Method and device for calculating fatigue life of main bearing of shield tunneling machine and medium

Abstract

The invention relates to the technical field of shield tunneling machine main bearing fatigue calculation, in particular to a shield tunneling machine main bearing fatigue life calculation method and device and a medium, and the method comprises the steps: building a main bearing load distribution calculation model; establishing a surface function of the roller contact area based on the roller modification function; establishing a cylindrical roller linear contact stress calculation model; and establishing a main bearing fatigue life calculation model, and calculating the main bearing fatigue life. According to the method, the roller modification is introduced into the calculation of the fatigue life of the main bearing, the calculation result can provide quantitative evaluation for the quality of the roller modification, in addition, the load distribution and the contact stress are respectively calculated, and the calculation difficulty is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of fatigue calculation of main bearings of shield machines, and in particular to a method, equipment and medium for calculating fatigue life of main bearings of shield machines. Background Art

[0002] A tunnel boring machine (TBM) is a type of engineering machinery used for tunnel excavation. It integrates mechanical, electrical, hydraulic, and information technologies, enabling it to excavate long, deep, and large-diameter tunnels. As a core component in the operation of a TBM, the main bearing is large, complex, and requires high maintenance costs. Once in operation, it cannot be replaced. This requires high reliability and a long lifespan. The bearing's load-bearing capacity and fatigue life depend not only on material properties but also on the rationality of the structural design. TBM main bearings utilize a three-row roller structure. To avoid stress concentration at the ends of straight busbar rollers under load, the main bearing rollers are typically reshaped.

[0003] Existing technologies generally evaluate the rationality of the main bearing roller modification method and size by comparing different contact stresses. Existing technologies rarely correlate roller modification with fatigue life. While algorithms correlating roller modification and fatigue life can account for the impact of roller modification on main bearing fatigue life, contact stresses are calculated using a load distribution model, which requires a limited number of roller slices. Otherwise, the calculations may fail to converge. Existing logarithmic modification formulas calculate bearing fatigue life by simultaneously considering the modification of both the roller ends and the middle edge, but fail to incorporate specific life calculation methods.

[0004] In summary, there is an urgent need for a shield machine main bearing fatigue life calculation method, equipment and medium to solve the problems in the existing technology. Summary of the Invention

[0005] The present invention aims to provide a method, device and medium for calculating the fatigue life of the main bearing of a shield machine. The specific technical solution is as follows:

[0006] A method for calculating the fatigue life of a shield machine main bearing comprises the following steps:

[0007] S1: Establish a main bearing load distribution calculation model. Specifically, obtain the roller distribution angles on the main thrust raceway, auxiliary thrust raceway, and radial raceway, calculate the roller elastic deformation at the roller distribution angles, establish the equilibrium equations for the isolator composed of the roller and inner ring under axial force, radial force, and overturning moment, and establish the main bearing load distribution calculation model based on the roller elastic deformation, equilibrium equation, and empirical formula to calculate the load on each roller.

[0008] S2: establishing a surface function of the roller contact area, specifically, calculating the roller radial surface function according to the shaping function, and obtaining the surface function of the roller contact area based on the roller radial surface function and the shaping function;

[0009] S3: Establish a cylindrical roller linear contact stress calculation model. Specifically, based on the surface function of the roller contact area, the contact stress distribution function and the contact area area are calculated, and the contact stress along the roller element line direction and the load on the roller are calculated.

[0010] S4: Establish a main bearing fatigue life calculation model, specifically, calculate the basic rated dynamic load of the raceway, calculate the roller load corresponding to the basic rated dynamic load of the raceway, slice along the roller element line direction, calculate the roller slice load corresponding to the basic rated dynamic load of the ring, calculate the roller slice load corresponding to the equivalent dynamic load of the ring, and calculate the fatigue life of the main bearing based on the roller load and the roller slice load.

[0011] Optionally, in S1, the roller distribution angle is calculated as follows:

[0012]

[0013] in, is the main push roller distribution angle, Z1 is the number of main push rollers, is the auxiliary push roller distribution angle, Z2 is the number of auxiliary push rollers, is the radial roller distribution angle, Z3 is the number of radial rollers;

[0014] The calculation formula of the roller elastic deformation is as follows:

[0015]

[0016] in, Indicates the elastic deformation of the roller at the distribution angle of the main push roller, Indicates the elastic deformation of the roller at the auxiliary push roller distribution angle, Indicates the roller elastic deformation at the radial roller distribution angle, D pw1 、D pw2 G are the distribution circle diameters of the main and auxiliary rollers respectively; a , G r are the axial clearance and radial clearance of the main bearing respectively; δ a , δ r , θ are the axial displacement, radial displacement and angular displacement of the inner ring respectively;

[0017] The balanced equation is expressed as follows:

[0018]

[0019] Among them, Fa Indicates the axial force, F r Indicates radial force, M k represents the overturning moment;

[0020] The empirical formula used to express the relationship between the elastic deformation of the roller and the load on the roller is as follows:

[0021]

[0022] in, L wei is the effective length of the roller, i=1,2,3, v1 and v2 represent the Poisson's ratio of the roller and raceway materials, and E1 and E2 represent the elastic modulus of the roller and raceway materials.

[0023] Optionally, in S2, the shaping function is specifically a shaping function of the roller along the element line direction, and the shaping function is determined by the shaping method of the roller.

[0024] Optionally, in S2, the surface function of the roller radial direction is as follows:

[0025]

[0026] Among them, z2(y) represents the surface function of the roller radial direction, D we represents the nominal diameter of the roller, z1(x) represents the roller shaping function along the element line direction;

[0027] The surface function of the roller contact area is as follows:

[0028] z(x,y)=z1(x)+z2(y);

[0029] Where z(x,y) represents the surface function of the roller contact area.

[0030] Optionally, in S3, the calculation expression of the contact stress distribution function is as follows:

[0031]

[0032] Where P(x, y) is the contact stress distribution function; Q is the load borne by the roller; δ is the elastic approach of the two objects when elastic deformation occurs; S is the size of the actual contact area; (x, y) and (x', y') are the coordinates of the two points in the contact area;

[0033] The expressions for the contact stress P(y) at the coordinate y along the roller line and the load q(y) on the roller are as follows:

[0034] P(y)=P(0,y);

[0035]

[0036] Among them, b y Represents the width of the contact area S at position y along the scrolling direction.

[0037] Optionally, in S4, the calculation expression for the fatigue life of the main bearing is as follows:

[0038]

[0039] Among them, L 10 represents the fatigue life of the main bearing, q iu,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the rotating state, q iv,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the static state, q iu,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the rotating state, q iv,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the static state.

[0040] Optionally, in S4, the roller load corresponding to the basic dynamic load rating of the raceway is calculated as follows:

[0041] Get the basic dynamic load rating of the raceway using the following expression:

[0042]

[0043] Among them, C i Indicates the basic rated dynamic load of the raceway, i = 1 indicates the main thrust raceway, i = 2 indicates the auxiliary thrust raceway, and i = 3 indicates the radial raceway; in the calculation of the main thrust raceway and the auxiliary thrust raceway, b m =1, In the calculation of radial raceway, b m3 =1.1,

[0044] The roller loads corresponding to the basic dynamic load rating of the raceway are divided into static and rotating states:

[0045] The roller load calculation method for the main thrust raceway and the auxiliary thrust raceway in the static state and the rotating state is the same, and the expression is as follows:

[0046]

[0047] The roller load expression of the radial raceway in the rotating state is as follows:

[0048]

[0049] The roller load expression of the radial raceway in the stationary state is as follows:

[0050]

[0051] Optionally, in S4, the roller slice load is calculated as follows:

[0052] Slice the roller along the roller element line and calculate the roller slice load corresponding to the basic rated dynamic load of the ring. The expression is as follows:

[0053] Main thrust roller and auxiliary thrust roller in stationary and rotating state:

[0054] Radial raceway in rotating state:

[0055] Radial raceway in stationary state:

[0056] Where m is the number of roller slices, P i,kj is the contact stress of the jth slice of the kth roller on the i-th raceway; q i,kj is the load of the jth slice of the kth roller on the i-th raceway;

[0057] Calculate the roller slice load corresponding to the equivalent dynamic load of the ring as follows:

[0058] The main push roller and the auxiliary push roller in the rotating state:

[0059] Main thrust roller and auxiliary thrust roller in stationary state:

[0060] Radial raceway in rotating state:

[0061] Radial raceway in stationary state:

[0062] Additionally, the present invention also includes a computer device comprising a memory and a processor;

[0063] The memory is used to store a computer program that can be executed on the processor;

[0064] The processor is used to implement the steps of the above-mentioned method for calculating the fatigue life of the main bearing of the shield machine when executing the computer program.

[0065] In addition, the present invention also includes a computer-readable storage medium having a computer program stored thereon. When the computer program is executed by a processor, the steps of the method for calculating fatigue life of a main bearing of a shield machine as described above are implemented.

[0066] The application of the technical solution of the present invention has the following beneficial effects:

[0067] The present invention introduces roller modification into the calculation of main bearing fatigue life. The calculation results can provide a quantitative evaluation of the quality of roller modification. In addition, the present invention calculates the load distribution and contact stress separately, which reduces the calculation difficulty.

[0068] In addition to the above-described objects, features and advantages, the present invention has other objects, features and advantages. The present invention will be further described in detail below with reference to the accompanying drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0069] In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0070] Figure 1 This is a flowchart of the steps of a method for calculating fatigue life of a main bearing of a shield machine in a preferred embodiment of the present invention;

[0071] Figure 2 This is a main bearing fatigue life distribution diagram corresponding to different crown modification coefficients in a preferred embodiment of the present invention. DETAILED DESCRIPTION

[0072] In order to enable those skilled in the art to better understand the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments. Obviously, the embodiments described 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 work are within the scope of protection of the present invention.

[0073] like Figure 1 As shown, this embodiment provides a method for calculating the fatigue life of a shield machine main bearing, comprising the following steps:

[0074] S1: Establish a main bearing load distribution calculation model. Specifically, obtain the roller distribution angles on the main thrust raceway, auxiliary thrust raceway, and radial raceway, calculate the roller elastic deformation at the roller distribution angles, establish the equilibrium equations for the isolator composed of the roller and inner ring under axial force, radial force, and overturning moment, and establish the main bearing load distribution calculation model based on the roller elastic deformation, equilibrium equation, and empirical formula to calculate the load on each roller.

[0075] S2: establishing a surface function of the roller contact area, specifically, calculating the roller radial surface function according to the shaping function, and obtaining the surface function of the roller contact area based on the roller radial surface function and the shaping function;

[0076] S3: Establish a cylindrical roller linear contact stress calculation model. Specifically, based on the surface function of the roller contact area, the contact stress distribution function and the contact area area are calculated, and the contact stress along the roller element line direction and the load on the roller are calculated.

[0077] S4: Establish a main bearing fatigue life calculation model, specifically, calculate the basic rated dynamic load of the raceway, calculate the roller load corresponding to the basic rated dynamic load of the raceway, slice along the roller element line direction, calculate the roller slice load corresponding to the basic rated dynamic load of the ring, calculate the roller slice load corresponding to the equivalent dynamic load of the ring, and calculate the fatigue life of the main bearing based on the roller load and the roller slice load.

[0078] Optionally, in S1, the roller distribution angle is calculated as follows:

[0079]

[0080] in, is the main push roller distribution angle, Z1 is the number of main push rollers, is the auxiliary push roller distribution angle, Z2 is the number of auxiliary push rollers, is the radial roller distribution angle, and Z3 is the number of radial rollers.

[0081] The calculation formula of the roller elastic deformation is as follows:

[0082]

[0083] in, Indicates the elastic deformation of the roller at the distribution angle of the main push roller, Indicates the elastic deformation of the roller at the auxiliary push roller distribution angle, Indicates the roller elastic deformation at the radial roller distribution angle, D pw1 、D pw2 G are the distribution circle diameters of the main and auxiliary rollers respectively; a , G r are the axial clearance and radial clearance of the main bearing respectively; δ a , δ r , θ are the axial displacement, radial displacement and angular displacement of the inner ring respectively;

[0084] The equilibrium equation of the isolator composed of the roller and the inner ring under axial force, radial force and overturning moment is constructed. Solving the equilibrium equation can obtain the axial displacement, radial displacement and angular displacement of the inner ring. The expression of the equilibrium equation is as follows:

[0085]

[0086] Among them, F a Indicates the axial force, F r Indicates radial force, M k represents the overturning moment;

[0087] According to the empirical formula given by Palmgren, the empirical formula is used to express the relationship between the elastic deformation of the roller and the load on the roller. Substituting the axial displacement, radial displacement and angular displacement of the inner ring into the empirical formula, the load on each roller can be calculated. The expression of the empirical formula is as follows:

[0088]

[0089] in, L wei is the effective length of the roller, i=1,2,3, v1 and v2 represent the Poisson's ratio of the roller and raceway materials, and E1 and E2 represent the elastic modulus of the roller and raceway materials.

[0090] Optionally, in S2, the shaping function is specifically a shaping function of the roller along the element line direction, and the shaping function is determined by the shaping method of the roller. In this embodiment, the expression of the logarithmic shaping formula is as follows:

[0091]

[0092] Where ξ is the convexity coefficient; A is the modification coefficient, which is generally taken as 3.5×10 -4 D we , where D we is the nominal diameter of the roller (mm), μ is the Poisson's ratio of the roller, and E is the elastic modulus of the roller (N / mm 2 );L we L is the effective length of the roller (mm), we =L w -2r,L w is the total length of the roller (mm), and r is the radius of the roller corner (mm).

[0093] Optionally, in S2, the surface function of the roller radial direction is as follows:

[0094]

[0095] Among them, z2(y) represents the surface function of the roller radial direction, D we represents the nominal diameter of the roller, z1(x) represents the roller shaping function along the element line direction;

[0096] The surface function of the roller contact area is as follows:

[0097] z(x,y)=z1(x)+z2(y);

[0098] Where z(x, y) represents the surface function of the roller contact area.

[0099] Optionally, in S3, the calculation expression of the contact stress distribution function is as follows:

[0100]

[0101] Where P(x, y) is the contact stress distribution function; Q is the load borne by the roller; δ is the elastic approach of the two objects when elastic deformation occurs; S is the size of the actual contact area; (x, y) and (x', y') are the coordinates of the two points in the contact area;

[0102] The expressions for the contact stress P(y) at the coordinate y along the roller line and the load q(y) on the roller are as follows:

[0103]

[0104] Among them, b y Represents the width of the contact area S at position y along the scrolling direction.

[0105] Optionally, in S4, the calculation expression for the fatigue life of the main bearing is as follows:

[0106]

[0107] Among them, L 10 represents the fatigue life of the main bearing, q iu,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the rotating state, q iv,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the static state, q iu,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the rotating state, q iv,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the static state.

[0108] Optionally, in S4, the roller load corresponding to the basic dynamic load rating of the raceway is calculated as follows:

[0109] Get the basic dynamic load rating of the raceway using the following expression:

[0110]

[0111] Among them, C iIndicates the basic rated dynamic load of the raceway, i = 1 indicates the main thrust raceway, i = 2 indicates the auxiliary thrust raceway, and i = 3 indicates the radial raceway; in the calculation of the main thrust raceway and the auxiliary thrust raceway, b m =1, In the calculation of radial raceway, b m3 =1.1,

[0112] The roller loads corresponding to the basic dynamic load rating of the raceway are divided into static and rotating states:

[0113] The roller load calculation method for the main thrust raceway and the auxiliary thrust raceway in the static state and the rotating state is the same, and the expression is as follows:

[0114]

[0115] The roller load expression of the radial raceway in the rotating state is as follows:

[0116]

[0117] The roller load expression of the radial raceway in the stationary state is as follows:

[0118]

[0119] Optionally, in S4, the roller slice load is calculated as follows:

[0120] Slice the roller along the roller element line and calculate the roller slice load corresponding to the basic rated dynamic load of the ring. The expression is as follows:

[0121] Main thrust roller and auxiliary thrust roller in stationary and rotating state:

[0122] Radial raceway in rotating state:

[0123] Radial raceway in stationary state:

[0124] Where m is the number of roller slices, P i,kj is the contact stress of the jth slice of the kth roller on the i-th raceway; q i,kj is the load of the jth slice of the kth roller on the i-th raceway;

[0125] Calculate the roller slice load corresponding to the equivalent dynamic load of the ring as follows:

[0126] The main push roller and the auxiliary push roller in the rotating state:

[0127] Main thrust roller and auxiliary thrust roller in stationary state:

[0128] Radial raceway in rotating state:

[0129] Radial raceway in stationary state:

[0130] Taking the main bearing of a shield machine as the research object, the fatigue life of the main bearing corresponding to different crown modification coefficients ξ is as follows: Figure 2 shown.

[0131] In addition, this embodiment also provides a computer device, including a memory and a processor;

[0132] The memory is used to store a computer program that can be executed on the processor;

[0133] The processor is used to implement the steps of the above-mentioned method for calculating the fatigue life of the main bearing of the shield machine when executing the computer program.

[0134] Exemplarily, the computer program may be divided into one or more modules / units, which are stored in the memory and executed by the processor to implement the present invention. The one or more modules / units may be a series of computer program instruction segments capable of implementing specific functions, and the instruction segments are used to describe the execution process of the computer program in the computer device.

[0135] The computer device may be a mobile phone, desktop computer, laptop, PDA, cloud server, or other computing device. The computer device may include, but is not limited to, a processor and memory. For example, the computer device may also include input and output devices, network access devices, buses, etc.

[0136] The processor may be a central processing unit (CPU), other general-purpose processors, digital signal processors (DSP), application-specific integrated circuits (ASIC), field-programmable gate arrays (FPGA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, etc. A general-purpose processor may be a microprocessor or any conventional processor, etc. The processor is the control center of the computer device and connects various parts of the entire computer device using various interfaces and lines.

[0137] The memory can be used to store the computer program and / or module, and the processor implements the computer program by running or executing the computer program and / or module stored in the memory, and calling the data stored in the memory. The memory can mainly include a program storage area and a data storage area, wherein the program storage area can store an operating system, at least one application required for a function (such as a sound playback function, an image playback function, etc.); the data storage area can store data created based on the use of the mobile phone (such as audio data, a phone book, etc.). In addition, the memory can include a high-speed random access memory and can also include a non-volatile memory, such as a hard disk, a memory, a plug-in hard disk, a smart memory card (Smart Media Card, SMC), a secure digital (Secure Digital, SD) card, a flash card (Flash Card), at least one disk storage device, a flash memory device, or other volatile solid-state storage device.

[0138] Wherein, if the module / unit integrated in the computer device is implemented in the form of a software functional unit and sold or used as an independent product, it can be stored in a computer-readable storage medium. Based on this understanding, the present invention implements all or part of the process in the above-mentioned embodiment method, and can also be completed by instructing the relevant hardware through a computer program. The computer program can be stored in a computer-readable storage medium, and when the computer program is executed by the processor, it can implement the steps of the above-mentioned various method embodiments. Wherein, the computer program includes computer program code, and the computer program code can be in source code form, object code form, executable file or some intermediate form. The computer-readable medium may include: any entity or device that can carry the computer program code, recording medium, U disk, mobile hard disk, magnetic disk, optical disk, computer memory, read-only memory (ROM, Read-Only Memory), random access memory (RAM, Random Access Memory), electrical carrier signal, telecommunication signal and software distribution medium, etc.

[0139] In addition, an embodiment of the present invention further provides a computer-readable storage medium having a computer program stored thereon. When the computer program is executed by a processor, the steps of the above-mentioned method for calculating fatigue life of a main bearing of a shield machine are implemented.

[0140] This embodiment proposes a fatigue life calculation method for three-row roller bearings for shield machines that takes roller modification into account. Roller modification is introduced into the fatigue life calculation process of the main bearing. The method of this embodiment also calculates the load distribution and contact stress separately, which reduces the calculation difficulty. The application of this embodiment method can provide a quantitative evaluation of the advantages and disadvantages of roller modification.

[0141] It should be noted that the device embodiments described above are merely illustrative, wherein the units described as separate components may or may not be physically separate, and 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 may be selected based on actual needs to achieve the objectives of this embodiment.

[0142] The foregoing description is merely a preferred embodiment of the present invention and is not intended to limit the present invention. Those skilled in the art will readily appreciate that various modifications and variations of the present invention are possible. Any modifications, equivalent substitutions, or improvements made within the spirit and principles of the present invention are intended to be within the scope of protection of the present invention.

Claims

1. A method for calculating the fatigue life of a shield machine main bearing, characterized in that: The following steps are involved: S1: Establish a main bearing load distribution calculation model. Specifically, obtain the roller distribution angles on the main thrust raceway, auxiliary thrust raceway, and radial raceway, calculate the roller elastic deformation at the roller distribution angles, establish the equilibrium equations for the isolator composed of the roller and inner ring under axial force, radial force, and overturning moment, and establish the main bearing load distribution calculation model based on the roller elastic deformation, equilibrium equation, and empirical formula to calculate the load on each roller. S2: establishing a surface function of the roller contact area, specifically, calculating the roller radial surface function according to the shaping function, and obtaining the surface function of the roller contact area based on the roller radial surface function and the shaping function; S3: Establish a cylindrical roller linear contact stress calculation model. Specifically, based on the surface function of the roller contact area, the contact stress distribution function and the contact area area are calculated, and the contact stress along the roller element line direction and the load on the roller are calculated. S4: Establish a main bearing fatigue life calculation model, specifically, calculate the basic rated dynamic load of the raceway, calculate the roller load corresponding to the basic rated dynamic load of the raceway, slice along the roller element line direction, calculate the roller slice load corresponding to the basic rated dynamic load of the ring, calculate the roller slice load corresponding to the equivalent dynamic load of the ring, and calculate the fatigue life of the main bearing based on the roller load and the roller slice load.

2. The method for calculating fatigue life of main bearing of shield machine according to claim 1, characterized in that: In S1, the roller distribution angle is calculated as follows: in, is the main push roller distribution angle, Z1 is the number of main push rollers, is the auxiliary push roller distribution angle, Z2 is the number of auxiliary push rollers, is the radial roller distribution angle, Z3 is the number of radial rollers; The calculation formula of the roller elastic deformation is as follows: in, Indicates the elastic deformation of the roller at the distribution angle of the main push roller, Indicates the elastic deformation of the roller at the auxiliary push roller distribution angle, Indicates the roller elastic deformation at the radial roller distribution angle, D pw1 、D pw2 G are the distribution circle diameters of the main and auxiliary rollers respectively; a , G r are the axial clearance and radial clearance of the main bearing respectively; δ a , δ r , θ are the axial displacement, radial displacement and angular displacement of the inner ring respectively; The balanced equation is expressed as follows: Among them, F a Indicates the axial force, F r Indicates radial force, M k represents the overturning moment; The empirical formula used to express the relationship between the elastic deformation of the roller and the load on the roller is as follows: in, L wei is the effective length of the roller, i=1,2,3, v1 and v2 represent the Poisson's ratio of the roller and raceway materials, and E1 and E2 represent the elastic modulus of the roller and raceway materials.

3. The method for calculating fatigue life of main bearing of shield machine according to claim 2, characterized in that: In S2, the shaping function is specifically a shaping function of the roller along the element line direction, and the shaping function is determined by the shaping method of the roller.

4. The method for calculating fatigue life of main bearing of shield machine according to claim 3, characterized in that: In S2, the surface function of the roller radial direction is as follows: Among them, z2(y) represents the surface function of the roller radial direction, D we represents the nominal diameter of the roller, z1(x) represents the roller shaping function along the element line direction; The surface function of the roller contact area is as follows: z(x,y)=z1(x)+z2(y); Where z(x, y) represents the surface function of the roller contact area.

5. The method for calculating fatigue life of main bearing of shield machine according to claim 4, characterized in that: In S3, the calculation expression of the contact stress distribution function is as follows: Where P(x, y) is the contact stress distribution function; Q is the load borne by the roller; δ is the elastic approach of the two objects when elastic deformation occurs; S is the size of the actual contact area; (x, y) and (x', y') are the coordinates of the two points in the contact area; The expressions for the contact stress P(y) at the coordinate y along the roller line and the load q(y) on the roller are as follows: P(y)=P(0,y); Among them, b y Represents the width of the contact area S at position y along the scrolling direction.

6. The method for calculating fatigue life of main bearing of shield machine according to claim 5, characterized in that: In S4, the calculation expression of main bearing fatigue life is as follows: Among them, L 10 represents the fatigue life of the main bearing, q iu,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the rotating state, q iv,c Indicates the roller load corresponding to the basic dynamic load rating of the raceway in the static state, q iu,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the rotating state, q iv,k Indicates the roller slice load corresponding to the basic dynamic load rating of the ring in the static state.

7. The method for calculating fatigue life of main bearing of shield machine according to claim 6, characterized in that: In S4, the roller load corresponding to the basic dynamic load rating of the raceway is calculated as follows: Get the basic dynamic load rating of the raceway using the following expression: Among them, C i Indicates the basic rated dynamic load of the raceway, i = 1 indicates the main thrust raceway, i = 2 indicates the auxiliary thrust raceway, and i = 3 indicates the radial raceway; in the calculation of the main thrust raceway and the auxiliary thrust raceway, b m =1,f ci =472.45388×0.73×0.85·γ i 2 / 9 , In the calculation of radial raceway, b m3 =1.1, The roller loads corresponding to the basic dynamic load rating of the raceway are divided into static and rotating states: The roller load calculation method for the main thrust raceway and the auxiliary thrust raceway in the static state and the rotating state is the same, and the expression is as follows: The roller load expression of the radial raceway in the rotating state is as follows: The roller load expression of the radial raceway in the stationary state is as follows:

8. The method for calculating fatigue life of main bearing of shield machine according to claim 7, characterized in that: In S4, the roller slice load is calculated as follows: Slice the roller along the roller element line and calculate the roller slice load corresponding to the basic rated dynamic load of the ring. The expression is as follows: Main thrust roller and auxiliary thrust roller in stationary and rotating state: Radial raceway in rotating state: Radial raceway in stationary state: Where m is the number of roller slices, P i,kj is the contact stress of the jth slice of the kth roller on the i-th raceway; q i,kj is the load of the jth slice of the kth roller on the i-th raceway; Calculate the roller slice load corresponding to the equivalent dynamic load of the ring as follows: The main push roller and the auxiliary push roller in the rotating state: Main thrust roller and auxiliary thrust roller in stationary state: Radial raceway in rotating state: Radial raceway in stationary state:

9. A computer device, characterized in that: including memory and processor; The memory is used to store a computer program that can be executed on the processor; The processor is configured to implement the steps of the method for calculating fatigue life of a main bearing of a shield machine according to any one of claims 1 to 8 when executing the computer program.

10. A computer-readable storage medium, characterized in that The computer-readable storage medium stores a computer program, which, when executed by a processor, implements the steps of the method for calculating fatigue life of a main bearing of a shield machine according to any one of claims 1 to 8.

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