear.

[0014] Furthermore, the wear amount per cycle is:

[0015] in, This represents the amount of wear accumulated within a time step. The wear coefficient is... For journals and bearings, the hardness of the softer material is... To contact pressure, The linear velocity of the journal surface. For time steps.

[0016] Furthermore, the bearing's load-bearing capacity and stability when partial wear occurs are determined by the overall stiffness of the bearing oil film, which is:

[0017] in, For the overall stiffness of the bearing oil film, Indicates the stiffness of the bearing. Indicates the damping of the bearing. , , , , , , and These are all dynamic characteristics of bearings.

[0018] A sliding bearing life assessment system, comprising: The fatigue module is used to solve the maximum oil film pressure and maximum shear stress under various working conditions based on the fluid lubrication calculation model, and to perform full-cycle damage accumulation assessment using the Miner's rule to calculate the material fatigue life of the sliding bearing. The wear module is used to solve the shaft center trajectory of the sliding bearing in each start-stop working cycle based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. The calculation module is used to calculate the bearing capacity and bearing stability when partial wear occurs based on the fluid lubrication calculation model and the accumulation of wear amount, and to obtain the wear life of the sliding bearing. The comparison module is used to compare the wear life of the sliding bearing with the material fatigue life of the sliding bearing to determine the life of the sliding bearing.

[0019] A terminal device includes a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement the steps of the method.

[0020] A computer-readable storage medium storing a computer program that, when executed by a processor, implements the steps of the method.

[0021] Compared with the prior art, the present invention has the following beneficial effects: This invention provides a method for assessing the life of sliding bearings. It calculates the bearing's axis trajectory during each start-stop cycle using a fluid lubrication calculation model, and calculates the wear amount in each cycle based on the Archard sliding wear model. Based on the accumulated wear amount and the fluid lubrication model, it calculates the bearing's load-bearing capacity and stability when partial wear occurs, thus obtaining the bearing's wear life. Furthermore, it calculates the oil film pressure, contact pressure, and shear stress during each start-stop cycle using the fluid lubrication calculation model, and uses Miner's rule to perform a full-cycle damage cumulative life assessment, calculating the bearing's material fatigue life. By comparing the bearing's wear life and material fatigue life, the bearing's lifespan is determined. This invention can accurately predict the lifespan of sliding bearings under frequent start-stop conditions. Effective lifespan prediction allows for advance understanding of the bearing's performance status and service life, providing a scientific basis for equipment maintenance, repair, and replacement. This enables rational production planning, avoids production accidents caused by sudden bearing failures, improves equipment reliability and production efficiency, and reduces maintenance costs and safety risks. Attached Figure Description

[0022] To more clearly illustrate the technical solutions of the embodiments of the present invention, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of the present invention and should not be regarded as a limitation on the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0023] Figure 1 This is a schematic diagram illustrating the frequent start-stop operation of the present invention.

[0024] Figure 2This is a flowchart of the sliding bearing life assessment method of the present invention.

[0025] Figure 3 This is a flowchart of the calculation process for the sliding bearing life assessment method of the present invention.

[0026] Figure 4 This is a flowchart of the fatigue life calculation process of the present invention.

[0027] Figure 5 This is a flowchart of the wear calculation process for a single start-stop cycle according to the present invention.

[0028] Figure 6 This is a schematic diagram showing the wear location and morphology of the present invention.

[0029] Figure 7 This is a circumferential distribution diagram of the oil film pressure at the point of maximum oil film pressure according to the present invention.

[0030] Figure 8 This is a diagram showing the axial force of the present invention.

[0031] Figure 9 shows the single wear amount and cumulative wear amount under multiple start-stop cycles in Embodiment 1 of the present invention, wherein Figure (a) is the wear amount of a single start-stop cycle and Figure (b) is the cumulative wear amount.

[0032] Figure 10 shows the nonlinear shaft center trajectory of the bearing of the present invention, wherein Figure (a) is the shaft center trajectory in the stable state and Figure (b) is the shaft center trajectory in the unstable state.

[0033] Figure 11 This is a diagram showing the oil film thickness after wear in Embodiment 1 of the present invention.

[0034] Figure 12 This is a diagram of the oil film pressure after wear in Embodiment 1 of the present invention.

[0035] Figure 13 This is a diagram of the shaft center trajectory during the 47,000th startup in Embodiment 1 of the present invention.

[0036] Figure 14 This is a schematic diagram of the structure of a sliding bearing life assessment system according to a preferred embodiment of the present invention.

[0037] Figure 15 This is a schematic diagram of the electronic device structure according to a preferred embodiment of the present invention. Detailed Implementation

[0038] The following description, in conjunction with the accompanying drawings, illustrates exemplary embodiments of this application, including various details to aid understanding. These should be considered merely exemplary. Therefore, those skilled in the art will recognize that various changes and modifications can be made to the embodiments described herein without departing from the scope and spirit of this application. Similarly, for clarity and brevity, descriptions of well-known functions and structures are omitted in the following description.

[0039] Obviously, the described embodiments are only some, not all, of the embodiments in this application. All other embodiments obtained by those skilled in the art based on the embodiments in this application without inventive effort are within the scope of protection of this application.

[0040] It should be noted that the terminals involved in the embodiments of this application may include, but are not limited to, mobile phones, personal digital assistants (PDAs), wireless handheld devices, tablet computers, personal computers (PCs), MP3 players, MP4 players, wearable devices (e.g., smart glasses, smartwatches, smart bracelets), smart home devices, and other smart devices.

[0041] Furthermore, the term "and / or" in this article is merely a description of the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A existing alone, A and B existing simultaneously, or B existing alone. Additionally, the character " / " in this article generally indicates that the preceding and following related objects have an "or" relationship.

[0042] The present invention will now be described in further detail with reference to the accompanying drawings: See Figures 1 to 3 This invention provides a method for evaluating the life of sliding bearings, which mainly considers two lifespans corresponding to three failure modes of sliding bearings: the wear lifespan corresponding to failure caused by insufficient load-bearing capacity or instability due to partial wear of the bearing, and the fatigue lifespan corresponding to fatigue failure of the material surface when the bearing wear is small but the working time is long.

[0043] The actual bearing life calculation process mainly consists of three parts: fatigue life calculation, bearing wear calculation, and bearing wear life calculation after partial wear. Details of each part are described below, and the relationships between them are as follows: Since fatigue life calculation is relatively quick, fatigue life is calculated first; then the cumulative wear under multiple start-stop cycles is calculated; next, the bearing load capacity and stability under existing wear are evaluated. If the load capacity or stability requirements are not met, the bearing is considered to have failed due to wear; finally, fatigue life and wear life are compared, and the smaller value is the final bearing life.

[0044] Specifically, the following steps are included: Step 1: Calculate fatigue life T1, such as Figure 4 As shown, the maximum oil film pressure of the sliding bearing under various operating conditions is solved based on the fluid lubrication calculation model. with maximum shear stress And calculate the stress amplitude. The Miner's law is used to assess the cumulative lifespan of damage throughout the entire lifecycle, and the number of cycles is obtained based on the rotational speed and operating time under various actual working conditions. The material undergoes The total damage rate suffered by the material in the second cycle was The total damage rate D of the bearing material after operating for its entire life cycle is obtained by summing the damage rates of all operating conditions. When the damage rate reaches 1, the bearing is considered to have undergone fatigue failure. If fatigue failure occurs, the number of cycles at this point is the fatigue life T1.

[0045] When a radial sliding bearing with round bearing shells is operating under normal conditions, the lubricating oil film is sufficient to completely separate the bearing shell and journal surfaces, thus theoretically preventing wear and resulting in an infinitely long theoretical lifespan. However, the materials on the bearing shell and journal surfaces are continuously subjected to the periodic action of the oil film force. For example, in a bearing where the journal rotates and the bearing shell is stationary, the materials on the surface of the journal, especially those at the center, undergo a similar process with each rotation of the journal. Figure 7 The pressure change process shown represents the stress amplitude at the maximum oil film pressure. The combined periodic action of oil film pressure and oil film shear stress can lead to fatigue failure of the surface material, especially under high loads and high speeds, where the large surface stress and high operating frequency can cause rapid fatigue failure.

[0046] The specific calculation process is as follows: The lifespan of the material at the most dangerous location is taken as the lifespan of the entire bearing. Fatigue life is checked at the most dangerous location. The location with the maximum stress amplitude is at the maximum oil film stress, and the location with the maximum shear stress is at the minimum oil film thickness. That is, the stress amplitude at the most dangerous location is taken as the stress amplitude at the most dangerous location for pulsating cyclic stress life check.

[0047] According to the third strength theory, the combined stress amplitude of oil film pressure and oil film shear stress is:

[0048] in, For maximum oil film pressure, This represents the maximum oil film shear stress.

[0049] According to stress amplitude The Miner criterion is used to verify the fatigue life of sliding bearing materials. The material damage rate is assumed to be D, and failure is considered to occur when D=1. Under stress... For a material to break under such conditions, it needs to undergo a certain number of cycles. According to the linear fatigue cumulative damage theory, the material undergoes... The total damage the material suffered after the next cycle was And so on, the material at stress levels The material requires a certain number of cycles to fail under the influence of the action. The material undergoes The total damage rate suffered by the material in the second cycle was .

[0050] Since the start-stop process is very short, we ignore the start-stop process and consider the working state. Using simple steady-state hydrodynamic lubrication theory, we calculate the stress under the corresponding working condition based on the parameters. This stress, combined with the cycle number obtained from the duration of the corresponding working condition, is used to calculate the damage rate for each working condition. The total damage rate of the bearing material after its entire life cycle is calculated by summing the damage rates of all working conditions.

[0051] in, , The number of stress applications corresponding to each working condition. , This represents the number of stress applications required for failure under maximum stress in each working condition. , The calculation formula is:

[0052] Where m is a material-related parameter. for The number of cycles required for material failure under symmetrical cyclic stress. This represents the stress amplitude.

[0053] Step 2: Calculate the wear and tear during a single startup process, such as... Figure 5 As shown, the transient fluid lubrication model is solved to calculate each time step. The combined forces of oil film force, rough peak contact force, and friction force Substitute the equations of motion to solve for the next moment. By repeating the process with parameters such as position at a given time, the shaft center trajectory and wear amount can be obtained.

[0054] Calculating wear using the Archard model requires contact stress, and solving for contact stress necessitates calculating the shaft center trajectory during start-up and shutdown. Therefore, the following nonlinear solution method is employed.

[0055] First, specify the initial state of the axis trajectory, including the starting position. Starting speed With acceleration Calculate the initial oil film thickness distribution based on the starting position. The calculation formula is:

[0056] in, Represents which time step, These represent the angular and axial coordinates of each position in the cylindrical coordinate system. For the radius gap, The relative position of the axis at a certain moment.

[0057] If the bearing currently has wear, the wear amount is superimposed on the corresponding oil film thickness to obtain the actual oil film thickness distribution. The calculation formula is:

[0058] in, This refers to the cumulative amount of wear and tear. This represents the number of times the device has started and stopped.

[0059] Based on actual oil film thickness distribution Substitute into the Reynolds equation to solve for the oil film pressure distribution. The average flow transient Reynolds equation is:

[0060] in, A coefficient related to oil film thickness and surface roughness. For lubricating oil viscosity, The linear velocity of the journal surface. Let be the journal radius. The change in oil film thickness over time is described by the journal center velocity at this moment. .

[0061] The oil film bearing capacity is then calculated by integrating the oil film pressure distribution. The formula for calculating the components in the two coordinate directions is:

[0062] Calculation of rough peak contact force based on Greenwood-Tripp micro-convex peak contact model The formula for calculating the components in the two coordinate directions is:

[0063]

[0064] in, To measure the overall elastic modulus, , , and , These are the elastic modulus and Poisson's ratio of the journal and bearing, respectively. and These represent the radius and density of the surface roughness peaks, respectively; and the film thickness ratio. When the ratio of oil film thickness to surface roughness is less than 4, Conversely, it is 0.

[0065] According to the Arcard formula, the contact pressure is... Substitute this into the solution to calculate the wear amount within this time step. The calculation formula is:

[0066] in, The wear coefficient is... The hardness of the journal and bearing material is determined by the softer material.

[0067] Calculating friction force from oil film pressure distribution The direction is perpendicular to the resultant force of the contact force and points in the direction that opposes the relative motion, causing the journal to climb in the opposite direction of rotation. The calculation formula is:

[0068] like Figure 8 As shown, the oil film bearing capacity of the journal is obtained respectively. Rough peak contact force With friction The components in both directions, added to the external load and gravity, yield the resultant external force on the journal. The position, velocity, and acceleration of the axis at the next moment are obtained from the net external force and the time step. The calculation formula is as follows:

[0069]

[0070] Based on the above steps of the nonlinear shaft center trajectory during the starting and stopping process of the sliding bearing, the shaft center position is determined. The axis motion trajectory is obtained by arranging the time steps t in sequence, and the wear amount at each time step is calculated. The accumulated wear during the Tth start-stop cycle is obtained by summing the data. .

[0071] Step 3: Accumulated wear and tear, such as Figure 6 As shown, shaded area 1 represents the worn area, shaded area 2 represents the original bearing profile, and shaded area 3 represents the worn bearing. The oil film thickness increases at the corresponding wear location, which will affect the wear generated during each start-up and shutdown. This is equivalent to the wear depth of each corresponding node, which is then summed to form the cumulative wear amount. The calculation formula is:

[0072] Step 4: Repeat steps 2 and 3 to obtain the cumulative wear of the bearing during the continuous start-stop process.

[0073] Step 5: Determine the wear life T2, such as Figure 2 As shown, a wear life test is performed after a certain period, including stability testing and load-bearing capacity testing. Stability testing verifies whether instability will occur after bearing wear. This is done by initially determining the bearing's stiffness and damping coefficients, then performing a complete shaft trajectory calculation to observe whether instability occurs. Load-bearing capacity is determined based on whether the bearing's stabilized film thickness ratio (the ratio of minimum oil film thickness to surface roughness) is less than the minimum film thickness ratio, i.e., the minimum oil film thickness. Is it less than the rated minimum film thickness? If the value is less than 1, the load-bearing capacity is considered insufficient. If instability or insufficient load-bearing capacity occurs, the period T at this moment is recorded as the wear life T2. Then the cycle of step four ends.

[0074] After partial wear, the load-bearing capacity of a circular bearing with the same eccentricity changes with the amount of wear, and its stiffness and damping also change systematically. Combined with commonly used bearing stability assessment methods, as shown in Figure 10, the overall stiffness of the bearing oil film... The overall stiffness of the bearing oil film after partial wear is a necessary condition for bearing stability. The value decreases as wear increases, therefore it is believed that bearings are more prone to instability after wear.

[0075]

[0076] in, These represent the stiffness and damping of the bearing, respectively. , , , , , , and These are all dynamic characteristics of bearings.

[0077] When the load-carrying capacity of a sliding bearing decreases, the eccentricity will increase to adapt to the load under the same load, which will lead to a decrease in oil film thickness. Insufficient minimum oil film thickness will result in increased bearing friction torque and wear, making it prone to problems such as rubbing and bearing seizure. Therefore, the minimum oil film thickness should be... Failure is determined when the film thickness is less than the rated minimum thickness.

[0078] The stability of the oil film can be directly determined by solving the nonlinear shaft center trajectory of the bearing, as shown in Figure 10. A bearing with good stability will have its shaft center trajectory converge to a point after startup, while instability will result in irregular whirls. However, for the sake of calculation simplicity, the overall stiffness of the bearing oil film is used instead. Instability can be determined when the overall stiffness of the bearing oil film is... Then, the shaft center trajectory can be calculated to determine whether the bearing is unstable.

[0079] Step Six: Compare the fatigue life T1 from Step One with the wear life T2 from Step Five, and take the smaller value as the predicted final life of the bearing.

[0080] The present invention will be further described in detail below through specific embodiments: Example 1: This embodiment is an example of life verification for a certain bearing. It is known that the surface material of the bearing is brass, and the bearing parameters are shown in Table 1.

[0081] Table 1 Bearing Parameter Table

[0082] Step 1: Before wear occurs, calculate the stress on the bearing surface material based on the maximum oil film pressure and maximum shear stress under steady state. Perform a start-up calculation to obtain the bearing's stable position at an eccentricity of 0.959 under this operating condition. The maximum oil film pressure at this position during stable operation is as follows: Figure 7 As shown, the maximum oil film pressure , maximum shear stress The combined calculated stress is:

[0083] The fatigue life N is substituted into the calculation conditions:

[0084] The total working cycle is 20,000 hours, and the number of stress exposures (n) at a speed of 1000 rpm is:

[0085] Substituting this into the equation, we obtain the surface material damage rate D over the entire process under this working condition:

[0086] Due to material failure rate Therefore, it is believed that no fatigue failure will occur within 20,000 hours, and the fatigue life is... .

[0087] Step Two: Establish as follows Figure 3 The model shown is a calculation model for multiple-start wear considering rough peak contact. The numerical model was solved in a computer, and the results are as follows: Figure 13 The shaft center trajectory for each startup process is shown in Figure 9(a). Based on the shaft center trajectory and the Archard wear model, the single wear amount is obtained as shown in Figure 9(a).

[0088] Step 3: After each start-up, add the previous wear amount to the calculated oil film thickness. Repeat this process until the minimum oil film thickness is insufficient or the stability is insufficient. Since the wear amount of a single start-up is very small, it usually takes multiple accumulations of wear amount to affect the bearing operation. Therefore, it is necessary to accumulate the wear amount of many starts at the corresponding position of the bearing bush. Considering that the wear growth process is very linear, the wear amount of multiple starts can be approximated as equal. The wear amount of 80,000 starts is equivalent to the sum of 1,000 times the wear amount of 80 starts, as shown in Figure 9(a), which represents the total wear amount between the 46,000th and 47,000th starts. Figure 9(b) shows the total wear amount after accumulating 47,000 starts.

[0089] Step Four: As Figure 11 As shown, in the 47th calculation, i.e., the 47,000th start-up, the oil film thickness changed due to accumulated wear compared to before wear. Figure 12 The oil film pressure shown has an adverse effect, reducing the load-bearing capacity of the oil film. In the calculations, the minimum film thickness ratio (the ratio of minimum oil film thickness to surface roughness) consistently fails to meet the requirement of being greater than 5 until stability is achieved. Therefore, it is considered that the load-bearing capacity after 47,000 starts does not meet the requirements. This is due to the overall stiffness of the bearing oil film throughout the process. Furthermore, the shaft trajectory did not become unstable, indicating that the bearing has not yet reached its stable lifespan. Therefore, 47,000 starts, or 11,750 hours, are taken as the wear life T2 of the bearing.

[0090] Step 6: Take the smaller value between fatigue life T1 and wear life T2, that is, 11750 hours of T2, as the predicted final life of the bearing.

[0091] Example 2: This invention also provides a sliding bearing life assessment system, such as... Figure 14As shown, the system includes: a fatigue module, a wear module, a calculation module, and a comparison module.

[0092] The fatigue module is used to solve the maximum oil film pressure and maximum shear stress under various working conditions based on the fluid lubrication calculation model, and to perform full-cycle damage accumulation assessment using the Miner's rule to calculate the material fatigue life of the sliding bearing. The wear module is used to solve the shaft center trajectory of the sliding bearing in each start-stop working cycle based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. The calculation module is used to calculate the bearing capacity and bearing stability when partial wear occurs based on the fluid lubrication calculation model and the accumulation of wear amount, and to obtain the wear life of the sliding bearing. The comparison module is used to compare the wear life of the sliding bearing with the material fatigue life of the sliding bearing to determine the life of the sliding bearing.

[0093] It is understood that the sliding bearing life assessment system provided by the present invention corresponds to the sliding bearing life assessment method provided in the foregoing embodiments. The relevant technical features of the sliding bearing life assessment system can be referred to the relevant technical features of the sliding bearing life assessment method, and will not be repeated here.

[0094] Another object of the present invention is to provide an electronic device, such as... Figure 15 As shown, it includes a memory, a processor, and a computer program stored in the memory and executable on the processor, the processor performing the steps of the sliding bearing life assessment method.

[0095] The method for assessing the life of a sliding bearing includes the following steps: Based on the fluid lubrication calculation model, the maximum oil film pressure and maximum shear stress under various working conditions are solved. The Miner rule is used to perform full-cycle damage accumulation assessment and calculate the material fatigue life of the sliding bearing. The shaft center trajectory of the sliding bearing in each start-stop working cycle is solved based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. Based on the fluid lubrication calculation model and the accumulation of wear, the bearing load capacity and bearing stability when partial wear occurs are calculated, and the wear life of the sliding bearing is obtained. The life of a sliding bearing is determined by comparing its wear life with its material fatigue life.

[0096] A fourth objective of this invention is to provide a computer-readable storage medium storing a computer program that, when executed by a processor, implements the steps of the sliding bearing life assessment method.

[0097] The method for assessing the life of a sliding bearing includes the following steps: Based on the fluid lubrication calculation model, the maximum oil film pressure and maximum shear stress under various working conditions are solved. The Miner rule is used to perform full-cycle damage accumulation assessment and calculate the material fatigue life of the sliding bearing. The shaft center trajectory of the sliding bearing in each start-stop working cycle is solved based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. Based on the fluid lubrication calculation model and the accumulation of wear, the bearing load capacity and bearing stability when partial wear occurs are calculated, and the wear life of the sliding bearing is obtained. The life of a sliding bearing is determined by comparing its wear life with its material fatigue life.

[0098] Those skilled in the art will understand that embodiments of the present invention can be provided as methods, systems, or computer program products. Therefore, the present invention can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, the present invention can take the form of a computer program product embodied on one or more computer-usable storage media (including, but not limited to, disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0099] This invention is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of the invention. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart illustrations and / or block diagrams. Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0100] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1 One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0101] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0102] 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 it. Although the present invention has been described in detail with reference to the above embodiments, those skilled in the art should understand that modifications or equivalent substitutions can still be made to the specific implementation of the present invention. Any modifications or equivalent substitutions that do not depart from the spirit and scope of the present invention should be covered within the scope of protection of the claims of the present invention.

Claims

1. A method for evaluating the life of a sliding bearing, characterized in that, include: Based on the fluid lubrication calculation model, the maximum oil film pressure and maximum shear stress under various working conditions are solved. The Miner rule is used to perform full-cycle damage accumulation assessment and calculate the material fatigue life of the sliding bearing. The shaft center trajectory of the sliding bearing in each start-stop working cycle is solved based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. Based on the fluid lubrication calculation model and the accumulation of wear, the bearing load capacity and bearing stability when partial wear occurs are calculated, and the wear life of the sliding bearing is obtained. The life of a sliding bearing is determined by comparing its wear life with its material fatigue life.

2. The method for evaluating the life of a sliding bearing according to claim 1, characterized in that, The total damage over the entire life cycle is represented by the total damage rate after operation over the entire life cycle. The total damage rate after operation over the entire life cycle is: in, The total damage rate after operation over the entire life cycle. , The number of stress applications corresponding to each working condition. , This represents the number of stress applications required for failure under maximum stress in each working condition.

3. The method for evaluating the life of a sliding bearing according to claim 2, characterized in that, The number of stress applications required for failure under maximum stress under each working condition is: in, For parameters related to materials, for The number of cycles required for material failure under symmetrical cyclic stress. This refers to the stress amplitude; in, For maximum oil film pressure, This represents the maximum oil film shear stress.

4. The method for evaluating the life of a sliding bearing according to claim 1, characterized in that, The calculation process for the shaft center trajectory during each start-stop cycle is as follows: Given the initial parameters at the starting point, calculate the initial oil film thickness, add it to the cumulative wear amount to obtain the actual oil film thickness, and substitute it into the transient Reynolds equation to iteratively solve for the oil film pressure; Replace the extrusion term with the velocity at that moment, calculate the oil film force from the oil film pressure, calculate the contact force based on the actual oil film thickness and bearing surface quality, and calculate the lubricating oil friction force based on the oil film pressure; Based on the oil film force, contact force, and lubricating oil friction, calculate the resultant force on the journal, substitute it into the equation of motion to obtain the acceleration, and calculate the position and velocity at the next moment.

5. The method for evaluating the life of a sliding bearing according to claim 1, characterized in that, Wear is expressed as oil film thickness: in, The initial oil film thickness. , This represents the relative position of the axis center at time t. These are the angular coordinates of each position in a cylindrical coordinate system. Let be the axial coordinates of each position in the cylindrical coordinate system. Where c is the number of starts and stops, and c is the radius gap. This represents the cumulative amount of wear and tear.

6. The method for evaluating the life of a sliding bearing according to claim 1, characterized in that, The wear amount in each cycle is: in, This represents the amount of wear accumulated within a time step. The wear coefficient is... For journals and bearings, the hardness of the softer material is... To contact pressure, The linear velocity of the journal surface. For time steps.

7. The method for evaluating the life of a sliding bearing according to claim 1, characterized in that, When partial wear occurs, the bearing's load-bearing capacity and stability are determined by the overall stiffness of the bearing oil film. The overall stiffness of the bearing oil film is: in, For the overall stiffness of the bearing oil film, Indicates the stiffness of the bearing. Indicates the damping of the bearing. , , , , , , and These are all dynamic characteristics of bearings.

8. A sliding bearing life assessment system, characterized in that, include: The fatigue module is used to solve the maximum oil film pressure and maximum shear stress under various working conditions based on the fluid lubrication calculation model, and to perform full-cycle damage accumulation assessment using the Miner's rule to calculate the material fatigue life of the sliding bearing. The wear module is used to solve the shaft center trajectory of the sliding bearing in each start-stop working cycle based on the fluid lubrication calculation model. Based on the shaft center trajectory, the wear amount in each cycle is calculated using the Archard sliding wear model. The calculation module is used to calculate the bearing capacity and bearing stability when partial wear occurs based on the fluid lubrication calculation model and the accumulation of wear amount, and to obtain the wear life of the sliding bearing. The comparison module is used to compare the wear life of the sliding bearing with the material fatigue life of the sliding bearing to determine the life of the sliding bearing.

9. A terminal 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 according to any one of claims 1 to 7.

10. A computer-readable storage medium storing a computer program, characterized in that, When the computer program is executed by a processor, it implements the steps of the method according to any one of claims 1 to 7.

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