Method and system for evaluating heavy-load working condition endurance capacity of ultra-high-temperature tapered roller bearing

Abstract

The invention discloses a method and a system for evaluating the endurance capacity of an ultra-high-temperature tapered roller bearing under a heavy-load working condition, belongs to the technical field of rolling bearing performance evaluation, and solves the problem that the endurance capacity of the tapered roller bearing under an extreme working condition cannot be accurately analyzed due to the lack of a method for comprehensively evaluating the limit performance of the bearing under the ultra-high-temperature heavy-load working condition at present. Comprising the steps of collecting various parameters of a to-be-evaluated tapered roller bearing; calculating to obtain the deformation of each part, and determining the displacement-deformation coordination conditions of the rolling body, the ferrule and the retainer; establishing a quasi-statics model of the tapered roller bearing, and calculating to obtain the contact height of the flange, the load distribution of the rolling body and the contact load of the rolling body and the retainer; calculating the equivalent stress between the roller and each part, the yield strength at the corresponding high temperature and the friction coefficient of the tapered roller bearing; and evaluating the high-temperature heavy-load working condition endurance capability of the tapered roller bearing according to the calculated parameters. The method is suitable for tapered roller bearing performance evaluation scenes.

Description

Technical Field

[0001] This invention belongs to the technical field of rolling bearing performance evaluation, specifically relating to a method for evaluating the endurance of tapered roller bearings under combined ultra-high temperature and heavy load conditions. Background Technology

[0002] Under the extreme operating conditions of hypersonic vehicles, tapered roller bearings, as core supporting components of power transmission, attitude control, and thermal protection systems, directly determine the reliability of the vehicle and the success rate of the mission. The aerodynamic heating, severe impact loads, and complex thermo-coupling environment faced by hypersonic vehicles place near-limit performance requirements on bearings.

[0003] When tapered roller bearings operate under ultra-high temperature and heavy load conditions, the high equivalent stress between the rollers and raceways, the contact force between the rollers and the flanges causing the rollers to skew, and the combined effects of the thermal softening effect of the material at high temperatures can lead to damage such as plastic deformation, excessive local wear, cage expansion and fracture, resulting in bearing failure and even catastrophic accidents such as bearing seizure and shaft breakage.

[0004] Currently, the analytical methods for evaluating the endurance of ultra-high temperature heavy-duty tapered roller bearings are not yet perfect. Therefore, it is necessary to comprehensively consider the influence of working conditions, structure, materials, etc., and construct an evaluation method for the endurance of ultra-high temperature heavy-duty tapered roller bearings under extreme working conditions, so as to provide a basis for bearing selection and design. Summary of the Invention

[0005] This invention proposes a method and system for evaluating the endurance of ultra-high temperature tapered roller bearings under heavy load conditions. The purpose is to solve the problem that there is currently a lack of analytical methods that can comprehensively evaluate the ultimate performance of bearings under ultra-high temperature and heavy load conditions, which leads to the inability to accurately analyze the endurance of tapered roller bearings under extreme conditions.

[0006] The present invention provides a method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, comprising: S1: Collect the geometric parameters of the tapered roller bearing to be evaluated, the material parameters of each component of the bearing, the bearing housing and the shaft at different temperatures, and the operating condition parameters. S2: Calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and determine the displacement-deformation compatibility conditions of the rolling elements, rings, and cage in combination with the skew factor. S3: Based on the displacement-deformation compatibility conditions of the rolling elements, rings, and cage, a quasi-static model of the tapered roller bearing is established to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. S4: Based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of small strain frames, calculate the equivalent stress between the rollers and each component and the corresponding yield strength at high temperature, and calculate the friction coefficient of the tapered roller bearing. S5: Based on the calculated flange contact height, contact load between rolling elements and cage, maximum equivalent stress, and friction coefficient of tapered roller bearing, evaluate the high-temperature heavy-load operating condition tolerance of tapered roller bearing.

[0007] Furthermore, a preferred embodiment is provided: the geometric parameters of the tapered roller bearing to be evaluated include: the inner raceway contact angle, the outer raceway contact angle, and the roller diameter of the tapered roller bearing to be evaluated.

[0008] Furthermore, a preferred embodiment is provided: the material parameters of the bearing components, bearing housing, and shaft at different temperatures include: the elastic modulus, Poisson's ratio, and density of the bearing components, bearing housing, and shaft at different temperatures; the bearing components include: rollers, raceways, and cages.

[0009] Furthermore, a preferred option is provided: the operating parameters include: rotational speed, load, and temperature.

[0010] Furthermore, a preferred embodiment is provided: in S4, the frictional torque of the tapered roller bearing is calculated using the law of conservation of energy.

[0011] Furthermore, a preferred solution is provided: in S3, the Dogbox-TRF collaborative solution algorithm is used to solve the quasi-static model of the tapered roller bearing.

[0012] Furthermore, a preferred embodiment is provided: In step S5, the step of assessing the high-temperature heavy-load tolerance of tapered roller bearings includes: Determine the allowable contact range of the flange, the allowable force of the cage, the allowable equivalent stress, and the allowable coefficient of friction; When the flange contact height of the tapered roller bearing is within the allowable range of flange contact, the contact load between the rolling elements and the cage is less than or equal to the allowable force of the cage, the maximum equivalent stress is less than the allowable equivalent stress, and the coefficient of friction of the tapered roller bearing is less than the allowable coefficient of friction, the tapered roller bearing meets the usage requirements; otherwise, it does not meet the usage requirements.

[0013] The present invention also proposes a computer device, the computer device including a memory and a processor, the memory storing a computer program, and when the processor runs the computer program stored in the memory, the processor executes the method for evaluating the heavy-load endurance of ultra-high temperature tapered roller bearings as described in any one or more of the above-described schemes.

[0014] The present invention also proposes a computer-readable storage medium for storing a computer program that executes a method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings as described in any one or more of the above-described schemes.

[0015] The present invention proposes a system for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, which is based on a method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings described in any one or more of the above-mentioned schemes. The system includes: Parameter acquisition module: used to acquire the geometric dimensional parameters of the tapered roller bearing to be evaluated, the material parameters of each component of the bearing, the bearing housing and the shaft at different temperatures, and the operating condition parameters; Condition Establishment Module: Used to calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and to determine the displacement-deformation compatibility conditions between the rolling elements, the rings, and the cage. The first calculation module is used to determine the quasi-static model of the tapered roller bearing based on the displacement-deformation compatibility conditions of the rolling elements, raceways, and cage, and to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. The second calculation module is used to calculate the equivalent stress between the roller and each component and the corresponding yield strength at high temperature based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of the small strain frame, and to calculate the friction coefficient of the tapered roller bearing. Endurance Assessment Module: This module is used to assess the high-temperature heavy-load endurance of tapered roller bearings based on the calculated flange contact height, contact load between the rolling elements and the cage, maximum equivalent stress, and the friction coefficient of the tapered roller bearing.

[0016] Compared with the prior art, the advantages of the present invention are: This invention considers thermal effects and the interactions between rolling elements, raceways, and cages, establishing a quasi-static model of tapered roller bearings. It specifically introduces a material property parameter correction mechanism and a thermal deformation coupling analysis module for high-temperature environments. Combined with the Dogbox-TRF collaborative solution algorithm, it calculates the stress state of each rolling element, raceway, and cage. During the calculation, the influence of temperature-induced deformation on roller attitude and contact angle is simultaneously considered, achieving a collaborative analysis of bearing mechanical behavior and thermal deformation at high temperatures. This ensures efficient quasi-static calculations while improving the model's accuracy under high-temperature conditions. Furthermore, it analyzes bearing friction and wear. By calculating input variables such as temperature, external load, speed, structural and material parameters, it enables rapid evaluation of tapered roller bearing performance under extreme conditions. This invention provides fundamental support for further improving the evaluation of tapered roller bearing endurance under ultra-high temperature and heavy-load conditions.

[0017] The core of this invention lies in constructing a novel evaluation index system, overcoming the limitations of traditional evaluation methods that lack comprehensiveness and specificity in characterizing bearing performance. Targeting specific failure modes common in bearings under high-temperature environments, such as flange wear, cage failure, contact fatigue, and frictional heating, the invention innovatively incorporates flange contact height, contact load between rolling elements and the cage, maximum equivalent stress, and the friction coefficient of tapered roller bearings into the evaluation scope. Specifically, flange contact height accurately characterizes the contact state and wear trend between the flange and the rollers at high temperatures; the contact load between the rolling elements and the cage directly reflects the stress stability of the cage under high-temperature conditions, preventing bearing failure due to cage damage; the maximum equivalent stress quantifies the stress level of key contact areas in the bearing under high-temperature conditions, providing crucial information for predicting bearing fatigue life; and the friction coefficient effectively assesses the lubrication state and energy loss of the bearing at high temperatures, relating to its operational stability and heat generation. These four types of indicators complement each other, forming a comprehensive evaluation dimension covering bearing structural contact, mechanical properties, failure risk, and operating efficiency. This significantly improves the comprehensiveness and accuracy of the evaluation of high-temperature tapered roller bearings, providing more scientific technical support for their design optimization, life prediction, and reliability improvement.

[0018] This invention is applicable to the performance evaluation of tapered roller bearings. Attached Figure Description

[0019] Figure 1 The flowchart is a method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to a specific embodiment of the present invention. Figure 2 This is a flowchart of the Dogbox-TRF collaborative solution algorithm described in Specific Embodiment 3 of the present invention. Detailed Implementation

[0020] In the following description, specific details such as particular system architectures and techniques are set forth for illustrative purposes and not for limitation, in order to provide a thorough understanding of the embodiments of this application. However, those skilled in the art will understand that this application can also be implemented in other embodiments without these specific details. In other instances, detailed descriptions of well-known systems, apparatuses, circuits, and methods are omitted so as not to obscure the description of this application with unnecessary detail.

[0021] The following is in conjunction with the appendix to this application specification. Figure 1-2 The technical solutions in the embodiments of this application are clearly and completely described. Obviously, the described embodiments are only a part of the embodiments of this application, and not all of the embodiments. Based on the embodiments in this application, all other embodiments obtained by those of ordinary skill in the art without creative effort are within the scope of protection of this application.

[0022] Implementation Method 1: Reference Figure 1 This implementation method is described below.

[0023] A method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings includes: S1: Collect the geometric dimensional parameters, material parameters of bearing components, bearing housing, and shaft at different temperatures, and operating condition parameters of the tapered roller bearing to be evaluated. The geometric dimensional parameters of the tapered roller bearing to be evaluated include: the inner raceway contact angle, the outer raceway contact angle, and the roller diameter. The material parameters of bearing components, bearing housing, and shaft at different temperatures include: the elastic modulus, Poisson's ratio, and density of bearing components, bearing housing, and shaft at different temperatures. The different temperatures are selected under operating conditions with temperatures greater than 800℃, and the elastic modulus, Poisson's ratio, and density of bearing components, bearing housing, and shaft are collected at several temperatures. The bearing components include: rollers, raceways, and cage. The operating condition parameters include: speed, load, and temperature.

[0024] S2: Calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and determine the displacement-deformation compatibility conditions between the rolling elements, the rings, and the cage. S3: Based on the displacement-deformation compatibility conditions of the rolling elements, rings, and cage, a quasi-static model of the tapered roller bearing is established to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. S4: Based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of the small strain frame, calculate the equivalent stress between the roller and each component and the corresponding yield strength at high temperature, and use the law of conservation of energy to calculate the friction coefficient of the tapered roller bearing. S5: Based on the calculated flange contact height, contact load between the rolling elements and the cage, maximum equivalent stress, and the friction coefficient of the tapered roller bearing, assess the high-temperature heavy-load operating capacity of the tapered roller bearing, including: determining the allowable flange contact range, allowable cage stress, allowable equivalent stress, and allowable friction coefficient; when the flange contact height of the tapered roller bearing is within the allowable flange contact range, the contact load between the rolling elements and the cage is less than or equal to the allowable cage stress, the maximum equivalent stress is less than the allowable equivalent stress, and the friction coefficient of the tapered roller bearing is less than the allowable friction coefficient, the tapered roller bearing meets the usage requirements; otherwise, it does not meet the usage requirements.

[0025] Implementation Method Two: This embodiment is a further illustrative example of S2 in the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings described in Embodiment 1.

[0026] For low-speed, high-temperature operating conditions, a quasi-static analysis model for tapered roller bearings is established: Based on the original bearing's geometric parameters, a deformation compatibility model considering temperature and assembly stress is proposed: The inner cylinder bears external pressure, and the outer cylinder bears internal pressure. Assembly stress (initial stress) occurs within this combined cylinder, along with the assembly pressure. The relationship with the radius interference Δ is: (1) in, Indicates the inner diameter of the inner cylinder, Indicates the outer diameter of the outer cylinder, Indicates the outer diameter of the inner cylinder. Indicates the amount of interference. This represents the temperature-dependent elastic modulus of the inner cylinder material. This indicates the temperature-dependent elastic modulus of the outer cylinder material. Poisson's ratio, representing the relationship between the inner cylinder material and temperature, This represents the Poisson's ratio of the outer cylinder material in relation to temperature.

[0027] In part radius At this point, the assembly stress of the inner and outer rings and the deformation caused by rotation. , and for: (2) in, This indicates the fitting stress of the inner ring. This indicates the fitting stress of the outer ring. This represents the temperature-dependent elastic modulus of the bearing. Indicates the inner angular velocity. Poisson's ratio, representing the bearing's temperature dependence, This indicates the temperature-dependent density of the bearing material. Indicates the outer diameter of a cylindrical part. The inner diameter of the cylindrical part is indicated by T; the temperature is indicated by T.

[0028] The amount of raceway deformation caused by temperature is expressed as: (3) in, ΔT represents the coefficient of thermal expansion, and ΔT represents the temperature increment.

[0029] Raceway radius considering assembly, rotational speed, and thermal expansion effects: (4) in, Indicates the first k The azimuth angle of the roller, This indicates the azimuth angle considering the effects of assembly, rotational speed, and thermal expansion. Outer raceway radius, This indicates the azimuth angle considering the effects of assembly, rotational speed, and thermal expansion. The inner raceway radius, Indicates the corresponding azimuth angle The initial dimension of the inner raceway radius, Indicates the corresponding azimuth angle The initial size of the outer raceway radius.

[0030] Based on the vector transformation method and the slicing method, a contact deformation model of the raceway and rollers is established to simulate the interaction between the rollers, raceways, and cages.

[0031] Among them, the contact deformation between the roller and the raceway for:

[0032] (5) In the formula, Indicates the first raceway on the inner raceway after loading. k The radial component of the position vector of the contact point of each roller in the azimuth coordinate system. Indicates the first raceway on the outer track after loading. k The radial component of the position vector of the contact point of each roller in the azimuth coordinate system. Indicates the inner raceway half-cone angle. Indicates the half-cone angle of the outer raceway.

[0033] Contact deformation between the roller and the flange Represented as: (6) In the formula, This represents the x-component of the position vector of the contact point of the flange in the flange contact coordinate system. This indicates the radius of the arc at the large end of the roller.

[0034] Next, the contact load equations between the roller and the outer raceway, the inner raceway, and the cage due to skewness are constructed. The deformation-contact load equations between the roller and the outer raceway and the inner raceway are expressed as follows: (7) In the formula, Indicates raceway contact deformation. k = i , o ; Poisson's ratio, representing the material of the raceway as a function of temperature, Poisson's ratio, representing the temperature-dependent properties of the roller material, This represents the temperature-dependent elastic modulus of the ring material. This indicates the temperature-dependent elastic modulus of the roller material. Indicates contact load, Indicates the effective contact length.

[0035] The deformation-contact load equation between the roller and the flange is expressed as: (8) in, The coefficients are related to the principal curvature difference function at the contact point. Represents the principal curvature and function at the contact point. This represents the combined elastic constant of the two objects. This indicates the contact load between the rolling element and the flange.

[0036] Implementation Method 3: Reference Figure 2 This implementation method is described below.

[0037] This embodiment is a further illustrative example of S3 in the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings described in Embodiment 1.

[0038] The steps for establishing the quasi-static model of a tapered roller bearing are as follows: Roller force balance equation: (9) (10) in, Indicates the number of slices. Indicates the first roller j Contact load on the inner raceway of each slice Indicates the first roller j Contact load on the outer raceway of each slice Indicates the first j The coordinates of the position of the slice center on the roller axis. This indicates the coordinates of the roller's geometric center on the roller's axis. This indicates the position coordinates of the flange contact point along the roller axis. Indicates the roller tilt angle. Indicates the roller skew angle. Indicates the first j The change in azimuth angle corresponding to each slice , Indicates the first j The distance from the center of each slice to the bearing axis. Indicates the first roller j The diameter of each slice, Indicates the semi-cone angle of the roller. Indicates the pressure angle of the retaining edge. This indicates the angle between the roller axis and the bearing axis. The roller radius indicating the centroid position. Indicates the radius of the arc at the large end of the roller. Indicates the effective contact length. Indicates centrifugal force. This indicates the frictional force between the roller and the inner raceway caused by roller misalignment. This represents the total frictional force between the roller and the outer raceway caused by roller misalignment. This represents the torque on the roller caused by the roller-inner raceway load due to skewness. This represents the torque on the roller caused by the roller-outer raceway load due to skewness. This represents the tilting moment caused by the roller-inner raceway load. This represents the tilting moment caused by the roller-outer raceway load. This indicates the contact force between the roller and the cage pocket. This represents the gyroscopic torque of the roller. This represents the coefficient of friction between the contact surfaces of the roller and the raceway.

[0039] The inner ring force balance equation is expressed as: (11) (12) This represents the transformation matrix from the roller coordinate system to the inner ring coordinate system. This indicates the contact load between the roller and the inner raceway. This indicates the contact load between the roller and the flange. This represents the vector of contact points between the roller and the inner raceway. This represents the vector of the contact point between the roller and the flange.

[0040] The flange contact height and the contact load between the rolling element and the cage are calculated using the quasi-static model of the tapered roller bearing described in this embodiment: Initial contact height between the large end of the roller and the inner ring flange for: (13) When the bearing is under load, the contact point between the large end of the roller and the inner ring flange will shift. The relationship between the contact point and its position is given by the following formula. By solving the above quasi-static model, the displacement of the contact point can be calculated. .

[0041] (14) This represents the transformation matrix from the inertial coordinate system to the edge coordinate system. This represents the initial coordinate vector of the contact point of the flange in the inertial coordinate system.

[0042] Therefore, the contact height between the large end of the roller and the inner ring flange of the tapered roller bearing under load is: (15) When the roller becomes misaligned, it interacts with the cage pocket. By solving the aforementioned mechanical equilibrium equations, the contact load between the roller and the cage pocket can be determined. .

[0043] In S3, by combining Dogbox and TRF algorithms, adjusting the order of computation, and debugging the iteration accuracy and maximum number of iterations, local optima can be effectively avoided, thereby improving solution efficiency and accuracy.

[0044] The specific calculation process is as follows: Figure 2 As shown.

[0045] The quasi-static model of a tapered roller bearing considering rolling element misalignment is expressed by a system of equations consisting of 4Z+5 equations. Among these, the displacement and rotation of the inner ring relative to the inertial coordinate system are... There are a total of 5 unknowns; in the roller coordinate system, the first... j The displacement and rotation of each rolling element are There are a total of 4Z unknowns.

[0046] The system of equations is solved using a combined algorithm of Dogbox and TRF to obtain the contact load on each rolling element and the contact force between the skewed rolling element and the cage pocket. The specific logic is as follows: (1) Preliminary estimate of inner circle displacement and rolling element displacement Determine the relative positions of the inner ring and the rollers; (2) Use the Dogbox-TRF collaborative solution algorithm to solve the equilibrium equations of the rollers and solve for the displacements of all rollers. ; (3) Use the Dogbox-TRF collaborative solution algorithm to solve the equilibrium equations of the inner ring and determine the displacement of the ring. If the solution converges, the inner loop is in equilibrium, and the current solution is the final solution; if not, use the current loop position and go to step (2).

[0047] The logic of the Dogbox-TRF collaborative solution algorithm is as follows: First, use Dogbox to quickly shrink the solution space to the effective constraint region. If the convergence accuracy tool is reached at this point, output the solution result sol. If the convergence accuracy tool is not reached at this point, use the calculated result sol_Dogbox as the initial data and substitute it into the TRF algorithm for calculation. If the convergence accuracy tool is reached, output the result sol. If it still does not converge, adjust the iteration number iter and the convergence accuracy.

[0048] This implementation innovatively proposes a collaborative solution strategy combining the Dogbox and TRF algorithms to solve the nonlinear equations of a high-temperature tapered roller bearing model, overcoming the performance bottleneck of a single algorithm under complex working conditions. The Dogbox algorithm, leveraging its rectangular trust region characteristics and boundary constraint handling advantages, demonstrates high convergence efficiency in exploring local solution spaces with low variable dimensions. Meanwhile, the TRF algorithm, by dynamically adjusting the trust region shape, effectively addresses the ill-conditioned and multi-extremum problems that may arise in the nonlinear equations, maintaining strong robustness in the global solution space search. The organic combination of the two forms a two-layer solution mechanism of "local fine optimization - global robust exploration": the Dogbox algorithm is used to quickly shrink the solution space to the effective constraint region, and then the TRF algorithm is used to accurately locate the global optimal solution in this region. This avoids the convergence lag of the single Dogbox algorithm under high-dimensional variables and overcomes the insufficient optimization efficiency of the TRF algorithm under strong constraints. In the end, it achieves a synergistic improvement in accuracy, efficiency and stability in solving the nonlinear equations of high-temperature tapered roller bearings, and provides a breakthrough numerical solution scheme for bearing performance evaluation under extreme working conditions.

[0049] Implementation Method Four: This embodiment is a further illustrative example of S4 in the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings described in Embodiment 1.

[0050] In S4, based on the obtained rolling element load distribution, the equivalent stress and the yield strength of the material at high temperature are calculated using the small strain thermoelastic theory.

[0051] Specifically: the equivalent stress of the bearing is expressed as a function of the deviatoric strain tensor under high-temperature conditions: (16) In the formula: S represents the deviatoric stress tensor.

[0052] The deviatoric stress tensor S is: (17) In the formula: Represents the stress tensor. This represents a fourth-order unit tensor.

[0053] The stress tensor is: (18) In the formula: Represents the temperature-dependent elastic tensor; This represents the strain tensor.

[0054] The expression for yield strength is: (19) In the formula: This represents the initial yield stress, in Pa. Indicates the melting temperature of the material, in °C. m Indicates the thermal softening index; This indicates the thermal softening factor.

[0055] The steps for calculating the friction coefficient of tapered roller bearings under high-temperature conditions are as follows: The frictional torque of a tapered roller bearing is expressed as: (20) in, This indicates the total power loss of a high-temperature dry friction tapered roller bearing. This represents the frictional power loss caused by differential sliding between the rolling elements and the raceway. This represents the frictional power loss caused by the sliding friction between the large end face of the rolling element and the inner ring flange. This represents the frictional power loss caused by the sliding friction between the skewed rolling element and the cage pocket. This represents the total frictional torque of a high-temperature dry friction tapered roller bearing. This represents the frictional torque caused by the differential sliding between the rolling elements and the raceways. This represents the frictional torque caused by the sliding friction between the large end face of the rolling element and the inner ring flange. This represents the frictional torque caused by the sliding friction between the skewed rolling element and the cage pocket. This indicates the rotational speed of the inner ring.

[0056] The coefficient of friction of the bearing is: (twenty one) In the formula: The value represents the frictional torque of the tapered roller bearing, d represents the bearing inner diameter, D represents the bearing outer diameter, and P represents the bearing equivalent load.

[0057] The bearing friction coefficient should be less than the allowable friction coefficient. (twenty two) in, This indicates the allowable coefficient of friction for a bearing under high-temperature conditions.

[0058] Implementation Method 5: This embodiment is a further illustrative example of S5 in the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings described in Embodiment 1.

[0059] Edge contact height h The contact load between the rolling elements and the cage is calculated in S3, and the maximum equivalent stress is selected from the equivalent stress between the rollers and each component obtained in S4.

[0060] The contact point between the roller ball base and the inner ring large flange should be controlled within the range of about 1 / 2 of the middle of the large flange, thereby determining the appropriate contact height range: (twenty three) in, This indicates the height of the inner ring large flange.

[0061] By evaluating the stress state of the cage at high temperatures, the initial fit clearance design considering thermal expansion compensation can be deduced, avoiding overload caused by abnormal clearance and ensuring the stability of roller movement. The contact force between the roller and the cage pocket. This can be calculated from S3, therefore: (twenty four) in, This indicates the allowable load of the cage under high-temperature conditions.

[0062] The specific evaluation criteria are: when the contact point of the edge is within the allowable range. Internal; the contact load of the cage is within the allowable value within, that is The maximum equivalent stress is less than the allowable equivalent stress. And the coefficient of friction is less than the allowable coefficient of friction. If the condition is met, then the tapered roller bearing meets the usage requirements; otherwise, it does not.

[0063] Implementation Method Six: A system for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, the system being based on the aforementioned method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, the system comprising: Parameter acquisition module: used to acquire the geometric dimensional parameters of the tapered roller bearing to be evaluated, the material parameters of each component of the bearing, the bearing housing and the shaft at different temperatures, and the operating condition parameters; Condition Establishment Module: Used to calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and to determine the displacement-deformation compatibility conditions between the rolling elements, the rings, and the cage. The first calculation module is used to determine the quasi-static model of the tapered roller bearing based on the displacement-deformation compatibility conditions of the rolling elements, raceways, and cage, and to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. The second calculation module is used to calculate the equivalent stress between the roller and each component and the corresponding yield strength at high temperature based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of the small strain frame, and to calculate the friction coefficient of the tapered roller bearing. Endurance Assessment Module: This module is used to assess the high-temperature heavy-load endurance of tapered roller bearings based on the calculated flange contact height, contact load between the rolling elements and the cage, maximum equivalent stress, and the friction coefficient of the tapered roller bearing.

Claims

1. A method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, characterized in that, The method includes: S1: Collect the geometric parameters of the tapered roller bearing to be evaluated, the material parameters of each component of the bearing, the bearing housing and the shaft at different temperatures, and the operating condition parameters. S2: Calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and determine the displacement-deformation compatibility conditions of the rolling elements, rings, and cage in combination with the skew factor. S3: Based on the displacement-deformation compatibility conditions of the rolling elements, rings, and cage, a quasi-static model of the tapered roller bearing is established to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. S4: Based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of small strain frames, calculate the equivalent stress between the rollers and each component and the corresponding yield strength at high temperature, and calculate the friction coefficient of the tapered roller bearing. S5: Based on the calculated flange contact height, contact load between rolling elements and cage, maximum equivalent stress, and friction coefficient of tapered roller bearing, evaluate the high-temperature heavy-load operating condition tolerance of tapered roller bearing.

2. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, The geometric parameters of the tapered roller bearing to be evaluated include: the inner raceway contact angle, the outer raceway contact angle, and the roller diameter.

3. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, The material parameters of the bearing components, bearing housing, and shaft at different temperatures include: the elastic modulus, Poisson's ratio, and density of the bearing components, bearing housing, and shaft at different temperatures; the bearing components include: rollers, raceways, and cages.

4. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, The operating parameters include: rotational speed, load, and temperature.

5. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, In S4, the frictional torque of the tapered roller bearing is calculated using the law of conservation of energy.

6. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, In S3, the Dogbox-TRF collaborative solution algorithm is used to solve the quasi-static model of the tapered roller bearing.

7. The method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to claim 1, characterized in that, In step S5, the steps for assessing the high-temperature heavy-load tolerance of tapered roller bearings include: Determine the allowable contact range of the flange, the allowable force of the cage, the allowable equivalent stress, and the allowable coefficient of friction; When the flange contact height of the tapered roller bearing is within the allowable range of flange contact, the contact load between the rolling elements and the cage is less than or equal to the allowable force of the cage, the maximum equivalent stress is less than the allowable equivalent stress, and the coefficient of friction of the tapered roller bearing is less than the allowable coefficient of friction, the tapered roller bearing meets the usage requirements; otherwise, it does not meet the usage requirements.

8. A computer device, characterized in that, The computer device includes a memory and a processor. The memory stores a computer program. When the processor runs the computer program stored in the memory, the processor executes the method for evaluating the heavy-load endurance of ultra-high temperature tapered roller bearings according to any one of claims 1-7.

9. A computer-readable storage medium, characterized in that, The computer-readable storage medium is used to store a computer program that executes the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings according to any one of claims 1-7.

10. A system for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings, characterized in that, The system is based on the method for evaluating the heavy-load tolerance of ultra-high temperature tapered roller bearings as described in any one of claims 1-7, and the system includes: Parameter acquisition module: used to acquire the geometric dimensional parameters of the tapered roller bearing to be evaluated, the material parameters of each component of the bearing, the bearing housing and the shaft at different temperatures, and the operating condition parameters; Condition Establishment Module: Used to calculate the deformation of each component based on the material parameters of each component of the bearing at different temperatures, and to determine the displacement-deformation compatibility conditions between the rolling elements, the rings, and the cage. The first calculation module is used to determine the quasi-static model of the tapered roller bearing based on the displacement-deformation compatibility conditions of the rolling elements, raceways, and cage, and to calculate the flange contact height, the load distribution of the rolling elements, and the contact load between the rolling elements and the cage. The second calculation module is used to calculate the equivalent stress between the roller and each component and the corresponding yield strength at high temperature based on the load distribution of the rolling elements and the thermo-elastic-plastic theory of the small strain frame, and to calculate the friction coefficient of the tapered roller bearing. Endurance Assessment Module: This module is used to assess the high-temperature, heavy-load endurance of tapered roller bearings based on the calculated flange contact height, contact load between the rolling elements and the cage, maximum equivalent stress, and the friction coefficient of the tapered roller bearing.

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