Bearing roller modification method under different load conditions, bearing and mechanical equipment

Abstract

The present invention discloses a shaping method for a bearing roller under different load conditions, a bearing and mechanical equipment. The shaping method for a bearing roller under different load conditions is used to correct the cross-sectional profile curve of the roller in the bearing. The shaping method includes: obtaining all actual load conditions of the bearing and the nonlinear stiffness coefficient of the spring used for the equivalent roller; establishing a finite element model of the bearing, using multiple springs as equivalent rollers in the finite element model, and loading the nonlinear stiffness coefficient on the spring; applying all actual load conditions to the finite element model respectively, and establishing a relationship diagram between the positions of multiple springs and the deformation amounts of the corresponding springs under all actual load conditions in the same coordinate system; in the relationship diagram, fitting the relationship between the position and the deformation amount to obtain a fitting curve as the cross-sectional profile curve of the roller.

Description

Technical Field

[0001] The invention relates to a bearing roller shaping method, and in particular to a bearing roller shaping method under different load conditions, a bearing and mechanical equipment. Background Art

[0002] Cylindrical roller bearings are a type of linear contact bearing with strong load-bearing capacity and good fatigue resistance, and are widely used in various mechanical equipment.

[0003] In cylindrical roller bearings, the contact between the roller and the raceway is a finite-length line contact. When the bearing is loaded, a large stress concentration inevitably occurs at both ends of the roller, which is known as the "edge effect." Due to the existence of the "edge effect," cylindrical roller bearings often suffer fatigue failure near the roller ends, which greatly reduces the service life of the bearing. In response to the load-bearing disadvantages and application limitations of straight-line cylindrical rollers, domestic and foreign scholars and bearing manufacturers have conducted in-depth research on roller shaping technology, proposing roller shaping methods such as cylindrical, fully convex arc, modified linear, and logarithmic types, which have been applied in engineering.

[0004] The current roller shaping method is mainly a symmetrical shaping method. When the roller is subjected to a uniform load, this shaping method can effectively solve the problem of stress concentration at the roller edge. However, in actual work, bearings often operate under the effect of eccentric loads and are subjected to multiple load conditions at the same time. At this time, the adaptability of traditional roller shaping methods to the actual working conditions of bearings is greatly reduced. Summary of the Invention

[0005] To meet the needs of the prior art, the present invention provides a method for modifying the shape of a bearing roller under different load conditions, a bearing, and a mechanical device.

[0006] The shaping method of bearing rollers under different load conditions is used to modify the cross-sectional profile curve of the rollers in the bearing. The shaping method includes:

[0007] Obtain all actual load conditions of the bearing and the nonlinear stiffness coefficients of the springs used for the equivalent rollers;

[0008] Establish a finite element model of the bearing, use multiple spring-equivalent rollers in the finite element model, and load the nonlinear stiffness coefficient on the spring;

[0009] Apply all actual load conditions to the finite element model respectively, and establish a relationship diagram between the positions of multiple springs and the deformation of the corresponding springs under all actual load conditions in the same coordinate system;

[0010] In the relationship diagram, the relationship between the position and the deformation is fitted to obtain a fitting curve, which is used as the cross-sectional profile curve of the roller.

[0011] Optionally, obtain all actual load conditions of the bearing, including:

[0012] At least two actual load conditions of the bearing are determined, wherein the at least two actual load conditions are such that the roller with the greatest load is the same roller.

[0013] Optionally, the relationship diagram is specifically a relationship diagram of the positions of multiple springs equivalent to the roller with the largest load and their deformations.

[0014] Optionally, the horizontal coordinate of the relationship diagram is specifically the position of multiple springs equivalent to the roller with the largest load, and the vertical coordinate of the relationship diagram is specifically the deformation of the corresponding spring.

[0015] Optionally, multiple spring-equivalent rollers are used in the finite element model, including:

[0016] In the finite element model, 15 springs are used to represent the roller with the largest load, and 4 springs are used to represent the other rollers.

[0017] Optionally, obtaining a nonlinear stiffness coefficient of a spring for the equivalent roller includes:

[0018] placing the roller between the two platens so that the roller can roll relative to the two platens;

[0019] Apply different forces to one of the pressure plates, with the direction of the force toward the roller;

[0020] Obtain the deformation of the roller under different forces and obtain the relationship curve between the deformation and the force;

[0021] The nonlinear stiffness coefficient is obtained according to the relationship curve.

[0022] Optionally,

[0023] Placing the roller between the two platens so that the roller can roll relative to the two platens includes:

[0024] Distribute the two pressing plates at intervals in the vertical direction, and place the roller horizontally between the two pressing plates so that the roller can roll relative to the two pressing plates, and the two pressing plates are in the vertical direction;

[0025] Apply different forces to one of the pressure plates, directed toward the roller, including:

[0026] Apply different forces to the upper pressure plate, with the direction of the force being vertically downward and toward the roller.

[0027] The present application also provides a bearing including a roller, wherein the cross-sectional profile curve of the roller is specifically a cross-sectional profile curve obtained according to the above-mentioned method for modifying the bearing roller under different load conditions.

[0028] The present application also provides a mechanical device, including a bearing, which is specifically the bearing described above.

[0029] Optionally, the mechanical equipment is a tunnel boring machine, and the bearing is a main bearing of the tunnel boring machine.

[0030] Compared with the above background technology, the present application provides a method for modifying bearing rollers under different load conditions. Based on finite element analysis technology, the rollers are treated as equivalent to nonlinear springs, cleverly transforming the problem of modifying bearing rollers into an analysis problem of nonlinear spring deformation. At the same time, the bearings are analyzed under complex load conditions in actual working conditions to obtain the deformation of the nonlinear spring of the equivalent roller. By fitting the binary relationship between the position of the linear spring and the deformation under different load conditions, the optimal roller modification curve that adapts to the actual working load conditions is obtained. Compared with traditional qualitative roller modification methods, the present application uses actual load conditions as input conditions to positively obtain personalized roller modification curves that adapt to complex load conditions. This greatly enhances the roller's adaptability to actual working load conditions, solves the problem of stress concentration of the rollers under actual working conditions, and thus improves the service life of the bearing. In addition, the present application performs nonlinear spring equivalent treatment on the rollers in the bearing and performs differentiated design. While ensuring the accuracy of the analysis, the number of finite element model grids is greatly reduced, greatly reducing the difficulty of finite element analysis.

[0031] The bearings and mechanical equipment provided in this application have the above-mentioned beneficial effects, which will not be elaborated here. BRIEF DESCRIPTION OF THE DRAWINGS

[0032] In order to more clearly illustrate the embodiments of the present invention or the technical solutions in 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 merely embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on the provided drawings without paying any creative work.

[0033] Figure 1 A flow chart of a method for modifying bearing rollers under different load conditions provided by an embodiment of the present invention;

[0034] Figure 2 A schematic diagram of an experimental process for obtaining a nonlinear stiffness coefficient of a spring for an equivalent roller provided in an embodiment of the present invention;

[0035] Figure 3 A schematic diagram of a bearing analysis model provided by an embodiment of the present invention;

[0036] Figure 4 This is a schematic diagram of a fitting curve obtained by fitting the relationship between position and deformation provided by an embodiment of the present invention. DETAILED DESCRIPTION

[0037] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0038] In order to enable those skilled in the art to better understand the solutions of the present invention, the present invention is further described in detail below with reference to the accompanying drawings and specific implementation methods.

[0039] The present application provides a method for modifying the profile of a bearing roller under different load conditions, which is used to modify the profile curve of the roller in the bearing. Figure 1 As shown, the shaping method includes:

[0040] S1. Obtain all actual load conditions of the bearing and the nonlinear stiffness coefficient of the spring used for the equivalent roller;

[0041] S2. Establish a finite element model of the bearing, use multiple spring-equivalent rollers in the finite element model, and load nonlinear stiffness coefficients on the springs;

[0042] S3. Apply all actual load conditions to the finite element model respectively, and establish a relationship diagram between the positions of the plurality of springs and the deformations of the corresponding springs under all actual load conditions in the same coordinate system;

[0043] S4. In the relationship diagram, the relationship between the position and the deformation is fitted to obtain a fitting curve as the cross-sectional profile curve of the roller.

[0044] The step of obtaining all actual load conditions of the bearing in step S1 includes:

[0045] At least two actual load conditions of the bearing are determined, wherein the at least two actual load conditions are such that the roller with the greatest load is the same roller.

[0046] In step S2, a finite element analysis model of the bearing is established, and the rollers in the finite element analysis model are equivalently treated using nonlinear springs. Before applying nonlinear spring equivalents to the rollers, the application method for different load conditions is determined, ensuring that the most loaded roller is the same under different load conditions. The number of springs used to equivalent a single rolling element is then determined. Based on roller size and actual requirements, more springs are used to equivalent the most loaded roller. To ensure the accuracy of the final shaping curve, it is recommended that the number of springs used to equivalent the most loaded roller be 10 or more.

[0047] The relationship diagram established in step S3 may be a relationship diagram between the positions of multiple springs equivalent to the roller with the largest load and their deformations.

[0048] In addition, the horizontal coordinate of the relationship diagram specifically represents the positions of the multiple springs equivalent to the roller with the largest load, and the vertical coordinate of the relationship diagram specifically represents the deformation of the corresponding spring.

[0049] In step S3, the finite element calculation results are obtained, the deformation of each spring of the equivalent maximum loaded roller under each load condition is analyzed, and the relationship between the spring position and the spring deformation under each load condition is established in the same coordinate system; finally, the relationship between the spring position and the spring deformation is fitted to obtain the best fitting curve, which is the solved optimal roller modification curve that adapts to the actual working load conditions.

[0050] This application aims at an adaptive roller shaping method for bearings under actual load conditions, realizing a positive roller generatrix shaping design that adapts to different load conditions, thereby solving the problem of local stress concentration in bearing rollers and improving the service life of bearings.

[0051] In a specific embodiment, for step S1, in order to obtain the nonlinear stiffness coefficient of the spring for the equivalent roller, experiments or finite element analysis can be used to obtain the coefficient. The experimental method is as follows:

[0052] placing the roller between the two platens so that the roller can roll relative to the two platens;

[0053] Apply different forces to one of the pressure plates, with the direction of the force toward the roller;

[0054] Obtain the deformation of the roller under different forces and obtain the relationship curve between the deformation and the force;

[0055] The nonlinear stiffness coefficient is obtained according to the relationship curve.

[0056] To improve the reliability of the experimental results, refer to the Figure 2 As shown, the two pressing plates are spaced apart in the vertical direction, and the roller is placed horizontally between the two pressing plates.

[0057] Specifically, the first pressure plate 6 and the second pressure plate 7 are spaced apart in the vertical direction, with the first pressure plate 6 on the top and the second pressure plate 7 on the bottom. The experimental roller 5 is placed between the first pressure plate 6 and the second pressure plate 7, and the rotation axis of the experimental roller 5 is horizontal. Obviously, the characteristics of the experimental roller 5 should be similar to those of the roller in the actual bearing, and the experimental roller 5 can roll relative to the two pressure plates.

[0058] Apply forces F of different magnitudes to the upper surface of the first pressure plate 6, with the direction of the force F being vertically downward and toward the experimental roller 5. In this embodiment, the bearing is mainly subjected to three different load conditions, which are represented as P1, P2 and P3 respectively. Then, the nonlinear stiffness coefficients of the springs used to be equivalent to the three rollers are obtained. The nonlinear stiffness coefficients are obtained by experimental methods. The schematic diagram of the experimental process is shown in the attached figure. Figure 2 As shown in the figure, a series of forces F1, F2, F m , and the deformation of the roller under the corresponding force is measured. n , and then obtain the nonlinear stiffness coefficient curve of the spring used to equivalent the three types of rollers, that is, the relationship curve between the deformation and the force.

[0059] Afterwards, a finite element model of the bearing was established, and the application methods of the three load conditions mentioned above were determined, so that under different load conditions, the roller with the largest load was the same roller. Then, all rollers in the bearing were treated as equivalent rollers with nonlinear springs. Among them, the roller with the largest load was treated as equivalent with 15 nonlinear springs, and the other rollers were treated as equivalent with 4 nonlinear springs. The schematic diagram of the established bearing analysis model is shown in the attached figure. Figure 3 As shown in the instruction manual. Figure 3 It can be seen that for the bearing analysis model, the rollers have been replaced by springs. The bearing includes a first outer ring 1, a second outer ring 2, and an inner ring 3. The roller 4 with the largest load is equivalent to 15 springs, while the rollers in other positions are equivalent to 4 springs.

[0060] Finally, the three load conditions were applied to the established finite element analysis model of the main bearing, and simulation calculations were carried out. Based on the finite element calculation results, the deformation of the 15 springs of the equivalent maximum loaded roller under the three load conditions was analyzed, △1, △2..., △ 15 In the same coordinate system, the relationship between the position of 15 springs and the spring deformation under three load conditions is established as shown in the attached figure. Figure 4 As shown. Among them, the horizontal axis between 5-75mm is the location of the roller generatrix. Then, by fitting the relationship between the position of 15 springs and the spring deformation under three load conditions, the best fitting curve that adapts to the three load conditions is obtained. This curve is the optimal roller modification curve that adapts to the actual working load conditions. The final roller modification curve is shown in the attached figure. Figure 4 shown.

[0061] It should be noted that, in addition to the experimental method for obtaining the nonlinear spring stiffness coefficient proposed in the above embodiment, it can also be obtained by establishing a finite element roller contact model. Furthermore, the bearing roller shaping method described in this application under different load conditions can not only modify the cross-sectional profile curve of cylindrical rollers, but also can be used to modify the shaping problem of tapered rollers. By analyzing bearings with equivalent tapered rollers with nonlinear springs, the tapered roller shaping problem can be converted into an analysis of the nonlinear spring deformation.

[0062] A bearing provided in the present application includes a roller, and the cross-sectional profile curve of the roller is specifically a cross-sectional profile curve obtained according to the shaping method of the bearing roller under different load conditions recorded above, thereby solving the problem of local stress concentration in the bearing roller and improving the service life of the bearing.

[0063] The present application provides a mechanical device with a bearing, including the bearing described in the above-mentioned specific embodiment; other parts of the mechanical device can refer to the existing technology and will not be elaborated in this article. Among them, the mechanical device can be specifically a tunnel boring machine, etc., and the bearing can be specifically the main bearing of the tunnel boring machine.

[0064] It should be noted that, in this specification, relational terms such as first and second are merely used to distinguish one entity from other entities, but do not necessarily require or imply any actual relationship or order between these entities.

[0065] The above is a detailed introduction to the bearing roller shaping method, bearings, and mechanical equipment provided by the present invention under different load conditions. Specific examples are used herein to illustrate the principles and implementation methods of the present invention. The description of the above embodiments is only intended to help understand the method and core concept of the present invention. It should be pointed out that, for those skilled in the art, several improvements and modifications may be made to the present invention without departing from the principles of the present invention, and such improvements and modifications also fall within the scope of protection of the claims of the present invention.

Claims

1. A method for modifying the profile of a bearing roller under different load conditions, for modifying the cross-sectional profile curve of the roller in the bearing, characterized in that: The shaping method comprises: Obtaining all actual load conditions of the bearing and the nonlinear stiffness coefficient of the spring equivalent to the roller; Establishing a finite element model of the bearing, using a plurality of springs to be equivalent to the rollers in the finite element model, and loading the nonlinear stiffness coefficient on the springs; Applying all the actual load conditions to the finite element model respectively, and establishing a relationship diagram between the positions of the plurality of springs and the corresponding deformations of the springs under all the actual load conditions in the same coordinate system; In the relationship diagram, fitting the relationship between the position and the deformation amount is performed to obtain a fitting curve as a cross-sectional profile curve of the roller; Obtain all actual load conditions for the bearing, including: At least two actual load conditions of the bearing are determined, wherein the at least two actual load conditions can cause the roller with the largest load to be the same roller.

2. The method for modifying the bearing roller under different load conditions according to claim 1, characterized in that: The relationship diagram is specifically a relationship diagram of the positions of the plurality of springs equivalent to the roller bearing the largest load and the deformation amounts thereof.

3. The method for modifying the bearing roller under different load conditions according to claim 2, characterized in that: The horizontal coordinate of the relationship diagram is specifically the position of the multiple springs equivalent to the roller with the largest load, and the vertical coordinate of the relationship diagram is specifically the deformation of the corresponding spring.

4. The method for modifying the bearing roller under different load conditions according to claim 2, characterized in that: In the finite element model, a plurality of springs are used to be equivalent to the rollers, comprising: In the finite element model, 15 springs are used to represent the roller with the largest load, and 4 springs are used to represent the other rollers.

5. The method for modifying the bearing roller under different load conditions according to claim 1, characterized in that: Obtaining the nonlinear stiffness coefficient of the spring equivalent to the roller includes: placing the roller between two pressing plates so that the roller can roll relative to the two pressing plates; Applying forces of different magnitudes to one of the pressure plates, with the direction of the forces being toward the roller; Obtaining the deformation of the roller under the applied forces of different magnitudes, and obtaining a relationship curve between the deformation and the applied forces; The nonlinear stiffness coefficient is obtained according to the relationship curve.

6. The method for modifying the bearing roller under different load conditions according to claim 5, characterized in that: Placing the roller between two pressure plates so that the roller can roll relative to the two pressure plates comprises: Distribute two pressing plates at intervals in the vertical direction, and horizontally place the roller between the two pressing plates so that the roller can roll relative to the two pressing plates; Applying forces of different magnitudes to one of the pressure plates, wherein the forces are directed toward the roller, comprises: Applying forces of different magnitudes to the upper pressure plate, wherein the direction of the forces is vertically downward and toward the roller.

7. A bearing, characterized in that: The roller comprises a cross-sectional profile curve of the roller, wherein the cross-sectional profile curve is specifically a cross-sectional profile curve obtained by the method for modifying the bearing roller under different load conditions according to any one of claims 1 to 6.

8. A mechanical device, characterized in that: The invention comprises a bearing, wherein the bearing is specifically the bearing described in claim 7 above.

9. The mechanical device according to claim 8, characterized in that: The mechanical equipment is specifically a tunnel boring machine, and the bearing is specifically a main bearing of the tunnel boring machine.

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