CN109145501A - A kind of aero-engine intershaft bearing local damage fault vibration emulation mode - Google Patents
A kind of aero-engine intershaft bearing local damage fault vibration emulation mode Download PDFInfo
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Abstract
A kind of intershaft bearing local damage fault vibration emulation mode provided by the invention first determines each bearing element initial position and speed according to given parameters, then judges whether bearing element enters damage field according to bearing element and damage relative position.If not entering, the contact load between each bearing element is calculated according to normal intershaft bearing kinetic model；If into damage field, it then first passes through local damage mathematical model and determines bearing element contact load, then according still further to normal bearing kinetic model calculation process, acquire resultant force suffered by each bearing element and resultant moment, finally substitute into differential equation of motion, obtain the position and speed of subsequent time bearing element, after reaching simulation time, jump out circulation, export outer ring vibration acceleration response simulation result, after finally carrying out resampling processing to vibration signal, the time-domain diagram and envelope spectrum of simulation result are obtained；The present invention can more accurately and effectively realize the simulation and analysis of vibratory response when to aero-engine intershaft bearing generation local damage failure.
Description
Technical field
The invention belongs to simulation analysis fields, are related to a kind of aero-engine intershaft bearing local damage fault vibration emulation
Method.
Background technique
Modern aeroengine reduces weight to improve thrust ratio, be widely used intershaft bearing connection high pressure rotor and
Low pressure rotor, to construct birotor principle axis shafting.Intershaft bearing Internal and external cycle rotates simultaneously, and revolving speed is very high, and faces environment again
The problems such as temperature is high, and load is big, poor lubrication, therefore its Internal and external cycle or rolling element, inevitably occur local damage
Failure.And intershaft bearing is as critical component, once major accident will be caused by breaking down.In order to ensure aero-engine
Operational safety realizes the EARLY RECOGNITION and diagnosis of failure, it is necessary to study the vibration of failure intershaft bearing.
Domestic and foreign scholars are more to the research of straight roller bearing local damage failure, and intershaft bearing is because inside and outside
For circle in high speed rotation, working condition is complicated, it has to consider three-dimensional motion, centrifugal force and the gyroscopic effect of bearing element, interior,
Outer ring and rolling element skew, contact surface, which skids, and retainer collision is contour replies immediately miscellaneous dynamics problem, therefore it is big to model difficulty.
Seldom, existing be mostly to carry out simulation analysis based on simple plane kinematics model to current open report, not
Consider that inside and outside circle and rolling element skew, retainer mentioned above collide contour quick-action mechanics problem.Naval aviation engineering college
Xu Kejun etc., which considers rolling element, to be there is local damage (such as Xu Kejun, Dong Fanghua, Qin Hai be diligent has in the rolling element of local defect
The modeling of Jie's bearing system dynamics and simulation study [J] vibration and impact, 2016,35 (2): 104-109.) and inner ring appearance part damage
(Dynamic Modeling and Response Analysis [J] sea of Xu Kejun, Dong Fanghua, Qin Hai duty inner wrap strip defect intershaft bearing when hurting
Aeronautical engineering institute of army journal, 2015,30 (1): 36-42.) geometry approach amount variation, be based on the simple dynamics of two-freedom
Model foundation intershaft bearing local damage faulty power model.Application No. is 201410135565.0 patents of invention to disclose
A kind of bearing vibration containing Single Point of Faliure responds simulating analysis, it is characterized in that common rolling bearing can be emulated
Inner ring, outer ring or rolling element Single Point of Faliure vibratory response.
Critical component of the intershaft bearing as aero-engine, rolling element skids and the High-speed transients such as retainer collision are dynamic
Mechanics problem is serious, and sees from literature search above, and existing research is to be directed to common rolling bearing, and study mostly
In also do not consider retainer.In addition, comparing with plain bearing, this special cylinder roller bearing of intershaft bearing is also contemplated that outer
Rotation, inclination and the skew of circle, and Internal and external cycle revolving speed is very high, cannot ignore inner ring and rolling element skew, and contact surface skids
With the high speeds problem such as retainer collision, but the existing Vibration Simulation for intershaft bearing failure is studied and is not considered that these are asked
Topic, therefore simulation result is accurate not enough.And if carrying out the experiment of intershaft bearing local damage by artificial setting failure obtains vibration
Dynamic signal is studied, although result is the most accurate, time-consuming, laborious and cost are too high.
Summary of the invention
The purpose of the present invention is to provide a kind of intershaft bearing local damage fault vibration emulation modes, solve existing
Simulation study is carried out by the damage fault vibration of the plane kinematics model agency bearing of common rolling bearing, there is emulation
As a result not accurate enough problem.
In order to achieve the above object, the technical solution adopted by the present invention is that:
A kind of intershaft bearing local damage fault vibration emulation mode provided by the invention, comprising the following steps:
Step 1) obtains structural parameters, material parameter, operating condition and the lubrication parameter of bearing；Inertia seat is established respectively
Mark system Oixiyizi, rolling element determine body coordinate system Obxbybzb, set delineation body coordinate system Orxryrzr, contact coordinate system OkxkykzkWith
Damage coordinate system Odxdydzd, and into above-mentioned coordinate system input shaft bearing structural parameters and operating condition, obtain each bearing element
Initial motion state；
Step 2) establishes five degree of freedom intershaft bearing kinetic model drawn game according to the bearing parameter that step 1) inputs respectively
Mathematical model is damaged in portion；
Step 3) judges whether bearing element enters damage zone according to the relative position between bearing element and damage field
Domain calculates between each element of bearing if bearing element does not enter damage field according to normal intershaft bearing kinetic model
Normal direction contact load；If bearing element enters damage field, calculated between each element of bearing according to local damage mathematical model
Normal direction contact load；
Step 4), by step 2) five degree of freedom intershaft bearing kinetic model and step 3) obtained in each member of bearing
Normal direction contact load between part carries out numerical integration in conjunction with variable step quadravalence Runge-Kutta-Fehlberg method, obtains down
The position and speed of one moment bearing element；
Step 5), loop iteration step 2) to step 4), until jumping out circulation after reaching simulation time；
Step 6) exports the vibratory response of outer ring acceleration, finally obtains the vibration of intershaft bearing local damage failure acceleration
The time-domain diagram and envelope spectrum of response.
Preferably, in step 1), structural parameters include bearing inner race diameter, outer rollaway nest diameter, rolling element diameter, keep
Frame internal diameter, rolls body length, rolling element number, retainer width, lesion width and lesion depths at retainer outer diameter；
Material parameter includes the elasticity modulus and Poisson's ratio of bearing inner race, bearing outer ring, rolling element and retainer；
Operating condition includes the radial load and axis that the revolving speed of bearing inner race, bearing outer ring revolving speed, bearing inner race are born
The radial load that bearing outer-ring is born；
Lubrication parameter includes tetra- lubricant ginsengs of A, B, C and D in lubricant trailed model μ=(A+Bu) exp (- Cu)+D
Number, in formula, μ is sliding speed when being u coefficient of friction；
The initial motion state of each bearing element includes the matter of bearing inner race, bearing outer ring, retainer and each rolling element
Heart position and speed.
Preferably, in step 2, five degree of freedom intershaft bearing kinetic model includes bearing inner race, rolling element and retainer
Translation and rotation the differential equation and bearing outer ring differential equation of motion, specifically:
Bearing inner race, the translation of rolling element and retainer and the rotation differential equation are expressed as follows:
In formula: m is bearing inner race, rolling element or retainer quality, and x is bearing element displacement, and t is the time, and ∑ F is bearing
The suffered resultant force of element, wherein the suffered resultant force of bearing element includes normal direction contact load fNWith tangential tractive force fτ；ω is angular speed,
J is rotary inertia, and ∑ M is resultant moment suffered by bearing element；
The differential equation of motion of bearing outer ring are as follows:
In formula, moFor bearing outer ring quality, yoAnd zoRespectively bearing outer ring mass center Y-axis and Z-direction displacement,WithRespectively bearing outer ring mass center Y-axis and Z-direction speed,WithFor bearing outer ring mass center Y-axis and Z axis acceleration
Degree, ∑ FyWith ∑ FzRespectively bearing outer ring resultant force suffered by Y-axis and Z-direction, kyAnd kzRespectively bearing outer ring is in Y
The stiffness coefficient of axis and Z-direction, cyAnd czRespectively damped coefficient of the bearing outer ring in Y-axis and Z-direction.
Preferably, if having a width on bearing outer ring is wd, depth hdDamage, judge rolling element whether enter damage
The specific method in region is:
In local damage coordinate system, rolling element center and ZdAngle between axis is θbd, damage wrapping angle on raceway
Half be θe；Work as θbd< θeWhen, into damage field, conversely, not entering damage field then.
Preferably, the tool of the normal direction contact load between each element of bearing is calculated according to normal intershaft bearing kinetic model
Body method is:
S1, if the run-off the straight and when skew during operation of rolling element in bearing element, along its length by rolling element
Direction is divided into m' circle sheet with microtomy；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, if the contact point is p, is obtained when contacting between k-th of circle sheet and bearing other each elements by following formula
To the p point relative to the vector r between ferrule central positionpr
rpr=rbr+rpb
Wherein, rbrPosition vector of the body coordinate system center relative to set delineation body coordinate system center is determined for rolling element；
rpbThe position vector at body coordinate system center is determined relative to rolling element for p point；
S4, the deflection δ being calculate by the following formula between k-th of circle sheet and lassok:
δk=± (rpr3-0.5Dr)
Wherein, rpr3Represent rprThird component taken just outside bracket, Dr takes outer rollaway nest when slice is contacted with outer rollaway nest
Diameter, when slice is contacted with interior rollaway nest, bracket takes negative, and Dr takes interior rollaway nest diameter；
S5 works as δkWhen > 0, the single circle sheet and raceway contact load are calculated according to Hertz line contact theory, calculated public
Formula are as follows:
Wherein, EeqIt is equivalent elastic modulus, leqIt is effective contact length of rolling element, dx is circle sheet thickness；
S6, will be used for single circle sheet in S5 and the calculation formula of raceway contact load is integrated along its contact length,
Obtain the normal direction contact load f acted on entire rolling elementN；
S7, according to Newton's third law obtain the bearing being in contact respectively with rolling element it is inside and outside circle and retainer suffered by
Active force.
Preferably, it is calculate by the following formula tangential tractive force f suffered by each element of bearingτ:
fτ=μ fN
In formula, μ is traction lubrication friction coefficient.
Preferably, the normal direction contact load between bearing outer ring and each element of bearing is calculated using local damage mathematical model
Specific method be:
Rolling element is divided into m' circle sheet with microtomy along its length by S1；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, when being contacted between k-th of circle sheet and bearing other each elements, if the contact point is p, in contact coordinate
In system, the position vector between p point and m point isLine r between p point and m pointmpWith zkAngle between axis is θR, then roll
Road is in position θRRadius R (the θ at placeR) it is calculate by the following formula:
R(θR)=ror+hd；
In formula: ror --- the radius of outer rollaway nest, hdIt is θRFunction；
S4, the geometry approach amount between rolling element and local damage are as follows:
S5 calculates the single circle sheet and raceway contact load, calculation formula according to Hertz line contact theory are as follows:
Compared with the existing technology, beneficial effects of the present invention:
A kind of intershaft bearing local damage fault vibration emulation mode provided by the invention, based on it can be considered that inside and outside circle
It skids with rolling element skew, contact surface and retainer collides the contour five degree of freedom intershaft bearing power for replying immediately miscellaneous dynamics problem
It learns model and carries out simulation analysis, it can the more acurrate vibratory response for simulating intershaft bearing under aero-engine actual complex operating condition.
In addition, damage model covers inside and outside circle and rolling element three types failure, and bearing member is fully considered in analytic process
The variation of geometry approach amount when part passes through damage, therefore obtained fault vibration response is more comprehensive and accurate.In addition, to failure
Then bearing acceleration vibratory response resampling obtains time-domain diagram and the emulation mode of envelope spectrum and can accurately and effectively analyze
Bearing vibration signal fault signature.Therefore, the present invention, which can be realized more accurately and effectively, occurs aero-engine intershaft bearing
The simulation and analysis of vibratory response when local damage failure.
Detailed description of the invention
Fig. 1 is the flow chart of method involved by the present invention；
Fig. 2 is each bearing element interaction diagram of the present invention；
Fig. 3 is the kinetic model of bearing outer ring of the present invention；
Fig. 4 is that geometry approach amount changes when rolling element of the invention passes through local damage；
Fig. 5 is outer ring local damage fault vibration simulation result of the invention, wherein a) is responded for outer ring radial acceleration
Time-domain diagram, b) it is envelope spectrogram；
Fig. 6 is inner ring local damage fault vibration simulation result of the invention, wherein a) is responded for outer ring radial acceleration
Time-domain diagram, b) it is envelope spectrogram；
Fig. 7 is rolling element local damage fault vibration simulation result of the invention, wherein a) is rung for outer ring radial acceleration
Answer time-domain diagram, b) it is envelope spectrogram.
Specific embodiment
With reference to the accompanying drawing, the present invention is described in more detail.
As shown in Figure 1, a kind of intershaft bearing local damage fault vibration emulation mode provided by the invention, including following step
It is rapid:
Step 1) obtains structural parameters, material parameter, operating condition and the lubrication parameter of bearing；Inertia seat is established respectively
Mark system Oixiyizi, rolling element determine body coordinate system Obxbybzb, set delineation body coordinate system Orxryrzr, contact coordinate system OkxkykzkWith
Damage coordinate system Odxdydzd, and into above-mentioned coordinate system input shaft bearing structural parameters and operating condition, obtain each bearing element
Initial motion state provides operation initial value for kinetic model；
Step 2) establishes five degree of freedom intershaft bearing kinetic model drawn game according to the bearing parameter that step 1) inputs respectively
Mathematical model is damaged in portion；
Step 3) judges whether bearing element enters damage zone according to the relative position between bearing element and damage field
Domain calculates between each element of bearing if bearing element does not enter damage field according to normal intershaft bearing kinetic model
Normal direction contact load；If bearing element enters damage field, calculated between each element of bearing according to local damage mathematical model
Normal direction contact load；
Step 4), by step 2) five degree of freedom intershaft bearing kinetic model and step 3) obtained in each member of bearing
Normal direction contact load between part carries out numerical integration in conjunction with variable step quadravalence Runge-Kutta-Fehlberg method, obtains down
The position and speed of one moment bearing element；
Step 5), loop iteration step 2) to step 4), until jumping out circulation after reaching simulation time；
Step 6) exports the vibratory response of outer ring acceleration, finally obtains the vibration of intershaft bearing local damage failure acceleration
The time-domain diagram and envelope spectrum of response.
In the step 1), structural parameters spindle holds each element geometric parameter, including bearing inner race diameter, outer rollaway nest
Diameter, retainer internal diameter, retainer outer diameter, rolls body length, rolling element number, retainer width, damage width at rolling element diameter
Degree and lesion depths；
Material parameter includes the elasticity modulus and Poisson's ratio of bearing inner race, bearing outer ring, rolling element and retainer；
Operating condition includes the revolving speed and the born radial load of the inside and outside circle of bearing of bearing inner race and bearing outer ring；
Lubrication parameter refers to tetra- lubricant ginsengs of A, B, C and D in lubricant trailed model μ=(A+Bu) exp (- Cu)+D
Number, different parameters is corresponding with for different lubricants, the coefficient of friction that μ is sliding speed in formula when being u；
The initial motion state of each bearing element includes the matter of bearing inner race, bearing outer ring, retainer and each rolling element
Heart position and speed.
The specific method for obtaining bearing original part initial motion state is, as shown in Figure 2:
Firstly, establishing coordinate system, which includes inertial coodinate system Oixiyizi, rolling element determine body coordinate system Obxbybzb、
Set delineation body coordinate system Orxryrzr, contact coordinate system OkxkykzkWith damage coordinate system Odxdydzd；
Secondly, the structural parameters for obtaining bearing and operating condition parameter are input in above-mentioned coordinate system respectively, axis is obtained
Hold the initial motion state of element；Initial motion state refer to relative position under initial motion state between all parts and
Relative velocity.
Five degree of freedom intershaft bearing kinetic model in the step 2), so-called five degree of freedom include retainer, roll
Body, bearing inner race and the bearing outer ring planar movement and pivoting of both direction and rolling element, bearing inner race and axis
The inclination and skew of bearing outer-ring.
Five degree of freedom intershaft bearing kinetic model includes translation and the rotation differential of bearing inner race, rolling element and retainer
The differential equation of motion of equation and bearing outer ring, specifically:
Bearing element translation is described by Newton's law, describes the rotation of bearing element by Eulerian equation, bearing inner race,
The translation of rolling element and retainer and the rotation differential equation are expressed as follows:
In formula: m is bearing inner race, rolling element or retainer quality, and x is bearing element displacement, and t is the time, and ∑ F is bearing
The suffered resultant force of element, wherein the suffered resultant force of bearing element includes all normal direction contact load f suffered by bearing elementNWith it is suffered
All tangential tractive force fτ；ω is angular speed, and J is rotary inertia, and ∑ M is resultant moment suffered by bearing element；
In order to study the vibratory response of bearing, above-mentioned model is also needed by additionally increasing by two translations on outer ring freely
It spends to simulate the measurement of acceleration transducer in actual test, as shown in figure 3, the differential equation of motion of bearing outer ring are as follows:
In formula, moFor bearing outer ring quality, yoAnd zoRespectively bearing outer ring mass center Y-axis and Z-direction displacement,WithRespectively bearing outer ring mass center Y-axis and Z-direction speed,WithFor bearing outer ring mass center Y-axis and Z axis acceleration
Degree, ∑ FyWith ∑ FzRespectively bearing outer ring resultant force suffered by Y-axis and Z-direction, kyAnd kzRespectively bearing outer ring is in Y
The stiffness coefficient of axis and Z-direction, cyAnd czRespectively damped coefficient of the bearing outer ring in Y-axis and Z-direction.
In step 3), judges whether bearing element enters according to rolling element and damage relative position using piecewise function and damage
Wound needs to first pass through local damage mathematical model and contact load is calculated if judgement enters damage field, then will contact
Load is updated in the differential equation of motion of kinetic model and is calculated；Otherwise, normal intershaft bearing kinetic model is utilized
Calculate the normal direction contact load between each element of bearing:
As shown in figure 4, interior rollaway nest and rolling bulk damage are similar so that outer rollaway nest is damaged as an example；If having on bearing outer ring
One width is wd, depth hdDamage, judge whether rolling element enters the specific method of damage field and be:
In local damage coordinate system, the angle between rolling element center and Zd axis is θbd, damage wrapping angle on raceway
Half be θe；Work as θbd< θeWhen, into damage field, conversely, not entering damage field then.
The specific method of the normal direction contact load between each element of bearing is calculated according to normal intershaft bearing kinetic model
It is:
S1, when run-off the straight in roller operation process and skew, the contact between roller and lasso (inner ring or outer ring) is long
Degree can change in the axial direction, therefore, rolling element is divided into the circle that the m' center of circle is l with microtomy along its length
Thin slice；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, if the contact point is p, is obtained when contacting between k-th of circle sheet and bearing other each elements by following formula
To the p point relative to the vector r between ferrule central positionpr
rpr=rbr+rpb
Wherein, rbrPosition vector of the body coordinate system center relative to set delineation body coordinate system center is determined for rolling element；
rpbThe position vector at body coordinate system center is determined relative to rolling element for p point；
S4, the deflection δ being calculate by the following formula between k-th of circle sheet and lassok:
δk=± (rpr3-0.5Dr)
Wherein, rpr3Represent rprThird component taken just outside bracket, Dr takes outer rollaway nest when slice is contacted with outer rollaway nest
Diameter, when slice is contacted with interior rollaway nest, bracket takes negative, and Dr takes interior rollaway nest diameter；
S5 works as δkWhen > 0, the single circle sheet and raceway contact load are calculated according to Hertz line contact theory, calculated public
Formula are as follows:
Wherein, EeqIt is equivalent elastic modulus, leqIt is effective contact length of rolling element, dx is circle sheet thickness；
S6, will be used for single circle sheet in S5 and the calculation formula of raceway contact load is integrated along its contact length,
Obtain the normal direction contact load f acted on entire rolling elementN；
S7, according to Newton's third law obtain the bearing being in contact respectively with rolling element it is inside and outside circle and retainer suffered by
Active force.
It can get traction lubrication friction coefficient μ according to the lubrication parameter that step 1 obtains, contact load substituted into traction lubrication
Model obtains tangential tractive force f suffered by rolling element in turnτ, calculating formula is as follows:
fτ=μ fN
In turn, by by all normal direction contact load f suffered by bearing elementNWith suffered all tangential tractive force fτIt asks
With resultant force ∑ F suffered by bearing element is calculated；
In turn, each bearing element Moment is easy to get according to position vector,
It is counted finally, resultant force and Moment suffered by the bearing element being calculated are updated in differential equation of motion
It calculates, obtains the acceleration vibratory response of bearing outer ring, inner ring, rolling element and retainer, and then acquire each bearing member of subsequent time
The displacement of part and speed are inputted as the data of kinetic model.
The specific of the normal direction contact load between bearing outer ring and each element of bearing is calculated using local damage mathematical model
Method is:
Rolling element is divided into the circle sheet that the m' center of circle is l with microtomy along its length by S1；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, when being contacted between k-th of circle sheet and bearing other each elements, if the contact point is p, in contact coordinate
In system, the position vector between p point and outer rollaway nest center of circle m point isP point contacts load with the normal direction calculated between each element of bearing
Line r between lotus pointmpWith zkAngle between axis is θR, then raceway is in position θRRadius R (the θ at placeR) it is calculate by the following formula:
R(θR)=ror+hd；
In formula: ror --- the radius of outer rollaway nest, hdIt is θRFunction；
S4, the geometry approach amount δ between rolling element and local damagebdAre as follows:
S5 calculates the single circle sheet and raceway contact load, calculation formula according to Hertz line contact theory are as follows:
Geometry approach amount δbdThe main finger injury of variation there is caused additional clearance；Local damage mathematical model is main
For calculating the size of contact load between local damage and bearing element.
In step 4), variable step quadravalence Long Ge-is mainly utilized in the solution procedure of each bearing element differential equation of motion
Ku Ta-Fei Er Burger method, by solve the differential equation, available each bearing element acceleration, speed and displacement, in turn
Obtain the data input of subsequent time kinetic model.
In step 5), when obtaining intershaft bearing local damage failure acceleration vibratory response envelope spectrum, it is contemplated that the fortune of front
Dynamic differential equation uses variable step Integration Strategy, it is therefore desirable to vibrate and ring to the outer ring acceleration of kinetic model output
Resampling processing should be first carried out, then seeks envelope spectrum again.
A kind of aero-engine intershaft bearing local damage fault vibration of the invention is emulated below with reference to three examples
Method is described in further detail, while verifying correctness of the invention, but this example is not intended to restrict the invention.
The analysis method that this example is compared using simulation result and theoretical formula.It is intershaft bearing outer ring local damage first
Failure, emulation is NJ205EC cylinder roller bearing, and bearing parameter is shown in Table 1.
1 NJ205EC bearing parameter of table
It inputs above-mentioned parameter and carries out simulation analysis by flow chart, obtain outer ring radial acceleration vibratory response time-domain diagram and packet
Network spectrum is as shown in Figure 5.It is clearly apparent damage in time-domain diagram and generates impact, the time interval of adjacent impact just corresponds to outer ring event
Hinder characteristic frequency, and since outer ring rotates, it can be seen that supporting region and non-bearing area are obvious in time-domain diagram.In envelope spectrum, more
Significantly see that outer ring turns frequency 100Hz and fault characteristic frequency 788Hz, in non-slip situation, simulation result and failure are special
It is consistent to levy frequency theory formula calculated value 788Hz, illustrates the correctness of emulation mode.
Then agency bearing inner race local damage fault vibration response carries out simulation analysis, and bearing parameter used is equally such as
Shown in table 1.
It inputs 1 bearing parameter of table and carries out simulation analysis by flow chart, obtain outer ring radial acceleration response time-domain diagram and packet
Network spectrum is impacted as shown in fig. 6, being equally clearly visible in time-domain diagram caused by inner ring damage, and between adjacent two attack time
Every just corresponding to inner ring fault characteristic frequency, inner ring is more clearly seen in envelope spectrum and turns frequency 50Hz and inner ring fault signature frequency
Rate, simulation result is consistent with inner ring fault characteristic frequency theoretical formula method value 1162Hz in non-slip situation, illustrates emulation side
The correctness of method.
It is finally intershaft bearing rolling element damage fault, on single rolling element surface, processing width 0.6mm depth 0.6mm is damaged,
Other parameters and table 1 are consistent, obtain outer ring radial acceleration response time-domain diagram and envelope spectrum simulation result as shown in fig. 7, same
It has been clearly visible in time-domain diagram and has rolled the impact that bulk damage generates, and it is just rolling element that adjacent attack time interval is corresponding
Fault characteristic frequency.Theoretical formula, which is updated to, also with bearing geometric parameter obtains rolling element defect theory fault characteristic frequency
For 377Hz, simulation result is consistent with theoretical formula method value.
By examples detailed above analysis as can be seen that simulation result of the invention is non-with theoretical formula value in non-slip situation
Often consistent, correctness has been verified.
Claims (7)
1. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode, which comprises the following steps:
Step 1) obtains structural parameters, material parameter, operating condition and the lubrication parameter of bearing；Inertial coodinate system is established respectively
Oixiyizi, rolling element determine body coordinate system Obxbybzb, set delineation body coordinate system Orxryrzr, contact coordinate system OkxkykzkAnd damage
Coordinate system Odxdydzd, and into above-mentioned coordinate system input shaft bearing structural parameters and operating condition, it is initial to obtain each bearing element
Motion state；
Step 2) establishes five degree of freedom intershaft bearing kinetic model according to the bearing parameter that step 1) inputs respectively and part is damaged
Hurt mathematical model；
Step 3) judges whether bearing element enters damage field according to the relative position between bearing element and damage field,
If bearing element does not enter damage field, the normal direction between each element of bearing is calculated according to normal intershaft bearing kinetic model
Contact load；If bearing element enters damage field, the method between each element of bearing is calculated according to local damage mathematical model
To contact load；
Step 4), by step 2) five degree of freedom intershaft bearing kinetic model and step 3) obtained in each element of bearing it
Between normal direction contact load, carry out numerical integration in conjunction with variable step quadravalence Runge-Kutta-Fehlberg method, obtain lower a period of time
Carve the position and speed of bearing element；
Step 5), loop iteration step 2) to step 4), until jumping out circulation after reaching simulation time；
Step 6) exports the vibratory response of outer ring acceleration, finally obtains intershaft bearing local damage failure acceleration vibratory response
Time-domain diagram and envelope spectrum.
2. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 1, special
Sign is, in step 1), structural parameters include bearing inner race diameter, outer rollaway nest diameter, rolling element diameter, retainer internal diameter,
Retainer outer diameter rolls body length, rolling element number, retainer width, lesion width and lesion depths；
Material parameter includes the elasticity modulus and Poisson's ratio of bearing inner race, bearing outer ring, rolling element and retainer；
Operating condition includes outside radial load and bearing that the revolving speed of bearing inner race, bearing outer ring revolving speed, bearing inner race are born
Enclose born radial load；
Lubrication parameter includes tetra- lubricant parameters of A, B, C and D in lubricant trailed model μ=(A+Bu) exp (- Cu)+D,
In formula, μ is sliding speed when being u coefficient of friction；
The initial motion state of each bearing element includes the mass center position of bearing inner race, bearing outer ring, retainer and each rolling element
It sets and speed.
3. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 1, special
Sign is, in step 2, five degree of freedom intershaft bearing kinetic model include bearing inner race, rolling element and retainer translation and
The differential equation of motion of the differential equation and bearing outer ring is rotated, specifically:
Bearing inner race, the translation of rolling element and retainer and the rotation differential equation are expressed as follows:
In formula: m is bearing inner race, rolling element or retainer quality, and x is bearing element displacement, and t is the time, and ∑ F is bearing element
Suffered resultant force, wherein the suffered resultant force of bearing element includes normal direction contact load fNWith tangential tractive force fτ；ω is angular speed, and J is
Rotary inertia, ∑ M are resultant moments suffered by bearing element；
The differential equation of motion of bearing outer ring are as follows:
In formula, moFor bearing outer ring quality, yoAnd zoRespectively bearing outer ring mass center Y-axis and Z-direction displacement,WithPoint
Not Wei bearing outer ring mass center Y-axis and Z-direction speed,WithAcceleration for bearing outer ring mass center in Y-axis and Z axis, ∑
FyWith ∑ FzRespectively bearing outer ring resultant force suffered by Y-axis and Z-direction, kyAnd kzRespectively bearing outer ring is in Y-axis and Z
The stiffness coefficient of axis direction, cyAnd czRespectively damped coefficient of the bearing outer ring in Y-axis and Z-direction.
4. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 1, special
Sign is, if having a width on bearing outer ring is wd, depth hdDamage, judge whether rolling element enters the tool of damage field
Body method is:
In local damage coordinate system, rolling element center and ZdAngle between axis is θbd, damage one of the wrapping angle on raceway
Half is θe；Work as θbd< θeWhen, into damage field, conversely, not entering damage field then.
5. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 1, special
Sign is, the specific method of the normal direction contact load between each element of bearing is calculated according to normal intershaft bearing kinetic model
It is:
S1, if the run-off the straight and when skew during operation of rolling element in bearing element, along its length by rolling element
M' circle sheet is divided into microtomy；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, if the contact point is p, is somebody's turn to do when contacting between k-th of circle sheet and bearing other each elements by following formula
P point is relative to the vector r between ferrule central positionpr
rpr=rbr+rpb
Wherein, rbrPosition vector of the body coordinate system center relative to set delineation body coordinate system center is determined for rolling element；rpbFor p
Point determines the position vector at body coordinate system center relative to rolling element；
S4, the deflection δ being calculate by the following formula between k-th of circle sheet and lassok:
δk=± (rpr3-0.5Dr)
Wherein, rpr3Represent rprThird component taken just outside bracket, Dr takes outer rollaway nest straight when slice is contacted with outer rollaway nest
Diameter, when slice is contacted with interior rollaway nest, bracket takes negative, and Dr takes interior rollaway nest diameter；
S5 works as δkWhen > 0, the single circle sheet and raceway contact load, calculation formula are calculated according to Hertz line contact theory are as follows:
Wherein, EeqIt is equivalent elastic modulus, leqIt is effective contact length of rolling element, dx is circle sheet thickness；
S6, will be used for single circle sheet in S5 and the calculation formula of raceway contact load is integrated along its contact length, obtain
Act on the normal direction contact load f on entire rolling elementN；
S7, according to Newton's third law obtain the bearing being in contact respectively with rolling element it is inside and outside circle and retainer suffered by work
Firmly.
6. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 5, special
Sign is, is calculate by the following formula tangential tractive force f suffered by each element of bearingτ:
fτ=μ fN
In formula, μ is traction lubrication friction coefficient.
7. a kind of aero-engine intershaft bearing local damage fault vibration emulation mode according to claim 1, special
Sign is, the specific side of the normal direction contact load between bearing outer ring and each element of bearing is calculated using local damage mathematical model
Method is:
Rolling element is divided into m' circle sheet with microtomy along its length by S1；
S2, judges whether each circle sheet contacts between other each elements with bearing；
S3, when being contacted between k-th of circle sheet and bearing other each elements, if the contact point is p, in contact coordinate system
In, the position vector between p point and m point isLine r between p point and m pointmpWith zkAngle between axis is θR, then raceway
In position θRRadius R (the θ at placeR) it is calculate by the following formula:
R(θR)=ror+hd；
In formula: ror --- the radius of outer rollaway nest, hdIt is θRFunction；
S4, the geometry approach amount between rolling element and local damage are as follows:
S5 calculates the single circle sheet and raceway contact load, calculation formula according to Hertz line contact theory are as follows:
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110532693A (en) * | 2019-08-29 | 2019-12-03 | 西安交通大学 | A kind of aero-engine intershaft bearing wear-out failure vibratory response emulation mode |
| CN117238418A (en) * | 2023-11-10 | 2023-12-15 | 奥谱天成(成都)信息科技有限公司 | Impact damage analysis method and device combining hyperspectral imaging technology with mechanical parameters |
Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103500268A (en) * | 2013-09-06 | 2014-01-08 | 西安交通大学 | High-speed angular contact ball bearing damage fault dynamic analysis method |
| CN103712785A (en) * | 2013-09-12 | 2014-04-09 | 西安交通大学 | Rolling bearing-rotor system damage vibration response quantitative calculation method |
| CN103927414A (en) * | 2014-04-04 | 2014-07-16 | 北京工业大学 | Vibration response simulation analyzing method for rolling bearing with single-point failures |
| CN105224713A (en) * | 2015-07-30 | 2016-01-06 | 西北工业大学 | A kind of derated design method of aeromotor intershaft bearing |
| CN105651515A (en) * | 2016-03-22 | 2016-06-08 | 西北工业大学 | Fault detection method and device for aircraft engine intermediate bearing |
| CN106599505A (en) * | 2016-12-23 | 2017-04-26 | 天津职业技术师范大学 | Optimal oil supply amount calculation model for dual-rotor system |
| CN107704695A (en) * | 2017-10-13 | 2018-02-16 | 北京工业大学 | A kind of full-scale quantitative Diagnosis method of housing washer defect |
| CN108195587A (en) * | 2018-02-12 | 2018-06-22 | 西安交通大学 | A kind of motor rolling Method for Bearing Fault Diagnosis and its diagnostic system |
-
2018
- 2018-09-13 CN CN201811070299.2A patent/CN109145501B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103500268A (en) * | 2013-09-06 | 2014-01-08 | 西安交通大学 | High-speed angular contact ball bearing damage fault dynamic analysis method |
| CN103712785A (en) * | 2013-09-12 | 2014-04-09 | 西安交通大学 | Rolling bearing-rotor system damage vibration response quantitative calculation method |
| CN103927414A (en) * | 2014-04-04 | 2014-07-16 | 北京工业大学 | Vibration response simulation analyzing method for rolling bearing with single-point failures |
| CN105224713A (en) * | 2015-07-30 | 2016-01-06 | 西北工业大学 | A kind of derated design method of aeromotor intershaft bearing |
| CN105651515A (en) * | 2016-03-22 | 2016-06-08 | 西北工业大学 | Fault detection method and device for aircraft engine intermediate bearing |
| CN106599505A (en) * | 2016-12-23 | 2017-04-26 | 天津职业技术师范大学 | Optimal oil supply amount calculation model for dual-rotor system |
| CN107704695A (en) * | 2017-10-13 | 2018-02-16 | 北京工业大学 | A kind of full-scale quantitative Diagnosis method of housing washer defect |
| CN108195587A (en) * | 2018-02-12 | 2018-06-22 | 西安交通大学 | A kind of motor rolling Method for Bearing Fault Diagnosis and its diagnostic system |
Non-Patent Citations (4)
| Title |
|---|
| HU QINGHUA等: ""A 5-DOF Model for Aeroengine Spindle Dual-rotor System Analysis"", 《CHINESE JOURNAL OF AERONAUTICS》 * |
| LINKAI NIU等: ""Dynamic Modeling and Vibration Response Simulation for High Speed Rolling Ball Bearings With Localized Surface Defects in Raceways"", 《JOURNAL OF MANUFACTURING SCIENCE AND ENGINEERING》 * |
| 牛蔺楷等: ""考虑三维运动和相对滑动的滚动球轴承局部表面"", 《机械工程学报》 * |
| 邓四二等: ""高速圆柱滚子轴承保持架动力学特性分析"", 《航空动力学报》 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN110532693A (en) * | 2019-08-29 | 2019-12-03 | 西安交通大学 | A kind of aero-engine intershaft bearing wear-out failure vibratory response emulation mode |
| CN110532693B (en) * | 2019-08-29 | 2021-07-13 | 西安交通大学 | Vibration response simulation method for abrasion fault of intermediate bearing of aircraft engine |
| CN117238418A (en) * | 2023-11-10 | 2023-12-15 | 奥谱天成(成都)信息科技有限公司 | Impact damage analysis method and device combining hyperspectral imaging technology with mechanical parameters |
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