CN114492135B - Method for shaping bearing roller under different load conditions, bearing and mechanical equipment - Google Patents
Method for shaping bearing roller under different load conditions, bearing and mechanical equipmentInfo
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- CN114492135B CN114492135B CN202210109170.8A CN202210109170A CN114492135B CN 114492135 B CN114492135 B CN 114492135B CN 202210109170 A CN202210109170 A CN 202210109170A CN 114492135 B CN114492135 B CN 114492135B
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- G—PHYSICS
- G06—COMPUTING OR CALCULATING; COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
- G06F30/23—Design optimisation, verification or simulation using finite element methods [FEM] or finite difference methods [FDM]
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- G—PHYSICS
- G06—COMPUTING OR CALCULATING; COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/10—Geometric CAD
- G06F30/17—Mechanical parametric or variational design
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- G—PHYSICS
- G06—COMPUTING OR CALCULATING; COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
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- Mathematical Analysis (AREA)
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- Rolling Contact Bearings (AREA)
Abstract
本发明公开了一种不同载荷条件下轴承滚子的修形方法、轴承和机械设备，不同载荷条件下轴承滚子的修形方法，用于修正轴承中滚子的剖面轮廓曲线，修形方法包括：获取轴承的全部实际载荷条件和用于等效滚子的弹簧的非线性刚度系数；建立轴承的有限元模型，在有限元模型中利用多根弹簧等效滚子，并将非线性刚度系数加载于弹簧上；分别将全部实际载荷条件施加于有限元模型，并在同一坐标系下建立得到在全部实际载荷条件下多根弹簧的位置和对应弹簧的变形量的关系图；在关系图中，对位置和变形量之间的关系进行拟合，得到拟合曲线，作为滚子的剖面轮廓曲线。
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 comprises: 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; fitting the relationship between the positions and the deformation amounts in the relationship diagram to obtain a fitting curve as the cross-sectional profile curve of the roller.
Description
Technical Field
The invention relates to a bearing roller shaping method, in particular to a bearing roller shaping method under different load conditions, a bearing and mechanical equipment.
Background
The cylindrical roller bearing is a linear contact bearing with strong bearing capacity and good fatigue resistance, and is widely applied to various mechanical equipment.
In cylindrical roller bearings, the contact of the rollers with the raceways is of limited length, and after loading the bearing inevitably results in a large stress concentration, the "edge effect", at both ends of the rollers. Due to the existence of the edge effect, the cylindrical roller bearing is often subjected to fatigue failure near the end part of the roller, and the service life of the bearing is greatly influenced. Aiming at the bearing disadvantages and application limitations of the straight bus cylindrical roller, the roller shape modification technology is studied intensively by scholars and bearing manufacturers at home and abroad, and cylindrical, full convex arc, modified linear, logarithmic and other roller shape modification methods are provided and applied to engineering.
The existing roller shaping method is mainly a symmetrical shaping method, when the roller bears uniform load, the shaping method can effectively solve the problem of stress concentration at the edge of the roller, but in actual work, the bearing operates under the unbalanced load effect and bears various load conditions, and at the moment, the adaptability of the traditional roller shaping method to the actual working condition of the bearing is greatly reduced.
Disclosure of Invention
In order to meet the needs of the prior art, the invention provides a method for repairing a bearing roller under different load conditions, a bearing and mechanical equipment.
The method for modifying the profile curve of the roller in the bearing is used for modifying the profile curve of the roller in the bearing under different load conditions, and comprises the following steps:
Acquiring all actual load conditions of the bearing and nonlinear stiffness coefficients of springs for equivalent rollers;
establishing a finite element model of the bearing, utilizing a plurality of spring equivalent rollers in the finite element model, and loading a nonlinear stiffness coefficient on the spring;
Respectively applying all actual load conditions to the finite element model, and establishing a relation diagram of the positions of a plurality of springs and the deformation of corresponding springs under all actual load conditions under the same coordinate system;
in the relation graph, the relation between the position and the deformation is fitted to obtain a fitting curve as a profile curve of the roller.
Alternatively, acquiring all actual load conditions of the bearing includes:
at least two actual load conditions of the bearing are determined, the at least two actual load conditions being such that the most loaded roller is the same roller.
Alternatively, the relation diagram is specifically a relation diagram of the positions of the plurality of springs equivalent to the roller with the largest load and the deformation amount of the springs.
Optionally, the abscissa of the relation chart is specifically the positions of the plurality of springs equivalent to the roller with the largest load, and the ordinate of the relation chart is specifically the deformation of the corresponding springs.
Optionally, using a plurality of spring equivalent rollers in the finite element model, comprising:
In the finite element model, 15 springs are used to equivalent the most loaded roller, and 4 springs are used to equivalent the other rollers.
Optionally, obtaining a nonlinear stiffness coefficient of the spring for the equivalent roller includes:
placing the roller between two platens so that the roller can roll relative to the two platens;
applying forces with different magnitudes to one of the pressing plates, wherein the direction of the forces faces the roller;
Acquiring deformation of the roller under acting forces of different magnitudes to obtain a relation curve of the deformation and the acting force;
And obtaining the nonlinear rigidity coefficient according to the relation curve.
Alternatively, the process may be carried out in a single-stage,
Placing the roller between two platens so that the roller can roll relative to the two platens, comprising:
The two pressing plates are distributed at intervals along the vertical direction, and the rollers are horizontally arranged between the two pressing plates, so that the rollers can roll relative to the two pressing plates, and the two pressing plates are along the vertical direction;
Applying forces of different magnitudes to one of the platens, the direction of the forces being toward the rollers, comprising:
different amounts of force are applied to the overlying platen in a direction vertically downward and toward the rollers.
The application also provides a bearing comprising the roller, wherein the profile curve of the roller is specifically the profile curve obtained by the method for shaping the bearing roller under different load conditions.
The application also provides mechanical equipment, which comprises a bearing, and the bearing is specifically the bearing.
Optionally, the mechanical device is in particular a heading machine, and the bearing is in particular a main bearing of the heading machine.
Compared with the background art, the method for repairing the bearing roller under different load conditions provided by the application is based on finite element analysis technology, the problem of repairing the bearing roller is skillfully converted into the problem of analyzing the deformation of the nonlinear spring by carrying out nonlinear spring equivalent treatment on the roller, meanwhile, the deformation of the nonlinear spring of the equivalent roller is obtained by analyzing the bearing under the complex load condition of the actual working condition, and the optimal roller repairing curve adapting to the load condition of the actual working condition is obtained by fitting the binary relation between the position of the linear spring and the deformation under different load conditions. Compared with the traditional qualitative roller shaping method, the method has the advantages that the actual load condition is used as an input condition, the personalized roller shaping curve adapting to the complex load condition is positively acquired, the adaptability of the roller to the actual working condition load is greatly enhanced, the problem of stress concentration of the roller under the actual working condition is solved, the service life of the bearing is further prolonged, in addition, the nonlinear spring equivalent processing is carried out on the roller in the bearing, the differential design is carried out, the number of finite element model grids is greatly reduced on the premise of guaranteeing the analysis precision, and the finite element analysis difficulty is greatly reduced.
The bearing and the mechanical equipment provided by the application have the beneficial effects and are not unfolded any more.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions in the prior art, the drawings that are required to be used in the embodiments or the description of the prior art will be briefly described below, and it is obvious that the drawings in the following description are only embodiments of the present invention, and that other drawings can be obtained according to the provided drawings without inventive effort for a person skilled in the art.
FIG. 1 is a flow chart of a method of modifying a bearing roller under different load conditions provided by an embodiment of the present invention;
FIG. 2 is a schematic illustration of an experimental procedure for obtaining a nonlinear stiffness coefficient of a spring for an equivalent roller provided by an embodiment of the present invention;
FIG. 3 is a schematic diagram of a bearing analysis model according to an embodiment of the present invention;
fig. 4 is a schematic diagram of a fitted curve obtained after fitting the relationship between the position and the deformation provided in the embodiment of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
The present invention will be further described in detail below with reference to the drawings and detailed description for the purpose of enabling those skilled in the art to better understand the aspects of the present invention.
The application provides a method for modifying a bearing roller under different load conditions, which is used for modifying a profile curve of the roller in the bearing, as shown in figure 1 of the specification, and comprises the following steps:
s1, acquiring all actual load conditions of a bearing and nonlinear stiffness coefficients of springs for equivalent rollers;
S2, establishing a finite element model of the bearing, utilizing a plurality of spring equivalent rollers in the finite element model, and loading a nonlinear stiffness coefficient on the spring;
s3, respectively applying all actual load conditions to the finite element model, and establishing a relation diagram of the positions of the plurality of springs and the deformation of the corresponding springs under all actual load conditions under the same coordinate system;
And S4, fitting the relation between the position and the deformation in the relation graph to obtain a fitting curve serving as a profile curve of the roller.
The step of acquiring all actual load conditions of the bearing in step S1 includes:
at least two actual load conditions of the bearing are determined, the at least two actual load conditions being such that the most loaded roller is the same roller.
In step S2, a finite element analysis model of the bearing is established, and the rollers in the finite element analysis model are subjected to equivalent treatment by adopting nonlinear springs. Before the roller is subjected to nonlinear spring equivalent, the application modes of different load conditions are firstly determined, so that the maximum loaded roller under different load conditions is the same. And then determining the number of springs for equivalent single rolling bodies, wherein more springs are used for equivalent loaded maximum rollers according to the roller size and actual requirements, and the number of springs for equivalent loaded maximum rollers is suggested to be more than or equal to 10 in order to ensure the accuracy of the final shaping curve.
The relationship diagram obtained in step S3 may be a relationship diagram of the positions of the plurality of springs equivalent to the roller having the largest load and the deformation amount thereof.
In addition, the abscissa of the relation chart is the positions of the plurality of springs equivalent to the roller with the largest load, and the ordinate of the relation chart is the deformation of the corresponding springs.
In step S3, a finite element calculation result is obtained, the spring deformation of the equivalent loaded maximum roller under each load condition is analyzed, the relation between the spring position and the spring deformation under each load condition is established under the same coordinate system, and finally, the relation between the spring position and the spring deformation is fitted to obtain a best fit curve, wherein the curve is the solved best roller modification curve adapting to the load condition of the actual working condition.
The application aims at the roller self-adaptive shape modification method of the bearing under the actual load condition, realizes the roller bus forward shape modification design adapting to different load conditions, further solves the problem of local stress concentration of the bearing roller, and prolongs the service life of the bearing.
In a specific embodiment, for step S1, in order to obtain the nonlinear stiffness coefficient of the spring for the equivalent roller, it can be known by experiment or finite element analysis, and for the experimental mode, the following is specifically adopted:
placing the roller between two platens so that the roller can roll relative to the two platens;
applying forces with different magnitudes to one of the pressing plates, wherein the direction of the forces faces the roller;
Acquiring deformation of the roller under acting forces of different magnitudes to obtain a relation curve of the deformation and the acting force;
And obtaining the nonlinear rigidity coefficient according to the relation curve.
In order to improve the reliability of the experimental result, referring to fig. 2 of the specification, two pressing plates are spaced apart in the vertical direction, and the rollers are horizontally placed between the two pressing plates.
Specifically, the first pressing plate 6 and the second pressing plate 7 are distributed at intervals in the vertical direction, the first pressing plate 6 is above, the second pressing plate 7 is below, the experimental roller 5 is placed between the first pressing plate 6 and the second pressing 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 rollers in actual bearings, and the experimental roller 5 can roll relative to the two pressing plates.
In this embodiment, the bearing mainly bears three different load conditions, denoted as P 1、P2 and P 3, respectively, and then acquires the nonlinear stiffness coefficients of springs for the three equivalent rollers, wherein the nonlinear stiffness coefficients are obtained through an experimental method, a schematic diagram of the experimental process is shown in fig. 2, a series of acting forces F 1、F2…,Fm are applied to the three rollers through an experimental device, deformation delta 1、δ2…,δn of the rollers under the corresponding acting forces is measured, and then a nonlinear stiffness coefficient curve of the springs for the three equivalent rollers, namely a relation curve of the deformation and the acting force, is obtained.
And then, establishing a finite element model of the bearing, and determining the application modes of the three load conditions so that the roller with the largest load is the same roller under different load conditions. And then carrying out nonlinear spring equivalent treatment on all the rollers in the bearing, wherein 15 nonlinear springs are adopted for equivalent of the roller with the largest load, 4 nonlinear springs are adopted for equivalent of other rollers, and the established bearing analysis model schematic diagram is shown in figure 3. As can be seen from fig. 3 of the description, the rollers have been replaced by springs for the bearing analysis model, wherein the bearing comprises a first outer ring 1, a second outer ring 2 and an inner ring 3, the most loaded roller 4 being equivalent by 15 springs, while the rollers at other positions are equivalent by 4 springs.
And finally, applying three load conditions to the established main bearing finite element analysis model one by one, and carrying out simulation calculation. Based on finite element calculation results, 15 spring deformation delta 1、△2…,△15 of the equivalent loaded maximum roller under three load conditions are analyzed, and the relation between 15 spring positions and the spring deformation under 3 load conditions is established under the same coordinate system and is shown in figure 4. The position of the roller bus is between 5mm and 75mm on the abscissa, then the relationship between 15 spring positions and spring deformation under three load conditions is fitted, the best fitting curve adapting to the three load conditions is obtained, the curve is the solved best roller shaping curve adapting to the actual working condition load conditions, and the finally obtained roller shaping curve is shown in figure 4.
It should be noted that the nonlinear spring rate set forth in the above embodiments may be obtained by establishing a finite element roller contact model, in addition to the experimental acquisition method. In addition, the method for modifying the shape of the bearing roller under different load conditions can modify the profile curve of the cylindrical roller, and the method can also be adopted for modifying the shape of the tapered roller, so that the problem of modifying the shape of the tapered roller is converted into the problem of analyzing the deformation of the nonlinear spring by analyzing the bearing with the nonlinear spring equivalent tapered roller.
The bearing provided by the application comprises the roller, wherein the profile curve of the roller is particularly a profile curve obtained by a shape modification method of the bearing roller under different load conditions, so that the problem of local stress concentration of the bearing roller can be solved, and the service life of the bearing is prolonged.
The application provides a mechanical device with a bearing, which comprises the bearing in the specific embodiment, and other parts of the mechanical device can refer to the prior art and are not developed herein, wherein the mechanical device can be a development machine and the like, and the bearing can be a main bearing of the development machine.
It should be noted that in this specification relational terms such as first and second are used solely to distinguish one entity from another entity without necessarily requiring or implying any actual such relationship or order between such entities.
The method for shaping the bearing roller, the bearing and the mechanical equipment under different load conditions are described in detail. The principles and embodiments of the present invention have been described herein with reference to specific examples, the description of which is intended only to facilitate an understanding of the method of the present invention and its core ideas. It should be noted that it will be apparent to those skilled in the art that various modifications and adaptations of the invention can be made without departing from the principles of the invention and these modifications and adaptations are intended to be within the scope of the invention as defined in the following claims.
Claims (9)
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210109170.8A CN114492135B (en) | 2022-01-28 | 2022-01-28 | Method for shaping bearing roller under different load conditions, bearing and mechanical equipment |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202210109170.8A CN114492135B (en) | 2022-01-28 | 2022-01-28 | Method for shaping bearing roller under different load conditions, bearing and mechanical equipment |
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| CN114492135B true CN114492135B (en) | 2025-09-19 |
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104636596A (en) * | 2014-12-26 | 2015-05-20 | 中国北方车辆研究所 | Cylindrical roller bearing asymmetric shape correction method under specific loads |
| CN113283036A (en) * | 2021-06-21 | 2021-08-20 | 中国船舶重工集团海装风电股份有限公司 | Finite element modeling method for self-aligning roller bearing |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20150004851A (en) * | 2012-04-24 | 2015-01-13 | 아크티에볼라게트 에스케이에프 | Module for determining an operating characteristic of a bearing |
| US9845825B2 (en) * | 2014-04-08 | 2017-12-19 | Nrb Bearings Ltd. | Roller bearing with enhanced stress bearing capacity |
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- 2022-01-28 CN CN202210109170.8A patent/CN114492135B/en active Active
Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104636596A (en) * | 2014-12-26 | 2015-05-20 | 中国北方车辆研究所 | Cylindrical roller bearing asymmetric shape correction method under specific loads |
| CN113283036A (en) * | 2021-06-21 | 2021-08-20 | 中国船舶重工集团海装风电股份有限公司 | Finite element modeling method for self-aligning roller bearing |
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