CN117313446B - Rolling bearing raceway defect expansion fault diagnosis method and system - Google Patents
Rolling bearing raceway defect expansion fault diagnosis method and system Download PDFInfo
- Publication number
- CN117313446B CN117313446B CN202311030446.4A CN202311030446A CN117313446B CN 117313446 B CN117313446 B CN 117313446B CN 202311030446 A CN202311030446 A CN 202311030446A CN 117313446 B CN117313446 B CN 117313446B
- Authority
- CN
- China
- Prior art keywords
- rolling
- bearing
- fault
- raceway
- defect
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Active
Links
- 238000005096 rolling process Methods 0.000 title claims abstract description 272
- 230000007547 defect Effects 0.000 title claims abstract description 138
- 238000000034 method Methods 0.000 title claims abstract description 40
- 238000003745 diagnosis Methods 0.000 title claims abstract description 18
- 238000006073 displacement reaction Methods 0.000 claims abstract description 36
- 230000005284 excitation Effects 0.000 claims abstract description 27
- 230000006870 function Effects 0.000 claims description 40
- 230000014509 gene expression Effects 0.000 claims description 39
- 230000033001 locomotion Effects 0.000 claims description 14
- 230000008569 process Effects 0.000 claims description 6
- 238000004590 computer program Methods 0.000 claims description 5
- 238000003860 storage Methods 0.000 claims description 4
- NAWXUBYGYWOOIX-SFHVURJKSA-N (2s)-2-[[4-[2-(2,4-diaminoquinazolin-6-yl)ethyl]benzoyl]amino]-4-methylidenepentanedioic acid Chemical compound C1=CC2=NC(N)=NC(N)=C2C=C1CCC1=CC=C(C(=O)N[C@@H](CC(=C)C(O)=O)C(O)=O)C=C1 NAWXUBYGYWOOIX-SFHVURJKSA-N 0.000 claims description 3
- 238000012512 characterization method Methods 0.000 description 9
- 230000002950 deficient Effects 0.000 description 9
- 238000010586 diagram Methods 0.000 description 8
- 239000011159 matrix material Substances 0.000 description 7
- 238000013016 damping Methods 0.000 description 6
- 238000004088 simulation Methods 0.000 description 6
- 230000000694 effects Effects 0.000 description 5
- 230000008878 coupling Effects 0.000 description 4
- 238000010168 coupling process Methods 0.000 description 4
- 238000005859 coupling reaction Methods 0.000 description 4
- 230000001133 acceleration Effects 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 3
- 230000005484 gravity Effects 0.000 description 3
- 238000001228 spectrum Methods 0.000 description 3
- 239000000463 material Substances 0.000 description 2
- 230000004044 response Effects 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000005094 computer simulation Methods 0.000 description 1
- 238000009826 distribution Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000005461 lubrication Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 230000000737 periodic effect Effects 0.000 description 1
Classifications
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR 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]
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F17/00—Digital computing or data processing equipment or methods, specially adapted for specific functions
- G06F17/10—Complex mathematical operations
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR 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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- General Physics & Mathematics (AREA)
- General Engineering & Computer Science (AREA)
- Data Mining & Analysis (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- Mathematical Physics (AREA)
- Algebra (AREA)
- Mathematical Analysis (AREA)
- Mathematical Optimization (AREA)
- Computational Mathematics (AREA)
- Pure & Applied Mathematics (AREA)
- Databases & Information Systems (AREA)
- Software Systems (AREA)
- Rolling Contact Bearings (AREA)
Abstract
The invention discloses a fault diagnosis method and a fault diagnosis system for the defect expansion of a rolling bearing raceway, wherein the method comprises the following steps: judging the severity of faults according to the size of the raceway defects, wherein the severity comprises slight faults, moderate faults and serious faults; determining a fault morphology function and a rolling body displacement excitation function according to the fault severity; based on the rolling body displacement excitation function, obtaining the Hertz contact stiffness coefficient of the rolling bearing; based on the Hertz contact stiffness coefficient of the rolling bearing, calculating the contact force and friction force between the rolling body and the rollaway nest to obtain the contact deformation between the rolling body and the rollaway nest; and determining the nonlinear restoring force of the rolling bearing containing the expansion fault of the raceway defect based on the contact force and the friction force between the rolling body and the raceway. The invention simulates the situation of the rolling path defect expansion fault more in line with the actual rolling path defect expansion fault based on the defect area parameter of the rolling path defect expansion fault and the actual structural parameter of the rolling bearing, and evaluates the damage degree of the rolling bearing under the actual running condition of the rolling bearing.
Description
Technical Field
The invention relates to the technical field of rolling bearing fault diagnosis, in particular to a rolling bearing raceway defect expansion fault diagnosis method and system.
Background
When the running temperature of the rolling bearing is increased or the inner ring and the outer ring of the bearing are severely inclined, larger negative working play is generated in the radial direction of the bearing, so that the extrusion stress between the rolling bodies and the roller path is increased, and the uneven degree of the load distribution of the whole circumference of the bearing is aggravated. In the process of circularly extruding and rolling the rolling body on the roller path, because the stress concentration part of the roller path or the rolling body exists on the secondary surface, when the maximum Hertz contact stress reaches a certain threshold value, fatigue defects occur on the secondary surface due to microscopic tearing of materials. Along with the continuous running of the bearing, the stress of the defect edge is larger, and under the reciprocating impact between the rolling body and the rollaway nest, the partial defect edge material is continuously lost to cause the defect profile to gradually expand or extend, so that the expansion defect of the bearing is formed, and the service life of the bearing is reduced.
In order to predict the vibration signal of the defective bearing, a defect fault characterization model needs to be established first. In the conventional bearing defect characterization model, the defect shape of the bearing is generally assumed to be a simpler geometric model, such as a rectangle, a circle, a triangle, a trapezoid, or simulated by adopting a piecewise trigonometric function and the like. However, the characterization model is greatly different from the actual defect fault morphology. In addition, little attention has been paid to expanding the profile morphology and characterization model of defects. The establishment of the bearing defect characterization method as true as possible is the basis for obtaining more accurate dynamic simulation signals.
Disclosure of Invention
The invention aims to provide a method and a system for diagnosing a rolling bearing raceway defect expansion fault, which simulate the situation of the rolling bearing raceway defect expansion fault more in line with reality based on a defect area parameter of the raceway defect expansion fault and an actual structural parameter of the rolling bearing, and evaluate the damage degree of the rolling bearing under the actual running condition of the rolling bearing.
In order to achieve the above object, the present invention provides the following solutions:
A method for diagnosing a rolling bearing raceway defect expansion failure, comprising the steps of:
S1, judging the severity of the fault according to the size of the raceway defect, wherein the method comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults;
s2, determining a fault morphology function and a rolling body displacement excitation function according to the fault severity;
S3, based on a rolling body displacement excitation function, respectively calculating the Hertz contact stiffness coefficients of the rolling body and the inner and outer raceways, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing;
S4, based on the Hertz contact stiffness coefficient of the rolling bearing, calculating the contact force and friction force between the rolling body and the rollaway nest to obtain the contact deformation between the rolling body and the rollaway nest;
And S5, determining the nonlinear restoring force of the rolling bearing with the raceway defect expansion fault based on the contact force and the friction force between the rolling body and the raceway.
Further, in the step S1, if the rolling element cannot completely fall into the defect pit yet, it is determined as a slight failure; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling element falls into the defect pit and can roll, judging that the rolling element is seriously faulty, specifically comprising:
Calculating a fault range angle in the case of a moderate fault:
Wherein R b is the radius of the outer raceway, R g is the radius of the rolling body, and h f is the maximum defect depth;
Comparing the sizes of the fault range angles theta f and theta fm corresponding to the expansion of the raceway defects by taking the fault range angle theta fm as a judging threshold value, and if theta f∈(0,θfm), if the rolling bearing is in a slight fault; if theta f＝θfm, the rolling bearing is in a moderate fault; if θ f>θfm, the rolling bearing is in heavy failure.
Further, the step S2 is to determine a fault morphology function and a rolling element displacement excitation function according to the severity of the fault, and specifically includes:
1) When the fault is slight and moderate, the rolling body is contacted with two edge points of the defect pit, the two edge points are used as circle centers to respectively form a first section of motion track and a second section of motion track, and the expression of the first section of motion track is as follows:
The expression of the second section of motion trail is as follows:
Assuming that the j-th rolling element position angle is θ j, the rolling element displacement excitation function d (θ j) at this point is expressed as follows:
In the formula, θ fR represents the position angle of the defect center, and the expressions of A 1、A2, delta and epsilon are as follows:
2) In the case of severe faults, the fault morphology is assumed to be an approximate elliptic curve, the long half shaft is a f, the short half shaft is b f, and the following steps are provided:
Pushing out the expression of b f according to the above formula (10);
the fault morphology function has the expression:
From the above formula (11), the fault morphology function is a function related to the maximum defect depth h f, the fault range angle θ f, and the bearing outer raceway radius R b;
For the rolling element displacement excitation d (θ j) at the position angle of the jth rolling element, it is expressed as follows:
In the method, in the process of the invention,
In addition, θ fR is a position angle where the defect center is located, s fj is a roughness at the j-th ball position in the bearing defect range, and the expression is as follows:
sfj＝φjdf (14)
where d f is the maximum profile value of the roughened surface profile and phi j is a random number uniformly distributed between-1 and 1.
Further, step S3, based on the rolling element displacement excitation function, calculates the hz contact stiffness coefficients of the rolling element and the inner and outer raceways, and further obtains the hz contact stiffness coefficient of the rolling bearing, which specifically includes:
Let the expression of the hertz contact stiffness coefficient k bj' of the rolling bearing be:
Wherein, for the roller bearing, n is 10/9; for the ball bearing, n is 3/2, k bej (e=i/o) represents the hertz contact stiffness coefficient of the rolling element and the inner and outer raceways respectively, and the expression is as follows:
Wherein E b is the elastic modulus, v b is the Poisson's ratio, and l b is the roller length; Σρ e is the sum of the curvatures of the ball and the raceway, δ e * is the dimensionless contact deflection, and the expressions of the two are as follows:
∑ρe＝ρxI+ρyI+ρxIIe+ρyIIe,e＝i/o (17)
Wherein,
Wherein ρ xI、ρyI、ρxIIe、ρyIIe is the principal radius of curvature of the rolling elements in contact with the inner and outer raceways, where e=i/o, and the specific expression is as follows:
Wherein d b is the diameter of the rolling element; f i denotes an inner raceway radius of curvature coefficient, f o denotes an outer raceway radius of curvature coefficient, d m denotes a bearing pitch diameter, and as can be seen from the above, once a ball bearing fails, not only a corresponding additional displacement excitation is generated, but also the hz contact stiffness coefficient is changed, and α j' denotes a contact angle between a jth rolling element and a raceway, and the expression is:
drj′＝xbcosθj+ybsinθj-c0-d(θj)cosα0 (22)
daj′＝zb+rdj(θxbsinθj-θybcosθj)-d(θj)sinα0 (23)
Wherein α 0 represents an initial contact angle, c 0 represents an initial bearing play, and a 0 represents an initial distance between the centers of curvature of the inner and outer raceways;
x b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the x-axis direction, y b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the y-axis direction, z b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the z-axis direction, theta xb is the rotation angle of the inner ring of the bearing relative to the outer ring around the x-axis direction, and theta yb is the rotation angle of the inner ring of the bearing relative to the outer ring around the y-axis direction; d aj 'and d rj' are axial and radial contact deformations, respectively; θ j is the position angle of the jth rolling element, and the expression is as follows:
Wherein N b is the number of rolling bodies, r b is the radius of an inner raceway, ω r is the rotational angular velocity of a rotating shaft, c c is the cage pocket gap, and t is time.
Further, the step S4 is to calculate a contact force and a friction force between the rolling element and the raceway based on the hertz contact stiffness coefficient of the rolling bearing, and obtain a contact deformation between the rolling element and the raceway, and specifically includes:
Assuming that the friction force between the rolling elements and the raceway satisfies the coulomb friction law, the contact force Q bj and the friction force F fj between the jth rolling element and the raceway are expressed as:
Qbj＝kbj′(dj′)n (25)
Wherein μ is a coefficient of friction; d j' is the contact deformation between the jth rolling element and the raceway, further written as:
Further, the step S5 is to determine a non-linear restoring force of the rolling bearing including the raceway defect expansion failure based on the contact force and the friction force between the rolling element and the raceway, and the specific expression is as follows:
Wherein, F bx ' means a component force of the bearing restoring force along the x-axis direction, F by ' means a component force of the bearing restoring force along the y-axis direction, F bz ' means a component force of the bearing restoring force along the z-axis direction, M bx ' means a component moment of the bearing restoring force about the x-axis direction, M by ' means a component moment of the bearing restoring force about the y-axis direction, and r dj means a radial distance of the center of curvature of the inner race at the j-th ball position.
The invention also provides a fault diagnosis system for the defect expansion of the rolling bearing raceway, which comprises the following steps:
The fault severity judging module is used for judging the fault severity according to the size of the raceway defect and comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults;
the function determining module is used for determining a fault morphology function and a rolling body displacement excitation function according to the fault severity;
The Hertz contact stiffness coefficient determining module is used for respectively calculating the Hertz contact stiffness coefficients of the rolling bodies and the inner and outer raceways based on the rolling body displacement excitation function, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing;
The contact deformation determining module is used for calculating the contact force and the friction force between the rolling body and the roller path based on the Hertz contact stiffness coefficient of the rolling bearing to obtain the contact deformation between the rolling body and the roller path;
and the rolling bearing nonlinear restoring force determining module is used for determining the rolling bearing nonlinear restoring force containing the raceway defect expansion fault based on the contact force and the friction force between the rolling bodies and the raceway.
According to the specific embodiment provided by the invention, the invention discloses the following technical effects: the rolling bearing raceway defect expansion fault diagnosis method and system provided by the invention are based on Hertz contact theory, consider the influence of rough surface caused by bearing defect expansion, and provide a more real rolling bearing expansion defect fault characterization method, which can describe the nonlinear supporting force of the rolling bearing in different raceway defect expansion processes, can be applied to dynamic modeling of complex rotary machinery, and simulate bearing defect faults with different expansion degrees. In addition, the defect expansion process at the outer raceway is taken as an example in the description, and the defect expansion characterization method is also applicable to the defect degree characterization of other types of rolling bearings such as ball bearings and roller bearings and any positions such as inner raceways, outer raceways and rolling bodies. Therefore, the invention can provide technical support for evaluating the damage degree of the bearing raceway under the actual running condition of the rotary machine.
Drawings
In order to more clearly illustrate the embodiments of the present invention or the technical solutions of the prior art, the drawings that are needed in the embodiments will be briefly described below, it being obvious that the drawings in the following description are only some embodiments of the present invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a flow chart of a method for diagnosing a rolling bearing raceway defect expansion failure of the present invention;
in fig. 2, (a) shows a schematic view of a rolling bearing failure, and (b) - (d) show schematic views of mild, moderate and severe failure, respectively;
In fig. 3, (a) shows a schematic diagram of a movement trace of the rolling element under a slight fault, and (b) shows a schematic diagram of a geometrical relationship corresponding to the slight fault;
FIG. 4 is a schematic illustration of the internal dimensional relationships of the bearing of the present invention;
FIG. 5 is a schematic diagram of a dual-span rotor-bearing housing system according to an embodiment of the present invention;
FIG. 6 is a force diagram of a dual-span rotor-bearing housing system according to an embodiment of the present invention;
FIG. 7 is a schematic view of a defective faulty bearing (outer ring portion) according to the present invention;
FIG. 8 is a schematic diagram of vibration response of a defective fault bearing, wherein (a) represents a experimentally measured waveform chart, (b) represents an experimentally measured envelope spectrum, (c) represents a simulated waveform chart, and (d) represents a simulated envelope spectrum;
FIG. 9 is a graph showing the effects of different levels of failure on the magnitude of the characteristic frequency of bearing defects;
reference numerals illustrate: in fig. 2: 2-1, the j-th rolling element; 2-2, a retainer; 2-3, inner ring; 2-4, an outer ring;
In fig. 5: 1. a first support bearing; 2. a second supporting bearing; 3. a third supporting bearing; 4. a support bearing IV; 5. a first bearing; 6. a second bearing; 7. a first shaft; 8. a first disk; 9. a second shaft; 10. a second disc; 11. a first nut; 12. a first shaft sleeve; 13. a second shaft sleeve; 14. a shaft sleeve III; 15. a shaft sleeve IV; 16. and a second nut.
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 invention aims to provide a rolling bearing raceway defect expansion fault diagnosis method, which simulates the situation of the raceway defect expansion fault more in line with reality based on the defect area parameter of the raceway defect expansion fault and the actual structural parameter of the rolling bearing, and evaluates the damage degree of the rolling bearing under the actual running condition of the rolling bearing.
In order that the above-recited objects, features and advantages of the present invention will become more readily apparent, a more particular description of the invention will be rendered by reference to the appended drawings and appended detailed description.
Initial conditions are first determined: let N b be the number of rolling elements of a certain rolling bearing, R b be the inner raceway radius, R b be the outer raceway radius, d b be the rolling element diameter, c 0 be the initial bearing play, c c be the cage pocket gap. The initial contact angle is α 0. The inner ring rotates along with the rotating shaft, and the angular speed is omega r. In fig. 2 (a) is a schematic diagram of a rolling bearing with a defect expansion fault, and it is assumed that the outer raceway of the bearing has a defect expansion fault, the maximum defect depth is h f, and the fault range angle is θ f. The assumptions are made as follows:
(1) The influence of factors such as temperature, lubrication and the like is not considered;
(2) Compared with the centrifugal force and the gyroscopic moment of the rotary machine, the centrifugal force and the gyroscopic moment of the rolling bodies have smaller influence, so that the effects of the centrifugal force and the gyroscopic moment of the rolling bodies of the bearing are not considered;
(3) The roughness at the bearing defect cannot be ignored because the defect of the raceway is rugged. While the roughness effect at non-defects is negligible with less impact.
As shown in fig. 1, the method for diagnosing the rolling bearing raceway defect expansion fault provided by the invention comprises the following steps:
S1, judging the severity of the fault according to the size of the raceway defect, wherein the method comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults;
s2, determining a fault morphology function and a rolling body displacement excitation function according to the fault severity;
S3, based on a rolling body displacement excitation function, respectively calculating the Hertz contact stiffness coefficients of the rolling body and the inner and outer raceways, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing;
S4, based on the Hertz contact stiffness coefficient of the rolling bearing, calculating the contact force and friction force between the rolling body and the rollaway nest to obtain the contact deformation between the rolling body and the rollaway nest;
And S5, determining the nonlinear restoring force of the rolling bearing with the raceway defect expansion fault based on the contact force and the friction force between the rolling body and the raceway.
Illustratively, (b) - (d) in fig. 2 are schematic diagrams of the evolution of the defect failure of the outer ring of the rolling bearing. In the initial state, the outer ring is slightly defective due to microscopic cracks of the minor surface, and at this time the rolling elements cannot yet fall completely into defective pits, which is noted as a slight failure, as shown in fig. 2 (b). As the rolling bodies continuously press the defective edge, the defective edge portion is further caused to peel off, and the minute defect is further expanded. The rolling elements just able to fall into the defect pit are noted as moderate faults, as shown in fig. 2 (c). As the defect continues to expand to both sides, the fault range angle gradually expands, dropping the rolling elements into the defect pit and allowing rolling to be noted as a serious fault, as shown in fig. 2 (d).
In the step S1, if the rolling elements cannot completely fall into the defect pit yet, a slight fault is determined; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling element falls into the defect pit and can roll, judging that the rolling element is seriously faulty, specifically comprising:
according to fig. 2 (c), the fault range angle in the case of a moderate fault is calculated:
Wherein R b is the radius of the outer raceway, R g is the radius of the rolling body, and h f is the maximum defect depth;
Comparing the sizes of the fault range angles theta f and theta fm corresponding to the expansion of the raceway defects by taking the fault range angle theta fm as a judging threshold value, and if theta f∈(0,θfm), if the rolling bearing is in a slight fault; if theta f＝θfm, the rolling bearing is in a moderate fault; if θ f>θfm, the rolling bearing is in heavy failure.
Further, the step S2 is to determine a fault morphology function and a rolling element displacement excitation function according to the severity of the fault, and specifically includes:
1) In the case of mild and moderate failure
In a slight fault condition of the rolling bearing, the movement trace of the rolling body in the defective fault region is shown in fig. 3 (a). It is noted that the movement trace of the rolling elements is independent of the defect shape. When the rolling body rolls into the fault area, the rolling body can be contacted with the defect edge point O 1, at the moment, the rolling body can circularly move along the revolution direction of the rolling body by taking the point O 1 as the circle center and R g as the radius until the rolling body is contacted with the defect other edge point O 2. The respective rolling element center moves from point a to point B and reaches the maximum descent depth of the rolling element at point B. Then, the rolling body continuously performs circular motion along the revolution direction of the rolling body by taking the O 2 point as the circle center until the rolling body rolls out of the defect area. At this time, the center position of the rolling element is located at the point C. Thus, according to the geometric relationship shown in FIG. 3 (b), the rolling elements are centeredThe motion trajectory equation of a segment can be expressed as:
Similarly, the rolling bodies are centered at The motion trajectory equation of a segment can be expressed as:
Assuming that the j-th rolling element position angle is θ j, the rolling element displacement excitation function d (θ j) at this point is expressed as follows:
In the formula, θ fR represents the position angle of the defect center, and the expressions of A 1、A2, delta and epsilon are as follows:
2) In severe fault
If θ f>θfm, i.e. the bearing is in a severe fault condition, the defect fault morphology can be assumed to be an approximate elliptic curve, the long half axis is a f, and the short half axis is b f. As can be seen from fig. 4:
Pushing out the expression of b f according to the above formula (10);
the fault morphology function has the expression:
From the above formula (11), the fault morphology function is a function related to the maximum defect depth h f, the fault range angle θ f, and the bearing outer raceway radius R b;
For the rolling element displacement excitation d (θ j) at the position angle of the jth rolling element, it is expressed as follows:
In the method, in the process of the invention,
In addition, θ fR is a position angle where the defect center is located, s fj is a roughness at the j-th ball position in the bearing defect range, and the expression is as follows:
sfj＝φjdf (14)
where d f is the maximum profile value of the roughened surface profile and phi j is a random number uniformly distributed between-1 and 1.
Specifically, step S3 is to calculate the hz contact stiffness coefficients of the rolling element and the inner and outer raceways based on the rolling element displacement excitation function, and further obtain the hz contact stiffness coefficient of the rolling bearing, and specifically includes:
Let the expression of the hertz contact stiffness coefficient k bj' of the rolling bearing be:
Wherein, for the roller bearing, n is 10/9; for a ball bearing, n is 3/2, k bej (e=i/o) represents the hertz contact stiffness coefficients of the rolling elements and the inner and outer raceways respectively (the calculation formulas of the inner and outer raceways are the same for the expression of formula 16, the difference is that the coefficients in the formulas are different, see formula 20), and the expression is as follows:
Wherein E b is the elastic modulus, v b is the Poisson's ratio, and l b is the roller length; Σρ e is the sum of the curvatures of the ball and the raceway, δ e * is the dimensionless contact deflection, and the expressions of the two are as follows:
∑ρe＝ρxI+ρyI+ρxIIe+ρyIIe,e＝i/o (17)
Wherein,
Wherein ρ xI、ρyI、ρxIIe、ρyIIe is the principal radius of curvature of the rolling elements in contact with the inner and outer raceways, where e=i/o, and the specific expression is as follows:
Wherein d b is the diameter of the rolling element; f i denotes an inner raceway radius of curvature coefficient, f o denotes an outer raceway radius of curvature coefficient, d m denotes a bearing pitch diameter, and as can be seen from the above, once a ball bearing fails, not only a corresponding additional displacement excitation is generated, but also the hz contact stiffness coefficient is changed, and α j' denotes a contact angle between a jth rolling element and a raceway, and the expression is:
drj′＝xbcosθj+ybsinθj-c0-d(θj)cosα0 (22)
daj′＝zb+rdj(θxbsinθj-θybcosθj)-d(θj)sinα0 (23)
Wherein α 0 represents an initial contact angle, c 0 represents an initial bearing play, and a 0 represents an initial distance between the centers of curvature of the inner and outer raceways;
x b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the x-axis direction, y b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the y-axis direction, z b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the z-axis direction, theta xb is the rotation angle of the inner ring of the bearing relative to the outer ring around the x-axis direction, and theta yb is the rotation angle of the inner ring of the bearing relative to the outer ring around the y-axis direction; d aj 'and d rj' are axial and radial contact deformations, respectively; θ j is the position angle of the jth rolling element, and the expression is as follows:
/>
Wherein N b is the number of rolling bodies, r b is the radius of an inner raceway, ω r is the rotational angular velocity of a rotating shaft, c c is the cage pocket gap, and t is time.
From the results shown in fig. 2 (a) - (d), it is known that the bearing defects gradually collapse at the edges, and thus the defect morphology is uneven. Therefore, the effect of friction should not be neglected when the balls roll into the defective load bearing area.
For example, the step S4 calculates the contact force and the friction force between the rolling element and the raceway based on the hertz contact stiffness coefficient of the rolling bearing, and obtains the contact deformation between the rolling element and the raceway, which specifically includes:
Assuming that the friction force between the rolling elements and the raceway satisfies the coulomb friction law, the contact force Q bj and the friction force F fj between the jth rolling element and the raceway are expressed as:
Qbj＝kbj′(dj′)n (25)
Wherein μ is a coefficient of friction; d j' is the contact deformation between the jth rolling element and the raceway, further written as:
Further, the step S5 is to determine a non-linear restoring force of the rolling bearing including the raceway defect expansion failure based on the contact force and the friction force between the rolling element and the raceway, and the specific expression is as follows:
Wherein, F bx ' means a component force of the bearing restoring force along the x-axis direction, F by ' means a component force of the bearing restoring force along the y-axis direction, F bz ' means a component force of the bearing restoring force along the z-axis direction, M bx ' means a component moment of the bearing restoring force about the x-axis direction, M by ' means a component moment of the bearing restoring force about the y-axis direction, and r dj means a radial distance of the center of curvature of the inner race at the j-th ball position.
Examples:
The bearing-rotor system of a test bed is taken as a modeling object. The system can be seen as a double-span rotor-bearing housing system supported by four bearings, as shown in fig. 5.
The system comprises 2 shafts, 1 bearing seat, 6 bearings, 2 nuts, 4 shaft sleeves, 1 belt pulley and other parts. The motor transmits power to the second shaft 9 through belt transmission. The second shaft 9 transmits power further into the first shaft 7 through the coupling. Of the 6 bearings, 4 bearings (support bearing one 1 to support bearing four 4) play a supporting role, and the other 2 bearings (bearing one 5 and bearing two 6) play a role of connecting the bearing housing with the shaft one 7. The test bed can apply a radial load in the negative x-axis direction, which acts on the bearing blocks and transfers the load further to the first shaft 7 via the first bearing 5.
The support bearing 1 and the support bearing 2 are known to be of a deep groove ball bearing 6011, which is used for supporting the shaft 7. The support bearing three 3 and the support bearing four 4 are of the type of angular ball bearing 7306C for supporting the second shaft 9. The first bearing 5 and the second bearing 6 are also deep groove ball bearings 6011. The geometric parameters of bearing 6011 and bearing 7306C can be seen in table 1.
The length of the first shaft 7 was 204mm and the diameter was 55mm. The length of the first disk 8 is 25mm, the outer diameter is 68.6mm, and the inner diameter is 55mm. The length of the second shaft 9 is 1420mm. The second disk 10 has a length of 15mm, an outer diameter of 75mm and an inner diameter of 30mm.
Table 1 main parameters of bearings 6011 and 7306C
As shown in fig. 6, to highlight the major contradiction, the double-span rotor-bearing housing system dynamics model makes the following assumptions:
(1) The first axis and the second axis are simulated by adopting a finite element method. Wherein, the first shaft is divided into 22 shaft segment units, and the second shaft is divided into 34 shaft segment units. All shaft section units adopt a Timoshenko beam unit model. The shaft segment parameters are shown in table 2. Each shaft segment contains 2 nodes in total, 12 degrees of freedom.
(2) Disc one is still modeled using the finite element method. Disk two is modeled using a centralized parametric approach, with a centralized quality point at node 57. The mass, the diameter moment of inertia and the pole moment of inertia of the second disc can be calculated according to the density and the geometric parameters of the belt pulley. In addition, 4 shaft sleeves and 2 nuts in the system are modeled by adopting a centralized parameter method. The 6 concentrated quality points are located at nodes 2, 6, 10, 14, 18, 22 in turn. And assuming that all imbalance forces in the system act on the concentrated mass points. Because the bearing seat has larger mass and does not rotate along with the shaft, the local deformation of the bearing seat is ignored, and the bearing seat is equivalent to a concentrated mass point. The concentrated mass point number is 59, considering only vibration of 2 degrees of freedom in the radial direction. The above concentrated quality parameters are detailed in table 3.
(3) The nonlinear factors of the dynamic model of the double-span rotor-rolling bearing-bearing seat system are mainly three. The non-linear supporting force of the rolling bearing, the non-linear supporting force of the bearing seat and the non-linear characteristic caused by the clearance fit of the coupling. The 4 support bearings are all simulated by adopting a nonlinear bearing force model and are sequentially positioned on the nodes 3, 7, 17 and 21. The support bearing is assumed to have a defect failure, and the rest support bearings are all healthy bearings. Since the first bearing and the second bearing only play a role in transmitting radial loads, the two bearings are equivalent to linear stiffness models. Wherein the first bearing connects the node 7 on the first shaft with the bearing seat node 59. The second bearing connects the node 17 on the first shaft with the bearing seat node 59. The coupling between the node 23 on the first shaft and the node 24 on the second shaft is likewise simplified to a spring-damping model. The support stiffness parameters of each member are shown in table 4.
Table 2 double-span rotor shaft segment unit parameters
TABLE 3 centralized quality point parameters
TABLE 4 support stiffness of the various components
A schematic diagram of the stress of the double-span rotor-bearing housing system is shown in fig. 6. According to Newton's second law, a bearing seat dynamics equation is established as follows:
Wherein m p is the mass of the bearing seat and is 12.77kg. k b1,2 and c b1,2 are equivalent support stiffness and damping for bearing one and bearing two, respectively. F r is the radial load to which the bearing housing is subjected. g represents the gravity acceleration, 9.81m/s 2.Fp is the nonlinear supporting force of the bearing seat, and the expression is:
in the formula, k p and c p are the bearing rigidity and damping of the bearing housing, respectively.
The matrix form of the dynamic equation of the double-span rotor-rolling bearing-bearing housing system can be expressed as:
Wherein M, J, K, C is the mass, gyro, rigidity and damping matrix of the system. Q is the vibration displacement vector of the system. F R、FU、FB、FG is the radial force, unbalanced force, bearing force, gravity vector of the system in turn. The corresponding expressions are as follows:
C＝αM+βK
FU＝[0,…,0,FUx1,FUy1,0,0,0,0,0,…,0,FUxq,FUyq,0,0,0,0,0,…,0,FUx57,FUy57,0,0,0,0,0,…,0]T
(q＝2,6,10,14,18,22,57)
FB＝[0,…,0,Fbxq′,Fbyq′,Fbzq′,Mbxq′,Mbyq′,0,0,…,0,Fbxp,Fbyp,Fbzp,Mbxp,Mbyp,0,0,…,0]T
(q＝3,p＝21,25,55)
FG＝[0,FG1,0,0,0,0,0,…,0,0,FGq,0,0,0,0,0,…,0,0,FG59]T,FGq＝-mqg,(q＝1,2,…,59)
In the formula, M S1、MS2、JS1、JS2、KS1、KS2 is the mass, gyro and rigidity matrix of the double-span rotor (a first shaft and a second shaft). K C is the rigidity matrix of the coupling. K B is the supporting stiffness matrix of the first bearing and the second bearing. M P and K P are the mass matrix and the support stiffness matrix of the bearing block, respectively. F Uxq and F Uyq are unbalanced forces at node q. F Gq and m q are the gravity and mass, respectively, at node q. In addition, the damping of the system is simulated in a proportional damping mode.
In order to verify the effectiveness of the defect characterization model, rolling bearing vibration tests with different defect depths are carried out, and acceleration signals at the outer surface of the bearing seat are collected. The radial loads applied by the test bed were all 2kN, and the running speed was 4200r/min. The outer race of the test fault bearing is shown in fig. 7. The maximum defect depth of the faulty bearing is known to be 0.05mm, with a defect range of 30 °. The fault bearing is mounted at one place of the support bearing. The vibration waveforms and envelope spectra of the fault bearings measured by the test are shown in fig. 8 (a) - (b), respectively. Setting simulation parameters to be the same as test working condition parameters, extracting vibration response results at a bearing seat (node 59), and drawing vibration acceleration waveforms and envelope spectrograms of the simulated and calculated bearing with faults, wherein the results are shown in fig. 8 (c) - (d).
As can be seen from fig. 8 (a) - (b), when the bearing is operating in a fault condition, the system vibration frequency at the bearing seat is dominated by the rolling bearing compliance vibration frequency (i.e., the outer ring fault characteristic frequency) and its higher harmonic frequency component nf vc due to the periodic excitation of the rolling bearing in a fault condition. Simulation and test results show that the amplitude of the frequency f vc is maximum, and the amplitude of the 2f vc、3fvc、4fvc and other higher harmonic frequencies are sequentially reduced. In addition, a frequency conversion f r with a lower amplitude exists in the system. Subsequently, test tests and simulation calculations were performed with defect depths of 0, 0.01mm, and 0.03mm, respectively. Further extracting the characteristic frequency f vc amplitude values of the healthy bearings obtained by simulation and test under different bearing defect depths as shown in figure 9. The amplitude of the frequency f vc is seen to increase with increasing defect depth, indicating that the more severe the bearing defect failure, the greater the frequency amplitude of f vc. The simulation is the same as the evolution law obtained by the test, and the amplitude value obtained by the simulation and the test is not much different under each working condition. The rules verify the correctness of the system dynamics model and the calculation result of the bearing in the fault state.
The invention also provides a fault diagnosis system for the defect expansion of the rolling bearing raceway, which comprises the following steps:
The fault severity judging module is used for judging the fault severity according to the size of the raceway defect and comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults;
the function determining module is used for determining a fault morphology function and a rolling body displacement excitation function according to the fault severity;
The Hertz contact stiffness coefficient determining module is used for respectively calculating the Hertz contact stiffness coefficients of the rolling bodies and the inner and outer raceways based on the rolling body displacement excitation function, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing;
The contact deformation determining module is used for calculating the contact force and the friction force between the rolling body and the roller path based on the Hertz contact stiffness coefficient of the rolling bearing to obtain the contact deformation between the rolling body and the roller path;
and the rolling bearing nonlinear restoring force determining module is used for determining the rolling bearing nonlinear restoring force containing the raceway defect expansion fault based on the contact force and the friction force between the rolling bodies and the raceway.
The invention also provides an electronic device, which comprises one or more processors and a memory;
one or more applications, wherein the one or more applications are stored in the memory and configured to be executed by the one or more processors, the one or more applications configured to perform a rolling bearing race defect expansion fault diagnosis method as described above.
The present invention also provides a non-transitory computer readable storage medium having stored thereon a computer program, characterized in that the computer program, when executed by a processor, implements a rolling bearing raceway defect expansion failure diagnosis method as described above.
Of course, those skilled in the art will appreciate that implementing all or part of the above-described methods may be implemented by a computer program for instructing relevant hardware (such as a processor, a controller, etc.), where the program may be stored in a computer-readable storage medium, and where the program may include the steps of the above-described method embodiments when executed. The storage medium may be a memory, a magnetic disk, an optical disk, or the like.
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 assist in understanding the methods of the present invention and the core ideas thereof; also, it is within the scope of the present invention to be modified by those of ordinary skill in the art in light of the present teachings. In view of the foregoing, this description should not be construed as limiting the invention.
Claims (6)
1. The fault diagnosis method for the rolling bearing raceway defect expansion is characterized by comprising the following steps of:
S1, judging the severity of the fault according to the size of the raceway defect, wherein the method comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults; the method specifically comprises the following steps:
Calculating a fault range angle in the case of a moderate fault:
Wherein R b is the radius of the outer raceway, R g is the radius of the rolling body, and h f is the maximum defect depth;
Comparing the sizes of the fault range angles theta f and theta fm corresponding to the expansion of the raceway defects by taking the fault range angle theta fm as a judging threshold value, and if theta f∈(0,θfm), if the rolling bearing is in a slight fault; if theta f＝θfm, the rolling bearing is in a moderate fault; if theta f>θfm, the rolling bearing is in serious fault;
s2, determining a fault morphology function and a rolling body displacement excitation function according to the fault severity; the method specifically comprises the following steps:
1) When the fault is slight and moderate, the rolling body is contacted with two edge points of the defect pit, the two edge points are used as circle centers to respectively form a first section of motion track and a second section of motion track, and the expression of the first section of motion track is as follows:
The expression of the second section of motion trail is as follows:
Assuming that the j-th rolling element position angle is θ j, the rolling element displacement excitation function d (θ j) at this point is expressed as follows:
In the formula, θ fR represents the position angle of the defect center, and the expressions of A 1、A2, delta and epsilon are as follows:
2) In the case of severe faults, the fault morphology is assumed to be an approximate elliptic curve, the long half shaft is a f, the short half shaft is b f, and the following steps are provided:
Pushing out the expression of b f according to the above formula (10);
the fault morphology function has the expression:
From the above formula (11), the fault morphology function is a function related to the maximum defect depth h f, the fault range angle θ f, and the bearing outer raceway radius R b;
For the rolling element displacement excitation d (θ j) at the position angle of the jth rolling element, it is expressed as follows:
In the method, in the process of the invention,
In addition, θ fR is a position angle where the defect center is located, s fj is a roughness at the j-th ball position in the bearing defect range, and the expression is as follows:
sfj＝φjdf (14)
Wherein d f is the maximum profile value of the rough surface profile, phi j is a random number uniformly distributed between-1 and 1;
S3, based on a rolling body displacement excitation function, respectively calculating the Hertz contact stiffness coefficients of the rolling body and the inner and outer raceways, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing; the method specifically comprises the following steps:
Let the expression of the hertz contact stiffness coefficient k bj' of the rolling bearing be:
Wherein, for the roller bearing, n is 10/9; for a ball bearing, n is 3/2; k bej (e=i/o) represents the hertz contact stiffness coefficient of the rolling bodies and the inner and outer raceways respectively, and the expression is as follows:
Wherein E b is the elastic modulus, v b is the Poisson's ratio, and l b is the roller length; Σρ e is the sum of the curvatures of the ball and the raceway, δ e * is the dimensionless contact deflection, and the expressions of the two are as follows:
∑ρe＝ρxI+ρyI+ρxIIe+ρyIIe,e＝i/o (17)
Wherein,
Wherein ρ xI、ρyI、ρxIIe、ρyIIe is the principal radius of curvature of the rolling elements in contact with the inner and outer raceways, where e=i/o, and the specific expression is as follows:
dm′＝dm+d(θj) (20)
Wherein d b is the diameter of the rolling element; f i denotes an inner race radius of curvature coefficient, f o denotes an outer race radius of curvature coefficient, d m denotes a bearing pitch diameter, and α j' denotes a contact angle between a jth rolling element and a race, expressed by:
drj′＝xbcosθj+ybsinθj-c0-d(θj)cosα0 (22)
daj′＝zb+rdj(θxbsinθj-θybcosθj)-d(θj)sinα0 (23)
wherein α 0 represents an initial contact angle, c 0 represents an initial bearing play, and a 0 represents an initial distance between the centers of curvature of the inner and outer raceways; x b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the x-axis direction, y b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the y-axis direction, z b is the vibration displacement of the inner ring of the bearing relative to the outer ring along the z-axis direction, theta xb is the rotation angle of the inner ring of the bearing relative to the outer ring around the x-axis direction, and theta yb is the rotation angle of the inner ring of the bearing relative to the outer ring around the y-axis direction; d aj 'and d rj' are axial and radial contact deformations, respectively; θ j is the position angle of the jth rolling element, and the expression is as follows:
Wherein N b is the number of rolling bodies, r b is the radius of an inner raceway, omega r is the rotation angular speed of a rotating shaft, c c is the pocket clearance of a retainer, and t is time;
S4, based on the Hertz contact stiffness coefficient of the rolling bearing, calculating the contact force and friction force between the rolling body and the rollaway nest to obtain the contact deformation between the rolling body and the rollaway nest;
And S5, determining the nonlinear restoring force of the rolling bearing with the raceway defect expansion fault based on the contact force and the friction force between the rolling body and the raceway.
2. The method for diagnosing a rolling bearing raceway defect expansion failure according to claim 1, wherein the step S4 is based on a hertz contact stiffness coefficient of the rolling bearing, and the contact force and friction force between the rolling element and the raceway are calculated to obtain the contact deformation between the rolling element and the raceway, and specifically comprises:
Assuming that the friction force between the rolling elements and the raceway satisfies the coulomb friction law, the contact force Q bj and the friction force F fj between the jth rolling element and the raceway are expressed as:
Qbj＝kbj′(dj′)n (25)
Wherein μ is a coefficient of friction; d j' is the contact deformation between the jth rolling element and the raceway, further written as:
3. The rolling bearing raceway defect expansion failure diagnosis method according to claim 2, characterized in that the step S5 is to determine a rolling bearing nonlinear restoring force containing the raceway defect expansion failure based on a contact force and a friction force between the rolling elements and the raceway, and the specific expression is as follows:
Wherein F bx ' means a component force of the bearing restoring force in the x-axis direction, F by ' means a component force of the bearing restoring force in the y-axis direction, F bz ' means a component force of the bearing restoring force in the z-axis direction, M bx ' means a component moment of the bearing restoring force in the x-axis direction, M by ' means a component moment of the bearing restoring force in the y-axis direction, and r dj means a radial distance of the center of curvature of the inner race at the j-th ball position.
4. A rolling bearing raceway defect expansion failure diagnosis system that performs the rolling bearing raceway defect expansion failure diagnosis method according to any one of claims 1 to 3, characterized by comprising:
The fault severity judging module is used for judging the fault severity according to the size of the raceway defect and comprises the following steps: if the rolling bodies cannot fall into the defect pits completely, judging that the rolling bodies slightly fail; if the rolling bodies just can fall into the defect pits, judging that the rolling bodies have moderate faults; if the rolling bodies fall into the defect pits and can roll, judging that the rolling bodies have serious faults;
the function determining module is used for determining a fault morphology function and a rolling body displacement excitation function according to the fault severity;
The Hertz contact stiffness coefficient determining module is used for respectively calculating the Hertz contact stiffness coefficients of the rolling bodies and the inner and outer raceways based on the rolling body displacement excitation function, and further obtaining the Hertz contact stiffness coefficient of the rolling bearing;
The contact deformation determining module is used for calculating the contact force and the friction force between the rolling body and the roller path based on the Hertz contact stiffness coefficient of the rolling bearing to obtain the contact deformation between the rolling body and the roller path;
and the rolling bearing nonlinear restoring force determining module is used for determining the rolling bearing nonlinear restoring force containing the raceway defect expansion fault based on the contact force and the friction force between the rolling bodies and the raceway.
5. An electronic device, characterized in that:
Including one or more processors;
A memory;
One or more application programs, wherein the one or more application programs are stored in the memory and configured to be executed by the one or more processors, the one or more program configured to perform the rolling bearing raceway defect expansion failure diagnosis method of any one of claims 1 to 3.
6. A non-transitory computer readable storage medium having stored thereon a computer program, wherein the computer program when executed by a processor implements the rolling bearing raceway defect expansion failure diagnosis method according to any one of claims 1 to 3.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311030446.4A CN117313446B (en) | 2023-08-16 | 2023-08-16 | Rolling bearing raceway defect expansion fault diagnosis method and system |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202311030446.4A CN117313446B (en) | 2023-08-16 | 2023-08-16 | Rolling bearing raceway defect expansion fault diagnosis method and system |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN117313446A CN117313446A (en) | 2023-12-29 |
| CN117313446B true CN117313446B (en) | 2024-06-11 |
Family
ID=89296119
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202311030446.4A Active CN117313446B (en) | 2023-08-16 | 2023-08-16 | Rolling bearing raceway defect expansion fault diagnosis method and system |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN117313446B (en) |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015032097A (en) * | 2013-08-01 | 2015-02-16 | Ntn株式会社 | Kinetics analysis method and analysis device for rolling bearing |
| CN114595526A (en) * | 2021-12-27 | 2022-06-07 | 哈尔滨理工大学 | Method for reducing collision of rolling bodies of ball bearing without retaining |
| CN115270342A (en) * | 2022-08-01 | 2022-11-01 | 安徽大学 | Multi-degree-of-freedom dynamic modeling method for deep groove ball bearing with spalling fault |
| CN116561904A (en) * | 2023-03-21 | 2023-08-08 | 苏州大学 | Rolling bearing dynamics modeling and vibration characteristic analysis method |
-
2023
- 2023-08-16 CN CN202311030446.4A patent/CN117313446B/en active Active
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2015032097A (en) * | 2013-08-01 | 2015-02-16 | Ntn株式会社 | Kinetics analysis method and analysis device for rolling bearing |
| CN114595526A (en) * | 2021-12-27 | 2022-06-07 | 哈尔滨理工大学 | Method for reducing collision of rolling bodies of ball bearing without retaining |
| CN115270342A (en) * | 2022-08-01 | 2022-11-01 | 安徽大学 | Multi-degree-of-freedom dynamic modeling method for deep groove ball bearing with spalling fault |
| CN116561904A (en) * | 2023-03-21 | 2023-08-08 | 苏州大学 | Rolling bearing dynamics modeling and vibration characteristic analysis method |
Non-Patent Citations (2)
| Title |
|---|
| 滚动轴承-转子系统的非线性动力学分析;张利芹;张小龙;常映辉;;重型机械科技;20070325(01);全文 * |
| 考虑外圈局部缺陷的滚动轴承非线性动力特性;张耀强;陈建军;唐六丁;林立广;;航空学报;20090425(04);全文 * |
Also Published As
| Publication number | Publication date |
|---|---|
| CN117313446A (en) | 2023-12-29 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Liu | A dynamic modelling method of a rotor-roller bearing-housing system with a localized fault including the additional excitation zone | |
| CN109027017B (en) | method for evaluating wear state of space rolling bearing | |
| Niu et al. | A systematic study of ball passing frequencies based on dynamic modeling of rolling ball bearings with localized surface defects | |
| Niu et al. | Dynamic modeling and vibration response simulation for high speed rolling ball bearings with localized surface defects in raceways | |
| CN110674585B (en) | High-rotating-speed rolling bearing-rotor system local damage fault simulation method | |
| CN110617953B (en) | New energy automobile high-speed motor bearing-rotor system dynamic characteristic analysis method | |
| Gao et al. | Behaviour of an angular contact ball bearing with three-dimensional cubic-like defect: A comprehensive non-linear dynamic model for predicting vibration response | |
| Mufazzal et al. | Theoretical and experimental analyses of vibration impulses and their influence on accurate diagnosis of ball bearing with localized outer race defect | |
| Liu et al. | Vibration characteristics of a high-speed flexible angular contact ball bearing with the manufacturing error | |
| Hou et al. | Vibration analysis of ball bearing considering waviness under high speed and an axial load | |
| LetUriondo et al. | Multi-body modelling of rolling element bearings and performance evaluation with localised damage | |
| CN117313446B (en) | Rolling bearing raceway defect expansion fault diagnosis method and system | |
| Xu et al. | Vibration analysis of a gear-rotor-bearing system with outer-ring spalling and misalignment | |
| Xi et al. | Advances in key mechanical parameters for reliability assessment of high-speed train bearings | |
| CN115270342B (en) | Multi-degree-of-freedom dynamics modeling method for deep groove ball bearing with spalling fault | |
| Karacay et al. | Vibrations of a grinding spindle supported by angular contact ball bearings | |
| CN117010149A (en) | High-speed deep groove ball bearing fault dynamics modeling method considering external excitation of gears | |
| CN109145501A (en) | A kind of aero-engine intershaft bearing local damage fault vibration emulation mode | |
| CN114021270A (en) | Method for calculating supporting force of non-centering ball bearing | |
| CN114580093A (en) | Method for calculating dynamic response of ball bearing with local fault of raceway | |
| Liu et al. | Influence of the local defect distribution on vibration characteristics of ball bearings | |
| Kadarno et al. | Vibration analysis of defected ball bearing using finite element model simulation | |
| Mishra et al. | Rolling element bearing fault modelling to develop a diagnosis scheme for oscillating and non-uniform shaft rotation | |
| Wu et al. | Vibration characteristics of a roller bearing with the waviness error | |
| Wang et al. | Dynamic modeling and analysis of two-span rotor-pedestal system with bearing tilt and extended defect: Simulation and experiment |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |