Load distribution calculation method and system, equipment and medium for main bearing of heading machine

Abstract

The application discloses a kind of load distribution calculation method and system of heading machine main bearing, equipment, medium, the method first determines the modification mode and modification function of roller, then obtains the elastic deformation between roller and raceway by non-Hertz contact theory calculation, then least square method is used to data fitting binary variable of load and elastic deformation, the fitting contact stiffness of each roller and fitting load deformation index are obtained, then main bearing statics balance analysis can obtain the axial displacement, radial displacement and angular displacement of bearing inner ring, and then the load distribution of main bearing can be calculated.The load distribution calculation method is based on non-Hertz contact theory to carry out contact stiffness fitting, and then the load distribution of roller is calculated based on fitting result, the influence of roller modification on load distribution is fully considered, so that the calculated load distribution is closer to actual value, and the accuracy of heading machine main bearing load distribution calculation is greatly improved.

Description

Technical Field

[0001] This invention relates to the field of bearing load distribution analysis technology, and in particular, to a method and system for calculating the load distribution of a tunneling machine main bearing, an electronic device, and a computer-readable storage medium. Background Technology

[0002] A tunnel boring machine (TBM) is a specialized piece of engineering machinery used for tunnel excavation. During underground construction, a cutterhead rotating on a main bearing continuously breaks up rock and excavates, forming a complete tunnel cross-section. It is a factory-integrated, assembly-line tunnel construction equipment combining mechanical, electrical, hydraulic, optical, and pneumatic systems. Currently, the main bearings in TBMs widely adopt a three-row, three-column roller bearing structure, specifically including an inner ring, outer ring, cage, and rollers. During excavation, the main bearings in the TBM need to withstand combined loads such as axial force, radial force, and overturning moment, making them typical low-speed, heavy-load bearings. To improve the load-bearing capacity of the main bearing, the rollers are generally modified to reduce stress concentration at the contact edge between the roller and the raceway, making the stress distribution more uniform along the generatrix of the roller. Currently, in calculating the load distribution of the main bearing, the relationship between roller load and deformation is obtained using the empirical formula given by Palmgren. However, this formula is quite old and analyzes straight generatrix rollers, without considering the impact of roller modification on the calculation of the main bearing load distribution. Therefore, if the Palmgren formula is still used to calculate the load distribution of the main bearing, there will be a large error in the calculation accuracy, resulting in poor accuracy of the load distribution calculation results of the main bearing. Summary of the Invention

[0003] This invention provides a method and system for calculating the load distribution of a tunneling machine main bearing, an electronic device, and a computer-readable storage medium to solve the technical problem that the existing technology does not consider the influence of roller modification on the load distribution calculation of the main bearing, resulting in poor accuracy of the load distribution calculation results of the main bearing.

[0004] According to one aspect of the present invention, a method for calculating the load distribution of a tunneling machine main bearing is provided, comprising the following:

[0005] Obtain the profile modification method and modification function of the main bearing rollers;

[0006] A series of loads were applied to the main push roller, the auxiliary push roller, and the radial roller respectively, and a series of elastic deformations between each roller and the raceway were calculated based on the non-Hertz contact theory and the shape modification function.

[0007] The least squares method was used to fit the data of the binary variables composed of load and elastic deformation, and the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller were obtained respectively.

[0008] Static equilibrium analysis of the main bearing is performed based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring.

[0009] The load distribution of the main bearing is calculated based on the axial, radial, and angular displacements of the inner ring of the bearing.

[0010] Furthermore, the process of calculating a series of elastic deformations between each roller and raceway based on non-Hertz contact theory and shape modification functions is specifically as follows:

[0011] The radial surface function of the roller is obtained by converting the roller's shape modification function;

[0012] The surface function of the contact area of ​​the roller is obtained by combining the roller's shape modification function and radial surface function;

[0013] The elastic deformation between the roller and the raceway is calculated based on the surface function of the contact area of ​​the roller and the non-Hertz line contact equation.

[0014] Furthermore, the expression for the non-Hertz line contact equation is:

[0015]

[0016] Where P(x,y) represents the contact stress distribution, F represents the load borne by the roller, z0(x,y) represents the initial distance between the roller contact surface and the raceway contact surface, δ represents the elastic convergence between the roller and the raceway when elastic deformation occurs, S represents the contact area under load, (x,y) and (x′,y′) represent the coordinates of two points in the contact area, and E′ represents the comprehensive material parameters. v1 and v2 represent the Poisson's ratios of the roller material and the raceway material, respectively, and E1 and E2 represent the elastic moduli of the roller material and the raceway material, respectively.

[0017] Furthermore, the process of using the least squares method to fit the data of the binary variables composed of load and elastic deformation to obtain the fitted contact stiffness and fitted load deformation index of the main pushing roller, auxiliary pushing roller, and radial roller respectively is as follows:

[0018] Based on the Palmgren formula, a fitting relationship is constructed, which is: F = Kδ n Where F represents the load borne by the roller, K represents the fitted contact stiffness, δ represents the elastic deformation between the roller and the raceway, and n represents the fitted load deformation index.

[0019] After converting the above fitting relationship into a logarithmic function, we obtain the fitting function as follows:

[0020] Based on a series of load data, a series of elastic deformations, and a fitting function, the least squares method was used to fit the fitting function, and the fitted contact stiffness and fitted load deformation index of the main push roller, the auxiliary push roller, and the radial roller were obtained respectively.

[0021] Furthermore, during the static equilibrium analysis of the main bearing, the axial static equilibrium equation is constructed as follows: Among them, F a M represents the axial load. k The value represents the overturning moment, K1 and K2 represent the fitted contact stiffness of the main push roller and the auxiliary push roller, respectively, and n1 and n2 represent the fitted load deformation exponents of the main push roller and the auxiliary push roller, respectively. This represents the elastic deformation of the i-th main thrust roller. This represents the elastic deformation of the i-th auxiliary push roller. This represents the distribution angle of the i-th main pusher roller. This represents the distribution angle of the i-th auxiliary pusher roller. Z1 represents the number of main push rollers. Z2 represents the number of auxiliary push rollers, D pw1 and D pw2 These represent the distribution circle diameters of the main push roller and the auxiliary push roller, respectively. θ represents the angular displacement of the inner ring of the bearing, δ a P represents the axial displacement of the bearing inner ring. a Indicates axial clearance;

[0022] The Newton-Raphson algorithm is used to solve the problem and obtain the axial displacement δ of the bearing inner ring. a And angular displacement θ.

[0023] Furthermore, during the static equilibrium analysis of the main bearing, the radial static equilibrium equation is constructed as follows: Among them, F r K3 represents the radial load, K3 represents the fitted contact stiffness of the radial rollers, and Z3 represents the number of radial rollers. This represents the distribution angle of the i-th radial roller. This represents the elastic deformation of the i-th radial roller. δ r P represents the radial displacement of the bearing inner ring. r Indicates radial clearance;

[0024] The Newton-Raphson algorithm is used to solve the problem, and the radial displacement δ of the bearing inner ring is obtained. r .

[0025] Furthermore, the load distribution of the main bearing is as follows:

[0026] The contact load of the i-th main pusher roller is:

[0027] The contact load of the i-th auxiliary push roller is:

[0028] The contact load of the i-th radial roller is:

[0029] In addition, the present invention also provides a load distribution calculation system for the main bearing of a tunneling machine, comprising:

[0030] The data acquisition module is used to acquire the modification method and modification function of the main bearing rollers;

[0031] The contact analysis module is used to apply a series of loads to the main push roller, auxiliary push roller and radial roller respectively, and calculate a series of elastic deformations between each roller and the raceway based on non-Hertz contact theory and shape modification function.

[0032] The data fitting module is used to fit the binary variables composed of load and elastic deformation using the least squares method, and to obtain the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller respectively.

[0033] The balance analysis module is used to perform static balance analysis of the main bearing based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller, and to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring.

[0034] The load analysis module is used to calculate the load distribution of the main bearing based on the axial, radial, and angular displacements of the bearing inner ring.

[0035] In addition, the present invention also provides an electronic device, including a processor and a memory, wherein the memory stores a computer program, and the processor executes the steps of the method described above by calling the computer program stored in the memory.

[0036] In addition, the present invention provides a computer-readable storage medium for storing a computer program for calculating the load distribution of the main bearing of a tunneling machine, wherein the computer program executes the steps of the method described above when running on a computer.

[0037] The present invention has the following effects:

[0038] The load distribution calculation method for the main bearing of a tunneling machine of the present invention first determines the profile of the main bearing rollers. After obtaining the profile function of the rollers, the elastic deformation between the rollers and raceways is calculated using non-Hertz contact theory. Non-Hertz contact theory can accurately calculate the stress magnitude in the contact area and the elastic deformation between the rollers and raceways under the condition of roller profile modification. Then, the least squares method is used to fit the data of the binary variables composed of load and elastic deformation, which can obtain the fitted contact stiffness and fitted load deformation index of the main thrust roller, auxiliary thrust roller, and radial roller. Then, the static equilibrium analysis of the main bearing is performed to obtain the axial displacement, radial displacement, and angular displacement of the inner ring of the bearing, and thus the load distribution of the main bearing can be calculated. The load distribution calculation method of the present invention, based on non-Hertz contact theory for contact stiffness fitting, and then calculating the roller load distribution based on the fitting results, fully considers the influence of roller profile modification on load distribution, making the calculated load distribution closer to the actual value, and greatly improving the accuracy of the load distribution calculation of the main bearing of the tunneling machine.

[0039] In addition, the load distribution calculation system for the main bearing of the tunneling machine of the present invention also has the above-mentioned advantages.

[0040] In addition to the objectives, features, and advantages described above, the present invention has other objectives, features, and advantages. The invention will now be described in further detail with reference to the figures. Attached Figure Description

[0041] The accompanying drawings, which form part of this application, are used to provide a further understanding of the invention. The illustrative embodiments of the invention and their descriptions are used to explain the invention and do not constitute an undue limitation of the invention. In the drawings:

[0042] Figure 1 This is a flowchart illustrating the load distribution calculation method for the main bearing of a tunneling machine according to a preferred embodiment of the present invention.

[0043] Figure 2 yes Figure 1 A schematic diagram of the sub-process of step S2.

[0044] Figure 3 This is a comparative diagram showing the main pusher roller contact stiffness calculated using a non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula, respectively, in a preferred embodiment of the present invention.

[0045] Figure 4 This is a comparative schematic diagram showing the auxiliary roller contact stiffness calculated using a non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula in a preferred embodiment of the present invention.

[0046] Figure 5This is a comparative schematic diagram showing the radial roller contact stiffness calculated using a non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula in a preferred embodiment of the present invention.

[0047] Figure 6 This is a comparative schematic diagram showing the distribution of the main thrust roller load calculated using the non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula in a preferred embodiment of the present invention.

[0048] Figure 7 This is a comparative schematic diagram showing the load distribution of the auxiliary push roller calculated using the non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula in a preferred embodiment of the present invention.

[0049] Figure 8 This is a comparative schematic diagram showing the radial roller load distribution calculated using the non-Hertz contact stiffness fitting formula and the existing Palmgren calculation formula in a preferred embodiment of the present invention.

[0050] Figure 9 This is a schematic diagram of the module structure of a load distribution calculation system for the main bearing of a tunneling machine according to another embodiment of the present invention. Detailed Implementation

[0051] The embodiments of the present invention will be described in detail below with reference to the accompanying drawings. However, the present invention can be implemented in many different ways as defined and covered below.

[0052] Understandable, such as Figure 1 As shown, a preferred embodiment of the present invention provides a method for calculating the load distribution of a tunneling machine main bearing, including the following:

[0053] Step S1: Obtain the profile modification method and profile modification function of the main bearing rollers;

[0054] Step S2: Apply a series of loads to the main push roller, auxiliary push roller and radial roller respectively, and calculate a series of elastic deformations between each roller and the raceway based on the non-Hertz contact theory and the shape modification function.

[0055] Step S3: Use the least squares method to fit the data of the binary variables composed of load and elastic deformation, and obtain the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller respectively.

[0056] Step S4: Perform static balance analysis of the main bearing based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring.

[0057] Step S5: Calculate the load distribution of the main bearing based on the axial displacement, radial displacement and angular displacement of the inner ring of the bearing.

[0058] It is understood that the load distribution calculation method for the main bearing of the tunneling machine in this embodiment first determines the shape modification of the main bearing rollers. After obtaining the roller shape modification function, the elastic deformation between the rollers and raceways is calculated using non-Hertz contact theory. Non-Hertz contact theory can accurately calculate the stress magnitude in the contact area and the elastic deformation between the rollers and raceways under the condition of roller shape modification. Then, the least squares method is used to fit the data of the binary variables composed of load and elastic deformation, which can fit the fitted contact stiffness and fitted load deformation index of the main thrust roller, auxiliary thrust roller, and radial roller. Then, the static equilibrium analysis of the main bearing can be performed to obtain the axial displacement, radial displacement, and angular displacement of the inner ring of the bearing, and then the load distribution of the main bearing can be calculated. The load distribution calculation method of this invention, based on non-Hertz contact theory, performs contact stiffness fitting, and then calculates the roller load distribution based on the fitting results. It fully considers the influence of roller shape modification on load distribution, making the calculated load distribution closer to the actual value, and greatly improving the accuracy of the load distribution calculation of the main bearing of the tunneling machine.

[0059] It is understood that in step S1, the roller modification methods include various methods such as no modification for the straight generatrix, logarithmic modification, intersecting circular arc modification, and tangent circular arc modification. Once the roller modification method is determined, the corresponding modification function can be obtained. For example, the modification function expression for logarithmic modification is: Where A represents the shaping factor, which is typically taken as 3.5 × 10⁻⁶. -4 D we D we L indicates the nominal diameter of the roller (mm). we L represents the effective length of the roller (mm). we =L w -2r, L w The value represents the total length of the roller (mm), and r represents the fillet radius of the roller (mm). It is understood that current tunneling machine main bearings include three types of rollers: main thrust rollers, auxiliary thrust rollers, and radial rollers. Therefore, it is necessary to obtain the modification functions for these three types of rollers. Of course, in other embodiments of this invention, if the tunneling machine main bearing includes only one or two types of rollers, only one or two modification functions need to be obtained accordingly. The modification methods for each roller can be the same or different. Furthermore, for the same modification method, since the nominal diameter, effective length, fillet radius, and other parameters of the main thrust roller, auxiliary thrust roller, and radial roller are different, the modification functions for the main thrust roller, auxiliary thrust roller, and radial roller are all different.

[0060] Understandable, such as Figure 2As shown, in step S2, the process of calculating a series of elastic deformations between each roller and raceway based on non-Hertz contact theory and shape modification function is specifically as follows:

[0061] Step S21: Calculate the radial surface function of the roller based on the roller's shape modification function;

[0062] Step S22: Combine the roller's profile function and radial surface function to obtain the surface function of the roller's contact area;

[0063] Step S23: Calculate the elastic deformation between the roller and the raceway based on the surface function of the contact area of ​​the roller and the non-Hertz line contact equation.

[0064] Specifically, the radial surface function of the roller is expressed as: Therefore, after determining the roller's profile function z1(x), the radial surface function z2(y) of the roller can be calculated. The surface function of the roller contact area can then be expressed as: z(x,y)=z1(x)+z2(y). The expression for the non-Hertz line contact equation is:

[0065]

[0066] Where P(x,y) represents the contact stress distribution (N / mm) 2 F represents the load borne by the roller (N), z0(x,y) represents the initial distance between the roller contact surface and the raceway contact surface (mm), δ represents the elastic approach amount between the roller and the raceway when elastic deformation occurs (mm), i.e., the elastic deformation amount, S represents the contact area under the load, (x,y) and (x′,y′) represent the coordinates of two points in the contact area, and E′ represents the comprehensive material parameters (N / mm). 2 ), v1 and v2 represent the Poisson's ratios of the roller material and the raceway material, respectively, and E1 and E2 represent the elastic moduli of the roller material and the raceway material, respectively.

[0067] For the main push roller, auxiliary push roller, and radial roller, a series of load values ​​(F1, F2, ..., F) are applied individually. m This allows us to calculate a series of elastic deformations (δ1, δ2, ..., δ) between the roller and the raceway. m For example, a series of axial loads can be applied to the main push rollers and the auxiliary push rollers, and a series of radial loads can be applied to the radial rollers, so that a series of elastic deformations between the main push rollers and the raceway, between the auxiliary push rollers and the raceway, and between the radial rollers and the raceway can be calculated respectively.

[0068] It is understandable that non-Hertz contact theory can accurately calculate the stress in the contact area and the elastic deformation between the roller and the raceway, given a certain load on the roller and considering roller profile.

[0069] It is understood that although the elastic deformation between the roller and the raceway can be accurately calculated in step S2, the load on the roller cannot be directly calculated from the elastic deformation. Therefore, this invention uses the least squares method to fit the data of the binary variable composed of load and elastic deformation to obtain the contact stiffness fitting function of the modified roller, so as to facilitate load distribution calculation. Specifically, in step S3, the process of using the least squares method to fit the data of the binary variable composed of load and elastic deformation to obtain the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller is as follows:

[0070] Based on the Palmgren formula, a fitting relationship is constructed, which is: F = Kδ n Where F represents the load borne by the roller, K represents the fitted contact stiffness, δ represents the elastic deformation between the roller and the raceway, and n represents the fitted load deformation index.

[0071] After converting the above fitting relationship into a logarithmic function, we obtain the fitting function as follows:

[0072] Based on a series of load data, a series of elastic deformations, and a fitting function, the least squares method was used to fit the fitting function, and the fitted contact stiffness and fitted load deformation index of the main push roller, the auxiliary push roller, and the radial roller were obtained respectively.

[0073] Specifically, we first construct the fitting relationship based on the Palmgren formula: F = Kδ n To simplify the fitting process, a new relationship is constructed by performing a logarithmic transformation on the above fitting equation: ln(F) = ln(K) + n·ln(δ). Let... This allows us to obtain the contact stiffness fitting function for the modified roller: Then, the least squares method is used to evaluate the series of load values ​​(F1, F2, ..., F) in step S2. m ) and a series of elastic deformation quantities (δ1, δ2, ..., δ mBy performing data fitting, the fitted contact stiffness K and fitted load deformation index n of the rollers can be obtained. It can be understood that for the main pushing roller, the auxiliary pushing roller, and the radial roller, individual fitting is performed, thereby obtaining the fitted contact stiffness K1 and fitted load deformation index n1 for the main pushing roller, the fitted contact stiffness K2 and fitted load deformation index n2 for the auxiliary pushing roller, and the fitted contact stiffness K3 and fitted load deformation index n3 for the radial roller.

[0074] It can be understood that in step S4, by substituting the calculated fitted contact stiffness and fitted load deformation index of the main thrust roller, auxiliary thrust roller, and radial roller into the constructed static equilibrium equation of the tunneling machine main bearing, the axial displacement, radial displacement, and angular displacement of the bearing inner ring can be calculated. Specifically, in the process of performing the static equilibrium analysis of the main bearing, the constructed axial static equilibrium equation is as follows:

[0075] Among them, F a M represents the axial load (N). k The value represents the overturning moment (N×mm), K1 and K2 represent the fitted contact stiffness of the main push roller and the auxiliary push roller, respectively, and n1 and n2 represent the fitted load deformation exponents of the main push roller and the auxiliary push roller, respectively. This represents the elastic deformation of the i-th main thrust roller, i.e., the distribution angle is... The elastic deformation of the main thrust roller at that location. This represents the elastic deformation of the i-th auxiliary roller, i.e., the distribution angle is... The elastic deformation of the auxiliary push roller at the location. This represents the distribution angle of the i-th main pusher roller. This represents the distribution angle of the i-th auxiliary push roller. The distribution angle of the roller with the maximum load on both the main push raceway and the auxiliary push raceway is 0°. Z1 represents the number of main push rollers. Z2 represents the number of auxiliary push rollers, D pw1 and D pw2 These represent the distribution circle diameters (mm) of the main push roller and the auxiliary push roller, respectively. θ represents the angular displacement (rad) of the inner ring of the bearing, δ a P represents the axial displacement (mm) of the bearing inner ring. a The axial clearance is expressed in mm. Then, the Newton-Raphson algorithm is used to solve for the axial displacement δ of the bearing inner ring. a And angular displacement θ. Among them, the Newton-Raphson algorithm is a mature existing algorithm, and its specific principle will not be elaborated here.

[0076] Furthermore, during the static equilibrium analysis of the main bearing, the radial static equilibrium equation was constructed as follows: Among them, F r K3 represents the radial load, K3 represents the fitted contact stiffness of the radial rollers, and Z3 represents the number of radial rollers. This represents the distribution angle of the i-th radial roller. The distribution angle of the roller with the maximum load on the radial raceway is 0°. This represents the elastic deformation of the i-th radial roller. δ r P represents the radial displacement (mm) of the bearing inner ring. r The radial clearance (mm) is then represented. The Newton-Raphson algorithm is then used to solve for the radial displacement δ of the bearing inner ring. r .

[0077] It can be understood that in step S5, after solving for the axial displacement, radial displacement, and angular displacement of the bearing inner ring, the contact load of the main thrust roller, auxiliary thrust roller, and radial roller at any position angle can be calculated, which can be specifically expressed as:

[0078] The contact load of the i-th main pusher roller is:

[0079] The contact load of the i-th auxiliary push roller is:

[0080] The contact load of the i-th radial roller is:

[0081] This allows us to obtain the load distribution of the main bearing.

[0082] It is understood that, in order to demonstrate the effectiveness and innovativeness of the load distribution calculation method of this invention, the inventors of this application have also conducted a comparative verification with the existing Palmgren calculation method. Specifically, taking the data in Table 1 as an example, the load distribution calculation method of this invention and the existing Palmgren calculation method were used to calculate the contact stiffness and load distribution of the main push roller, auxiliary push roller, and radial roller, respectively. The calculation results are as follows: Figures 3 to 8 As shown in the comparison, it can be seen that the contact stiffness calculated using the non-Hertz contact stiffness fitting function of the present invention is less than the contact stiffness calculated by the Palmgren formula. There are also some differences in the load distribution calculation results, especially the load distribution results of the auxiliary push roller are quite different. The calculation results of the present invention are closer to the actual values.

[0083] In addition, such as Figure 9As shown, another embodiment of the present invention also provides a load distribution calculation system for the main bearing of a tunneling machine, preferably employing the load distribution calculation method described above. The system includes:

[0084] The data acquisition module is used to acquire the modification method and modification function of the main bearing rollers;

[0085] The contact analysis module is used to apply a series of loads to the main push roller, auxiliary push roller and radial roller respectively, and calculate a series of elastic deformations between each roller and the raceway based on non-Hertz contact theory and shape modification function.

[0086] The data fitting module is used to fit the binary variables composed of load and elastic deformation using the least squares method, and to obtain the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller respectively.

[0087] The balance analysis module is used to perform static balance analysis of the main bearing based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller, and to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring.

[0088] The load analysis module is used to calculate the load distribution of the main bearing based on the axial, radial, and angular displacements of the bearing inner ring.

[0089] It is understood that the load distribution calculation system for the main bearing of the tunneling machine in this embodiment first determines the shape modification method of the main bearing rollers. After obtaining the roller shape modification function, it calculates the elastic deformation between the rollers and the raceway using non-Hertz contact theory. Non-Hertz contact theory can accurately calculate the stress magnitude in the contact area and the elastic deformation between the rollers and the raceway under the condition of roller shape modification. Then, the least squares method is used to fit the data of the binary variables composed of load and elastic deformation, which can fit the fitted contact stiffness and fitted load deformation index of the main thrust roller, auxiliary thrust roller, and radial roller. Then, the static equilibrium analysis of the main bearing can be performed to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring, and then the load distribution of the main bearing can be calculated. The load distribution calculation system of this invention, based on non-Hertz contact theory, performs contact stiffness fitting, and then calculates the roller load distribution based on the fitting results. It fully considers the influence of roller shape modification on load distribution, making the calculated load distribution closer to the actual value, and greatly improving the accuracy of the load distribution calculation of the main bearing of the tunneling machine.

[0090] In addition, another embodiment of the present invention provides an electronic device including a processor and a memory, wherein the memory stores a computer program, and the processor executes the steps of the method described above by calling the computer program stored in the memory.

[0091] In addition, another embodiment of the present invention provides a computer-readable storage medium for storing a computer program for calculating the load distribution of the main bearing of a tunneling machine, wherein the computer program executes the steps of the method described above when run on a computer.

[0092] Common computer-readable storage media include: floppy disks, flexible disks, hard disks, magnetic tapes, any other magnetic media, CD-ROMs, any other optical media, punch cards, paper tape, any other physical media with perforated patterns, random access memory (RAM), programmable read-only memory (PROM), erasable programmable read-only memory (EPROM), flash erasable programmable read-only memory (FLASH-EPROM), any other memory chips or cartridges, or any other media readable by a computer. Instructions may further be transmitted or received by a transmission medium. The term transmission medium can include any tangible or intangible medium used to store, encode, or carry instructions for machine execution, and includes digital or analog communication signals or intangible media that facilitate communication of such instructions. Transmission media include coaxial cables, copper wires, and optical fibers, which contain conductors for transmitting a bus of computer data signals.

[0093] The above description is merely a preferred embodiment of the present invention and is not intended to limit the invention. Various modifications and variations can be made to the present invention by those skilled in the art. Any modifications, equivalent substitutions, improvements, etc., made within the spirit and principles of the present invention should be included within the scope of protection of the present invention.

[0094] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product implemented 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. The solutions in the embodiments of this application can be implemented in various computer languages, such as the object-oriented programming language Java and the interpreted scripting language JavaScript.

[0095] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. 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... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0096] 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.

[0097] 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.

[0098] Although preferred embodiments of this application have been described, those skilled in the art, upon learning the basic inventive concept, can make other changes and modifications to these embodiments. Therefore, the appended claims are intended to be interpreted as including the preferred embodiments as well as all changes and modifications falling within the scope of this application.

[0099] Obviously, those skilled in the art can make various modifications and variations to this application without departing from the spirit and scope of this application. Therefore, if such modifications and variations fall within the scope of the claims of this application and their equivalents, this application also intends to include such modifications and variations.

Claims

1. A method for calculating the load distribution of a tunneling machine main bearing, characterized in that, Includes the following: Obtain the profile modification method and modification function of the main bearing rollers; A series of loads were applied to the main push roller, the auxiliary push roller, and the radial roller respectively, and a series of elastic deformations between each roller and the raceway were calculated based on the non-Hertz contact theory and the shape modification function. The least squares method was used to fit the data of the binary variables composed of load and elastic deformation, and the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller were obtained respectively. Static equilibrium analysis of the main bearing is performed based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring. The load distribution of the main bearing is calculated based on the axial, radial, and angular displacements of the inner ring of the bearing. The process of calculating a series of elastic deformations between each roller and raceway based on non-Hertz contact theory and shape modification function is as follows: The radial surface function of the roller is obtained by converting the roller's shape modification function; The surface function of the roller's contact area is obtained by combining the roller's shape modification function and radial surface function; whereby the roller's radial surface function is expressed as: Thus, in determining the shape modification function of the roller The radial surface function of the roller can then be calculated, and the surface function of the roller contact area can be expressed as: , D we Indicates the nominal diameter of the roller; The elastic deformation between the roller and the raceway is calculated based on the surface function of the contact area of ​​the roller and the non-Hertz line contact equation. The process of using the least squares method to fit data to the binary variables composed of load and elastic deformation, and to obtain the fitted contact stiffness and fitted load deformation index of the main pushing roller, auxiliary pushing roller, and radial roller respectively, is as follows: Based on the Palmgren formula, a fitting relationship is constructed, which is as follows: ,in, The value represents the load borne by the roller, K represents the fitted contact stiffness, δ represents the elastic deformation between the roller and the raceway, and n represents the fitted load deformation index. After converting the above fitting relationship into a logarithmic function, we obtain the fitting function as follows: , , , ; Based on a series of load data, a series of elastic deformations, and a fitting function, the least squares method was used to fit the fitting function, and the fitted contact stiffness and fitted load deformation index of the main push roller, the auxiliary push roller, and the radial roller were obtained respectively.

2. The method for calculating the load distribution of the main bearing of a tunneling machine as described in claim 1, characterized in that, The expression for the non-Hertz line contact equation is: ； Where P(x,y) represents the contact stress distribution, F represents the load borne by the roller, z0(x,y) represents the initial distance between the roller contact surface and the raceway contact surface, δ represents the elastic convergence between the roller and the raceway when elastic deformation occurs, and S represents the contact area under the load. This represents the coordinates of two points in the contact area. Indicates comprehensive material parameters, v1 and v2 represent the Poisson's ratios of the roller material and the raceway material, respectively, and E1 and E2 represent the elastic moduli of the roller material and the raceway material, respectively.

3. The method for calculating the load distribution of the main bearing of a tunneling machine as described in claim 1, characterized in that, During the static equilibrium analysis of the main bearing, the axial static equilibrium equation is constructed as follows: , of which F a M represents the axial load. k The value represents the overturning moment, K1 and K2 represent the fitted contact stiffness of the main push roller and the auxiliary push roller, respectively, and n1 and n2 represent the fitted load deformation exponents of the main push roller and the auxiliary push roller, respectively. This represents the elastic deformation of the i-th main thrust roller. This represents the elastic deformation of the i-th auxiliary push roller. This represents the distribution angle of the i-th main pusher roller. This represents the distribution angle of the i-th auxiliary pusher roller. Z1 represents the number of main push rollers. Z2 represents the number of auxiliary push rollers, D pw1 and D pw2 These represent the distribution circle diameters of the main push roller and the auxiliary push roller, respectively. , , This indicates the angular displacement of the bearing's inner ring. This indicates the axial displacement of the bearing's inner ring. Indicates axial clearance; The axial displacement of the bearing inner ring is obtained by using the Newton-Raphson algorithm. and angular displacement .

4. The method for calculating the load distribution of the main bearing of a tunneling machine as described in claim 3, characterized in that, During the static equilibrium analysis of the main bearing, the radial static equilibrium equation is constructed as follows: , of which F r K3 represents the radial load, K3 represents the fitted contact stiffness of the radial rollers, and Z3 represents the number of radial rollers. This represents the distribution angle of the i-th radial roller. , This represents the elastic deformation of the i-th radial roller. , P represents the radial displacement of the bearing inner ring. r Indicates radial clearance; The radial displacement of the bearing inner ring is obtained by using the Newton-Raphson algorithm. .

5. The method for calculating the load distribution of the main bearing of a tunneling machine as described in claim 4, characterized in that, The load distribution of the main bearing is as follows: The contact load of the i-th main pusher roller is: ; The contact load of the i-th auxiliary push roller is: ; The contact load of the i-th radial roller is: .

6. A load distribution calculation system for a tunneling machine main bearing, employing the load distribution calculation method for a tunneling machine main bearing as described in any one of claims 1 to 5, characterized in that, include: The data acquisition module is used to acquire the modification method and modification function of the main bearing rollers; The contact analysis module is used to apply a series of loads to the main push roller, auxiliary push roller and radial roller respectively, and calculate a series of elastic deformations between each roller and the raceway based on non-Hertz contact theory and shape modification function. The data fitting module is used to fit the binary variables composed of load and elastic deformation using the least squares method, and to obtain the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller and radial roller respectively. The balance analysis module is used to perform static balance analysis of the main bearing based on the fitted contact stiffness and fitted load deformation index of the main push roller, auxiliary push roller, and radial roller, and to obtain the axial displacement, radial displacement, and angular displacement of the bearing inner ring. The load analysis module is used to calculate the load distribution of the main bearing based on the axial, radial, and angular displacements of the bearing inner ring.

7. An electronic device, characterized in that, The method includes a processor and a memory, wherein the memory stores a computer program, and the processor executes the steps of the method as described in any one of claims 1 to 5 by calling the computer program stored in the memory.

8. A computer-readable storage medium for storing a computer program for calculating the load distribution of a tunneling machine's main bearing, characterized in that, The computer program, when run on a computer, performs the steps of the method as described in any one of claims 1 to 5.

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