JP2016051370A - Analysis method and analysis system for roller bearings - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide an analysis method and an analysis system for a roller bearing that, in a roller bearing, enable bearing analysis capable of reducing influence of movement in an axial direction and analysis of characteristics of contact load, lifetime, and the like.SOLUTION: An analysis method for a roller bearing includes the steps of: generating a first finite element model of the roller bearing; with either of a rolling contact surface of a roller (1, 1a, or 1b) and a raceway surface of bearing rings (2 and 3) as a starting point in the generated first finite element model of the roller bearing, adding addition objects (5 and 6) which extend in a direction away from the opposing surfaces; and creating a second finite element model in which the other of the rolling contact surface of the roller (1, 1a, or 1b) and the raceway surface of the bearing rings (2 and 3) and a tip end of the addition objects (5 and 6) are connected by pseudo spring elements, and analyzing a contact load on the basis of a displacement of the pseudo spring elements (7 and 8) at the time of applying a load to the roller bearing.SELECTED DRAWING: Figure 8

Description

  The present invention relates to an analysis method and an analysis system for analyzing characteristics such as rigidity and life of a roller bearing.

  Japanese Patent No. 5445258 (Patent Document 1) discloses an analysis method of a rolling bearing model having rolling elements such as balls and cylindrical rollers in which rolling elements are provided between the inner ring and the outer ring so as to be able to roll in the circumferential direction. Has been. In this method, the finite element model creation unit divides the elements from the CAD data for the inner ring and the outer ring, replaces the rolling elements themselves with the same number of spring elements in the circumferential direction, and based on the radial clearance of the rolling bearing, Set the characteristic of displacement with respect to the load of the element and set the analysis model of the finite element. Then, the displacement, strain, and stress of the rolling bearing or the shaft or housing supported by the rolling bearing are obtained from the created analysis model. In the analysis system described in Patent Document 1, in the case of a ball bearing, the rolling element itself is replaced with one spring element, but in the case of a cylindrical roller bearing, the rolling element itself is replaced with a plurality of spring elements.

  In “Tribologist”, Vol. 48, No. 9 (2003) 765-772 (Non-patent Document 1), in order to calculate the natural frequency of the outer ring of the tapered roller bearing to which an axial load is applied, the roller and raceway surface are calculated. Assuming a vibration system due to elastic contact between the outer ring, the inertial moment system angular direction natural frequency and the outer ring mass system axial direction natural frequency are shown.

  Furthermore, “Mechanical Society of Japan Proceedings” Vol. 78, No. 790 (2012-6), 2278-2291 (Non-patent Document 2) includes rolling elements and inner / outer rings in the bearing, and contact elements of the outer ring and the housing. The use of spring elements in between is described.

  The actual bearing analysis requires a three-dimensional bearing analysis that considers not only radial and circumferential directions but also axial movement. However, although each document describes that the rolling element is replaced with a spring element or that a spring element is provided between the rolling element and the race, the bearing is considered in consideration of the axial movement of the roller bearing. It does not describe the analysis.

Japanese Patent No. 5445258

"Tribologist" Vol. 48, No. 9 (2003) 765-772 "Mechanical Society of Japan," Vol. 78, No. 790 (2012-6), 2278-2291

  SUMMARY OF THE INVENTION Accordingly, the present invention provides a roller bearing analysis method and an analysis system for a roller bearing capable of analyzing a bearing that can reduce the influence of the axial movement of the roller and analyzing characteristics such as surface pressure and life. With the goal.

  The present invention is an analysis method for analyzing a roller bearing including a roller and a bearing ring, the step of generating a finite element model of the roller bearing, a roller of the generated finite element model of the roller bearing, Using the step of generating a finite element model with a spring element added between the opposite race and the finite element model of a roller bearing with a spring element, the displacement of the spring element can be detected when a load is applied to the roller bearing. And a step of adding a spring element, starting from one of the rolling surface of the roller and the raceway surface of the raceway, extends in a direction away from the facing surface. Adding an appendage, and adding a pseudo-spring element that connects either the rolling surface of the roller or the raceway surface of the raceway to the tip of the appendage.

  In the present invention, since the change in the length of the pseudo spring element can be reduced even if the roller moves in the axial direction, the influence on the analysis of the contact load due to the movement of the roller in the axial direction can be reduced.

  Preferably, the roller bearing is a radial roller bearing, and the pseudo spring element extends in a radial direction of the roller. By providing the pseudo spring element so as to extend in the radial direction, even if the roller moves in the axial direction, the inclination of the pseudo spring element can be reduced, and the influence thereof can be reduced. More preferably, by making the pseudo spring element longer than the diameter of the roller, the influence when the roller moves in the axial direction can be further reduced.

  Preferably, one end of the appendage is provided on the rolling surface of the roller, and the pseudo spring element is provided between the other end of the appendage and the raceway surface of the raceway, or one end of the appendage is provided on the raceway. The pseudo spring element is provided between the other end of the appendage and the rolling surface of the rolling element.

  Preferably, the roller bearing is a spherical roller bearing including a spherical roller, and the tip portion of the additional member extends in the radial direction of the spherical roller and is positioned on the center of curvature of the raceway surface of the raceway ring. By providing the appendage in this way, the inclination of the pseudo spring element can be reduced even if the spherical roller moves in the axial direction, so that the influence on the movement in the axial direction can be reduced.

  Another aspect of the present invention is an analysis system for analyzing a roller bearing including a roller and a bearing ring, and inputs various data including dimensions relating to each part of the roller and the bearing ring, and clearances between the parts. A first finite element model of the roller bearing including the roller based on the input means and various data input by the input means, and the roller rolling surface in the generated first finite element model And an appendage extending in a direction away from the facing surface starting from one of the raceways of the raceway and the raceway of the roller ring, and the other of the raceway surface of the roller and the raceway A finite element model creating means for creating a second finite element model of the roller bearing to which a pseudo spring element for connecting the tip of the appendage is added, and a finite element model creating means. To under a load for the second finite element model of receiving comprises analyzing means for analyzing the contact load on the basis of the displacement of the pseudo-spring element.

  With this analysis system, since the change in the length of the pseudo spring element can be reduced even when the roller moves in the axial direction, the influence on the analysis of the contact load due to the movement of the roller in the axial direction can be reduced.

  According to the present invention, bearing analysis can be performed while reducing the influence of axial movement, and characteristics such as surface pressure and life can be analyzed.

It is a conceptual diagram for demonstrating the influence when an axial direction load is added to a cylindrical roller bearing. In order to explain the analysis method of the cylindrical roller bearing of one embodiment of the present invention, it is a diagram showing an addition and a pseudo spring element added to the cylindrical roller bearing. It is the figure which abbreviate | omitted the pseudo spring element and showed the cylindrical roller and the additional thing in order to demonstrate the analysis method of the cylindrical roller bearing of one Embodiment of this invention. It is a conceptual diagram for demonstrating the analysis method of the cylindrical roller bearing of other embodiment of this invention. It is a conceptual diagram which shows the cylindrical roller bearing of further another embodiment of this invention. It is a conceptual diagram which shows the spherical roller bearing of other embodiment of this invention. It is a block diagram of the cylindrical roller bearing analysis system of one embodiment of this invention. It is a flowchart for demonstrating operation | movement of the cylindrical roller bearing analysis system of one Embodiment of this invention.

  Embodiments of the present invention will be described below with reference to the drawings.

  FIG. 1 is a conceptual diagram for explaining the influence when a cylindrical roller slides in the axial direction. 1A, a cylindrical roller bearing is analyzed by replacing the elastic contact stiffness between the raceway surfaces of the cylindrical roller 1 and the inner ring 2 and the outer ring 3 with a spring element 4 as described in Patent Document 1. The inner ring 2 and the outer ring 3 are track rings. A clearance C1 exists between the cylindrical roller 1 and the raceway surface of the inner ring 2 or the outer ring 3, and the length from the raceway surface of the inner ring 2 or the outer ring 3 to the center of rotation of the cylindrical roller 1 is L1. When the bearing is analyzed, the gap C1 is almost 0 or a minute value, and it is only necessary to evaluate the pushing amount of the cylindrical roller 1 in the radial direction. Therefore, even if the gap C1 exists, no problem occurs.

  As shown in FIG. 1B, when the cylindrical roller 1 slides with a load applied in the direction indicated by the arrow A, the spring element 4 is inclined by θ1 with respect to the radial direction of the cylindrical roller 1, and the spring element 4 has a length. The length increases from L1 to L2. At this time, the gap between the inner ring 2 or outer ring 3 and the cylindrical roller 1 is C2 = C1 + (L2−L1), C2> C1, as shown in FIG. To be evaluated.

  2 and 3 are views showing an addition to the cylindrical roller bearing in order to explain a method for analyzing the cylindrical roller bearing as an example of the radial bearing according to the embodiment of the present invention.

  In one embodiment of the present invention, a pseudo spring element 7 added to a virtual appendage 5 is used instead of the spring element 4 shown in FIG. That is, a virtual additional material 5 extending from a rolling surface of the cylindrical roller 1 or a raceway surface of the raceway to a direction away from the facing surface is added to the rolling of the cylindrical roller 1. A pseudo spring element 7 is added to connect one of the surface and the raceway surface of the raceway and the tip of the appendage 5.

  As shown in FIG. 2A, the cylindrical roller 1 that operates as a rolling element is positioned with a gap C3 between the inner ring 2 that operates as a raceway and the raceway surface of the outer ring 3. The appendage 5 is provided by providing a plurality of sufficiently long pseudo spring elements 7 between one end of the appendage 5 and the raceway surface of the outer ring 3 so that the cylindrical roller 1 slides in the axial direction. This is to reduce the influence of the inclination of the.

  One end of the appendage 5 is provided on the raceway surface that is a contact surface of the outer ring 3 with the cylindrical roller 1 across the cylindrical roller 1, and the tip of the appendage 5 extends to the inner ring 2 side. One end of the pseudo spring element 7 is provided on the rolling surface of the cylindrical roller 1 on the outer ring 3 side, and the other end of the pseudo spring element 7 is provided at the tip of the appendage 5. The pseudo-spring element 7 is added in the radial direction with respect to the rolling surface of the cylindrical roller 1 and has a length L3. The reason why the pseudo spring element 7 is added in the radial direction is that the angle formed between the extending direction of the pseudo spring element 7 and the rolling surface of the cylindrical roller 1 is approximately 90 degrees.

  Here, the pseudo spring element 7 is a virtual element for analyzing the life of the cylindrical roller bearing and the like using a model represented by a finite element method. The amount of expansion / contraction with respect to the load of the pseudo spring element 7 is defined in advance or is obtained in advance by experiment or calculation. The pseudo spring element 7 may be equivalent to a spring element that can be calculated by giving Young's modulus and Poisson's ratio as a cross-sectional area and material property values. The finite element method is one of the methods for numerically obtaining an approximate solution of a differential equation that is difficult to solve analytically. The region in which the equation is defined is divided into subregions (elements), and each subregion Approximate equations with a relatively simple and common interpolation function.

  As shown in FIG. 2B, when the cylindrical roller 1 slides in the direction of the arrow A by the slide amount δ, the pseudo spring element 7 extends to satisfy L3 <L4. At this time, the gap C3 should be unchanged, but due to the extension of the pseudo spring element 7, the calculation results in C4 = C3 + (L4-L3) as shown in FIG. 2C, and the gap C4 becomes the gap C3. More than. Since L3 = L4 cos θ2, C4 = C3 + L4 (1−cos θ2). However, when L3 (≈L4) is sufficiently large, the angle between L4 and the raceway surface of the outer ring 3 is approximately 90 degrees and θ2≈0, so L4 (1−cos θ2) ≈0, that is, C4≈C3. It is considered that the influence of the inclination of the pseudo spring element 7 is reduced.

  Next, as a supplement, with reference to FIG. 3, it is shown that the difference ΔC = C4−C3 between C4 and C3 is sufficiently small with respect to the slide amount δ of the cylindrical roller 1, and that C4≈C3. To do.

ΔC = C4-C3 is from the three square theorem = √ (L3 ² + δ ² ) −L3
= L3 × (1+ (δ / L3) ² ) ^0.5 −L3
≒ L3 × (1 + 0.5 × (δ / L3) ² ) −L3
≒ 0.5 × L3 × (δ / L3) ²

That is, ΔC≈0.5 × (δ / L3) × δ
If δ = 0.1 mm and L3 = 10 mm,
ΔC≈0.05 × δ (= 0.005 × 0.1 = 0.0005)

  Therefore, if L3 is set to 100 times or more of the sliding amount of the cylindrical roller 1, the evaluation error of the change in the direction of the load and the gap can be made sufficiently small. Although it depends on the amount of slide, it is preferable to select L3> a cylindrical roller diameter as a guideline for L3.

  In the cylindrical roller bearing, the outer ring 3 is supported by a mounting hole of a housing (not shown), and a shaft (not shown) is fitted into a fitting hole (not shown) of the inner ring 2. Thereby, a shaft is rotatably supported with respect to a housing by a cylindrical roller bearing. When a load is applied to the cylindrical roller bearing through the shaft, the cylindrical roller 1 shares and supports the load inside the bearing. A load supported by the cylindrical roller 1 is referred to as a rolling element load, and the rolling element load is calculated in consideration of deformation due to contact between the cylindrical roller 1 and the raceway surfaces of the inner ring 2 and the outer ring 3.

  In this embodiment, the contact load based on the Hertzian contact model between the cylindrical roller 1 and the inner ring 2 and the outer ring 3 is analyzed using the displacement amount of the pseudo spring element 7 when a load is applied to the cylindrical roller 1 as a parameter. Thus, the balance relationship of the three-dimensional cylindrical roller 1 considering not only the radial direction and the circumferential direction but also the axial movement can be obtained.

  Here, the Hertz contact model is a technique for analyzing stress or pressure applied to elastic contact portions such as spherical surfaces and spherical surfaces, cylindrical surfaces and cylindrical surfaces, and arbitrary curved surfaces and curved surfaces (“Mechanical Engineering Handbook” Design Edition β4 Element and Tribology (2005) 145-147).

  4 and 5 are conceptual diagrams for explaining a method of analyzing a cylindrical roller bearing according to another embodiment of the present invention. In FIG. 2, for the sake of simplification of explanation, the appendage 5 and the pseudo spring element 7 are provided only on the inner ring 2 side. However, the embodiment shown in FIG. Are respectively provided on the inner ring 2 and outer ring 3 side of the cylindrical roller 1, and as shown in FIG. 4B, a pseudo spring element is provided between the rolling surface of the cylindrical roller 1 on the outer ring 3 side and the tip side of the appendage 5. 7 is arranged in the radial direction, and the pseudo spring element 8 is arranged in the radial direction between the rolling surface of the cylindrical roller 1 on the inner ring 2 side and the tip of the appendage 6.

  In the example shown in FIG. 5A, one end of the appendage 5 is disposed on the raceway surface of the inner ring 2 and one end of the appendage 6 is disposed on the raceway surface of the outer ring 3. Then, as shown in FIG. 5 (b), a pseudo spring element 7 is arranged in the radial direction between the tip of the appendage 5 and the rolling surface on the inner ring 2 side of the cylindrical roller 1, and the tip of the appendage 6. A pseudo spring element 8 is arranged in the radial direction between the portion and the rolling surface of the cylindrical roller 1 on the outer ring 3 side.

  Also in the embodiment shown in FIGS. 4 and 5, since the influence on the pseudo spring elements 7 and 8 due to the change in the axial direction can be reduced, the change in the direction of the load becomes minute, the rolling surface of the cylindrical roller 1, The evaluation error of the clearance between the raceway surfaces of the inner ring 2 and the outer ring 3 is also small. A tapered roller may be used instead of the cylindrical roller 1.

  FIG. 6 is a view showing an example in which an appendage is provided on a spherical roller of a spherical roller bearing (self-aligning bearing) according to another embodiment of the present invention. In FIG. 6, the spherical roller 1 a uses a convex curved surface generated when a circular arc having a certain radius is rotated around its central axis as a rolling surface. The inner ring raceway surface of the inner ring 2a and the outer ring raceway surface of the outer ring 3 have a spherical shape centered on the bearing center.

  The center of curvature of the raceway surface of the outer ring 3a is P1, and the center of curvature of the raceway surface of the inner ring 2a is P2. The centers of curvature P1 and P2 are on an extension line in the radial direction with respect to the rolling surface on the inner ring 2a side and the rolling surface on the outer ring 3a side of the spherical roller 1a. The tip of the appendage 5 is provided at the center of curvature P1, and the other end of the appendage 5 is provided on the rolling surface of the spherical roller 1a on the inner ring 2a side. The tip of the appendage 6 is provided at the center of curvature P2, and the other end of the appendage 6 is provided on the outer ring 3a side rolling surface of the spherical roller 1a.

  A plurality of pseudo spring elements 7 are provided between the center of curvature P1 of the appendage 5 and the raceway surface of the outer ring 3a, and a plurality of pseudo spring elements 8 are provided between the center of curvature P2 of the appendage 6 and the raceway surface of the inner ring 2a. Is added. Since the pseudo spring elements 7 and 8 are respectively provided in the radial direction, the angle formed by the extension direction of the pseudo spring elements 7 and 8 and the rolling surface of the spherical roller 1a can be approximately 90 degrees. In the same manner as described above, it is possible to mitigate the influence when an action is applied to the spherical roller 1a in the axial direction.

  FIG. 7 is a block diagram of a rolling bearing analysis system according to an embodiment of the present invention.

  In FIG. 7, the analysis device 30 includes an input unit 31 that operates as an input unit, a control unit 32, a memory 33, and an output unit 34. The input unit 31 is operated by an operator so that, for example, the cylindrical roller 1, the inner ring 2, the outer ring 3, the additions 5 and 6, and the pseudo spring elements 7 and 8 shown in FIG. Enter design data including clearance.

  The control unit 32 is configured by, for example, a CPU, and includes a finite element model generation unit 35 for a bearing, a finite element model generation unit 36 for a shaft and a housing, a finite element model coupling unit 37, an adduct generation unit 38, a pseudo A spring element generation unit 39 and an analysis unit 40 that operates as analysis means are included. The bearing finite element model generating unit 35, the shaft and housing finite element model generating unit 36, and the finite element model coupling unit 37 operate as a finite element model generating means.

  The bearing finite element model generation unit 35 is based on various design data input from the input unit 31, for example, a three-dimensional finite element of a cylindrical roller bearing including the cylindrical roller 1, the inner ring 2, and the outer ring 3. Generate a model. The shaft or housing finite element model generation unit 36 generates a three-dimensional finite element model of the shaft or housing to be fitted to the inner ring 2 based on various design data input from the input unit 31. The finite element model coupling unit 37 couples the generated finite element model of the cylindrical roller bearing and the three-dimensional finite element model of the shaft and the housing.

  The adduct generation unit 38 generates a finite element model of the additions 5 and 6 including virtual finite elements and rigid elements, and the pseudo spring element generation unit 39 generates the pseudo spring elements 7 and 8. The analysis unit 40 loads the cylindrical roller bearing using a finite element model obtained by adding the appendages 5 and 6 and the pseudo spring elements 7 and 8 to the finite element model of the cylindrical roller bearing fitted to the shaft or the housing. The displacement amount of the pseudo spring elements 7 and 8 under load is analyzed.

  The memory 33 temporarily stores various data input from the input unit 31 and outputs the data to the control unit 32, or a bearing finite element model generation unit 35, a shaft or housing finite element model generation unit 36, a finite element model coupling unit. 37, the output images of the addition product generation unit 38 and the pseudo spring element generation unit 39 are stored, and the data analyzed by the analysis unit 40 is stored. The output unit 34 includes, for example, a printer and a display.

  FIG. 8 is a flowchart for explaining the operation of the rolling bearing analysis system according to the embodiment of the present invention.

  In order to analyze the cylindrical roller bearing, the operator obtains data of the shaft and the housing, the cylindrical roller 1 constituting the cylindrical roller bearing, the inner ring 2, the outer ring 3, the appendage 5, and the pseudo spring elements 7 and 8. Input from the input unit 31. Various rolling bearing data may be input in advance from the input unit 31 and stored in the memory 33, and the operator may read out desired data when analysis is necessary.

  In step S <b> 1 shown in FIG. 8, the finite element model generation unit 36 for the shaft and housing of the control unit 32 generates a finite element model for the shaft and housing in which the cylindrical roller bearing is fitted. In step S2, the bearing finite element model generator 35 generates a finite element model of the cylindrical roller bearing. In step S3, the finite element model coupling unit 37 couples the finite element model of the shaft or housing and the finite element model of the cylindrical roller bearing to generate a finite element model.

  In step S4, the adduct generation unit 38 generates adducts 5 and 6 including finite elements and rigid elements, and generates a finite element model obtained by adding the adducts 5 and 6 to the finite element model of the cylindrical roller bearing. . In the example shown in FIG. 4A, one end of the appendage 5 is provided on the outer ring 3 side rolling surface of the cylindrical roller 1, and one end of the appendage 6 is provided on the inner ring 2 side rolling surface. In the example shown in FIG. 5A, one end of the appendage 5 is provided on the inner ring 2, and one end of the appendage 6 is provided on the outer ring 3. In the example shown in FIG. 6, one end of the appendage 5 is provided on the inner ring 2a side rolling surface of the spherical roller 1a, and one end of the appendage 6 is provided on the outer ring 3a side rolling surface.

  In step S <b> 5, the pseudo spring element generation unit 39 generates the pseudo spring elements 7 and 8, and adds the generated pseudo spring elements 7 and 8 to the model to which the appendages 5 and 6 are added. In the example shown in FIG. 4B, a pseudo spring element 7 is added between the tip of the appendage 5 and the raceway surface of the outer ring 3, and between the tip of the appendage 6 and the raceway surface of the inner ring 2. The pseudo spring element 8 is added to the above. In the example shown in FIG. 5B, a pseudo spring element 7 is added between the tip of the appendage 5 and the inner ring 2 side rolling surface of the cylindrical roller 1, and the tip of the appendage 6 and the cylinder A pseudo spring element 8 is added between the outer ring 3 side rolling surface of the roller 1. In the example shown in FIG. 6, a pseudo spring element 7 is added between the center of curvature P1 and the raceway surface of the outer ring 3a, and a pseudo spring element 8 is added between the center of curvature P2 and the raceway surface of the inner ring 2a. To do.

  In step S6, the analysis unit 40 determines the displacement amount, load, and finite element of the pseudo spring elements 7 and 8 when a load is applied to the shaft of each roller bearing to which the appendages 5 and 6 and the pseudo spring elements 7 and 8 are added. Analyze characteristic values such as model deformation and stress, bearing surface pressure and life.

  In the embodiment shown in FIG. 8, the finite element model of the roller bearing including the shaft and the housing generated in steps S1 to S3 is defined as a first finite element model, and in steps S4 and S5 A finite element model to which a pseudo spring element is added is defined as a second finite element model. In other words, the finite element model before adding the appendage and the pseudo spring element is referred to as a first finite element model, and the finite element model to which the appendage and the pseudo spring element are added is referred to as a second finite element model. .

  In this embodiment, when a load is applied to the cylindrical roller bearing, the pseudo spring elements 7 and 8 are extended and the gap C3 shown in FIG. 2B is increased like C4. However, L4 is selected to be sufficiently large. Therefore, θ2 is approximately 90 degrees, and the influence of the inclination of the pseudo spring elements 7 and 8 can be reduced. Therefore, based on the displacement amount and load of the spring element when the value of the load is changed, the total deformation amount of the cylindrical roller 1, the stress and deformation of the shaft shaft and the housing, and the bearing life can be calculated.

  Furthermore, data such as a mounting position, a bearing internal specification, and a clearance for prolonging the life of the cylindrical roller bearing may be obtained from the life analysis result. Furthermore, the contact surface pressure and life can be determined from a Hertz contact model based on the spring load. In addition, the oil film thickness can be obtained from the rotational speed and the transfer speed, or the PV value of the soot can be obtained. The PV value is expressed as the product of the surface pressure P and the sliding speed V, and is used to determine the allowable operating range of the bearing material.

  The present invention can be applied not only to radial bearings but also to thrust bearings.

  The present invention is used to analyze the characteristics of cylindrical roller bearings, tapered roller bearings, and spherical roller bearings.

DESCRIPTION OF SYMBOLS 1 Cylindrical roller, 1a Spherical roller, 2,2a Inner ring, 3,3a Outer ring, 5,6 Addition, 7,8 Pseudo spring element, 30 Analysis device, 31 Input part, 32 Control part, 33 Memory, 34 Output part, 35 bearing finite element model generating unit, 36 shaft or housing finite element model generating unit, 37 finite element model connecting unit, 38 adduct generating unit, 39 pseudo spring generating unit, 40 analyzing unit.

Claims (7)

An analysis method for analyzing a roller bearing including a roller and a bearing ring,
Generating an image of the roller bearing;
Adding a spring element between the roller in the image of the generated roller bearing and the bearing ring facing it;
Using a finite element model of the roller bearing to which the spring element is added, and analyzing the contact load based on the displacement of the spring element when a load is applied to the roller bearing,
Adding the spring element comprises:
Adding one of the rolling surface of the roller and the raceway surface of the raceway as an origin, and adding an additive consisting of a finite element or a rigid element extending in a direction away from the facing surface;
A method for analyzing a roller bearing, comprising: adding a pseudo spring element that connects one of the rolling surface of the roller and the raceway surface of the bearing ring and the tip of the appendage. The roller bearing is a radial roller bearing,
The roller bearing analysis method according to claim 1, wherein the pseudo spring element extends in a radial direction of the roller.   The roller bearing analysis method according to claim 1, wherein the pseudo spring element is longer than a diameter of the roller.   One end of the appendage is provided on a rolling surface of the roller, and the pseudo spring element is provided between the other end of the appendage and a raceway surface of the raceway. Analysis method for roller bearings as described in 1.   One end of the additional material is provided on a raceway surface of the raceway, and the pseudo spring element is provided between the other end of the additional material and a rolling surface of the rolling element. An analysis method for a roller bearing according to claim 1. The roller bearing is a spherical roller bearing including a spherical roller,
The roller bearing analysis method according to any one of claims 1 to 3, wherein a tip portion of the additional object extends in a radial direction of the spherical roller and is located on a center of curvature of a raceway surface of the raceway. An analysis system for analyzing a roller bearing including a roller and a bearing ring,
Input means for inputting various data including dimensions regarding the respective parts of the roller and the bearing ring, and clearances between the parts;
Based on various data input by the input means, a first finite element model of a roller bearing including the roller is generated, and the rolling surface of the roller and the raceway in the generated first finite element model From one of the raceway surfaces of the ring as a starting point, an appendage extending in a direction away from the opposing surface is added, and the other of the rolling surface of the roller and the raceway surface of the raceway, and A finite element model creating means for generating a second finite element model of the roller bearing to which a pseudo spring element for connecting the tip of the appendage is added;
An analysis system for a roller bearing, comprising analysis means for analyzing a contact load based on a displacement of the pseudo spring element when a load is applied to a second finite element model of the roller bearing created by the finite element model creation means.

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