CN107526902A - Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods - Google Patents

Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods Download PDF

Info

Publication number
CN107526902A
CN107526902A CN201710858574.6A CN201710858574A CN107526902A CN 107526902 A CN107526902 A CN 107526902A CN 201710858574 A CN201710858574 A CN 201710858574A CN 107526902 A CN107526902 A CN 107526902A
Authority
CN
China
Prior art keywords
bearing
rolling bearing
represent
rotor
function
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.)
Pending
Application number
CN201710858574.6A
Other languages
Chinese (zh)
Inventor
汪爱明
孟国营
夏云
毕玉洁
程晓涵
杨杰
时剑文
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
China University of Mining and Technology CUMT
China University of Mining and Technology Beijing CUMTB
Original Assignee
China University of Mining and Technology Beijing CUMTB
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by China University of Mining and Technology Beijing CUMTB filed Critical China University of Mining and Technology Beijing CUMTB
Priority to CN201710858574.6A priority Critical patent/CN107526902A/en
Publication of CN107526902A publication Critical patent/CN107526902A/en
Pending legal-status Critical Current

Links

Classifications

    • G—PHYSICS
    • G06—COMPUTING; CALCULATING OR COUNTING
    • G06F—ELECTRIC DIGITAL DATA PROCESSING
    • G06F30/00—Computer-aided design [CAD]
    • G06F30/10—Geometric CAD
    • G06F30/17—Mechanical parametric or variational design
    • 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
    • G06F2119/06—Power analysis or power optimisation

Abstract

The invention discloses the rolling bearing rigidity and damped coefficient ONLINE RECOGNITION that running rotor based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods, is realized using the unbalance response of 4 measuring points in rotating shaft.Technical scheme includes：The unbalance response data of 4 measuring points in the rotating shaft including bearing measuring point to be measured are obtained, to the unbalance response data nondimensionalization of 4 measuring points, and frequency domain is transformed to, obtains 4 measuring point vectors；Utilize 4 measuring point vector calculation bearing vector coefficients；Bearing rigidity and damped coefficient is calculated according to bearing vector coefficient.

Description

Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods
Technical field
Rotor dynamics field of the present invention, in particular it relates to a kind of single-deck twin spans rolling bearing rotor-support-foundation system bearing module Recognition methods.
Background technology
Rotating machinery widely uses in national economy all trades and professions, and its core component is rotor.Critical turn is predicted exactly The rotor dynamics behavior such as speed, dynamic response, margin of stability, being capable of the reliable and stable operation of effective guarantee rotating machinery and production peace Entirely.It is one of key issue of rotor-bearing system dynamics analysis to establish a rational mechanical model of comparison.If in model Some parameters and actual value gap are larger, and dynamic analysis result will be caused insincere.Rotor bearing under operating condition is firm Degree, the determination of damped coefficient are exactly a parameter for being difficult to determine.Although laboratory static measurement values or various numbers can be used Value calculating method determines, but due to in-site installation after, the operating mode of bearing has many differences with laboratory or design conditions, and static state is surveyed Value and numerical computation differ larger with actual value, cause the critical speed that calculates or unbalance response etc. with measured value often It is inconsistent.It can be said that up to the present, the determination of operating condition lower bearing rigidity, damped coefficient be rotor dynamics technology and A difficult point in engineering design.
4 measuring points need to be only utilized in rotating shaft based on continuous dynamic (dynamical) Rotor System with Rolling Bearings coefficient recognition methods Unbalance response data, the bearing rigidity that can monitor running rotor on-line is damped, there is important theory significance and engineering valency Value.
The content of the invention
It is an object of the invention to provide based on continuous dynamic (dynamical) Rotor System with Rolling Bearings bearing rigidity and damped coefficient Recognition methods, by the unbalance response data of 4 measuring points in rotating shaft, realize the bearing rigidity with regard to running rotor can be monitored on-line Damped coefficient, adequately predict that the dynamic behavior of rotors provides technical support.
The technical scheme is that：
1. a kind of bearing rigidity based on continuous dynamic (dynamical) Rotor System with Rolling Bearings, damped coefficient recognition methods, its It is characterised by, this method comprises the following steps：
(1) the unbalance response data of 4 measuring points in the rotating shaft including bearing measuring point are obtained；
(2) to the unbalance response data nondimensionalization of 4 measuring points, and transform to frequency domain, obtain 4 measuring points to Amount；
(3) rolling bearing coefficient vector is calculated；
(4) the rolling bearing coefficient vector is utilized, obtains bearing rigidity and damping.
2. the method as described in claim 1, it is characterised in that the unbalance response data of 4 measuring points are：
In the unbalance response date expression of 4 measuring points, zs4Represent position of the bearing in rotating shaft, zs1、 zs2、zs3The position of other 3 measuring points of rotating shaft is represented, w represents axis of rotation frequency, β1、β2、β3、β4Represent 4 measuring point imbalances The phase of response.
3. the method as described in claim 1, it is characterised in that 4 measuring point vectors are：
In 4 measuring point vector expressions, L is shaft length,
4. the method as described in claim 1, it is characterised in that rotor-support-foundation system rolling bearing coefficient vector calculation formula For：
In the rotor-support-foundation system rolling bearing coefficient vector calculation formula, E represents rotating shaft modulus of elasticity, and I represents that rotating shaft is shaken Dynamic inertia, ksxx=kxx+i·w·cxx、ksyy=kyy+i·w·cyy, kxx、、kyyRepresent bearing rigidity coefficient, cxx、cyyRepresent Left bearing damped coefficient,
Gyn11=Gu(qs1,q1) gyn21=Gu(qs2,q1) gyn31=Gu(qs3,q1)
Gyn12=Gu(qs1,q2), gyn22=Gu(qs2,q2), gyn32=Gu(qs3,q2),
Gyn13=Gu(qs1,q3) gyn23=Gu(qs2,q3) gyn33=Gu(qs3,q3)
Gu(q,qi)、Gv(q,qi) For Green's function,z1Represent coordinate of the left bearing in z-axis, z2Represent left bearing in z axles On coordinate, z3Represent coordinate of the eccentric rotating disk in z-axis.
5. method as claimed in claim 4, it is characterised in that for Euler-Bernoulli rotator models, Ge Linhan Number Gu(q,qi)、Gv(q,qi) be：
The Green's function Gu(q,qi)、Gv(q,qi) in expression formula, sjFor equation s4- k=0 root, i values 1,2,3, u (q-qi) it is Heaviside function.
6. method as claimed in claim 4, it is characterised in that for Rayleigh rotator models, Green's function Gu(q, qi)、Gv(q,qi) be：
The Green's function Gu(q,qi)、Gv(q,qi) in,
f1(s)=s7+2L1s5+(L1 2-P2-K)s3-KL1S,
f2(s)=s6+2L1S4+(L1 2-P2-K)s2-KL1,
F (s)=s8+2L1·s6+(-2K+L1 2-P2)s4-2L1K·s2+K2,
sj(j=1-8) it is the root of Equation f (s)=0, u (q-qi) it is Heaviside function,
7. the method as described in claim 1, it is characterised in that rolling bearing rigidity, damping are respectively： kxx=real (ksxx)、kyy=real (ksyy)、cxx=imag (ksxx)/ω、cyy=imag (ksyy)/ω；
In the rolling bearing rigidity, damped coefficient expression formula, real () is represented to take real, and imag () is represented The imaginary part of plural number.
Beneficial effects of the present invention：
Patent methods described of the present invention is directed to single-deck twin spans Rotor System with Rolling Bearings, using 4 measuring points in rotating shaft not Equilibrium response data, monitor the bearing rigidity and damped coefficient of running rotor on-line, adequately predict the power of rotors Scholarship and moral conduct has the characteristics that easily implementation, cost are low to provide technical support.
Brief description of the drawings
Fig. 1 is based on continuous dynamic (dynamical) rotor unbalance value recognition methods schematic diagram；
Fig. 2 is single-deck twin spans rotor structure schematic diagram.
Embodiment
Derivation of the present invention is described further with reference to the accompanying drawings and detailed description.
(1) it is respectively zs to set 4 point positions1、zs2、zs3、zs4, nondimensionalization position is respectively qs1、qs2、 qs3、 qs4, surveying expression formula of the unbalanced data in time domain is：
Nondimensionalization expression formula of 4 eyeball unbalanced datas in frequency domain be：
(2) according to the continuous kinetic theory of rotor unbalance, then have：
In formula,
k1.xx、k1.xy、k1.yx、k1.yyRepresent left bearing stiffness coefficient, c1.xx、c1.xy、c1.yx、c1.yyRepresent left bearing damping Coefficient, k2.xx、k2.xy、k2.yx、k2.yyRepresent right bearing stiffness coefficient, c2.xx、c2.xy、c2.yx、 c2.yyRepresent right bearing damping system Number, mdRepresent the quality of eccentric rotating disk, w represents the rotational frequency of rotating shaft, and e, α represent the eccentric distance and partially of eccentric rotating disk respectively Heart angle, Gv(q,qi) it is Green's function, L represents shaft length, Y1、Y2、Y3、X1、X2、X3Represent left bearing, eccentric rotating disk, the right side Dimensionless unbalance response of the bearing on x directions, y directions in frequency domain.
NoteThen have：
Note
Gxn11=Gv(qs1,q1) gxn21=Gv(qs2,q1) gxn31=Gv(qs3,q1)
Gxn12=Gv(qs1,q2), gxn22=Gv(qs2,q2), gxn32=Gv(qs3,q2)；
Gxn13=Gv(qs1,q3) gxn23=Gv(qs2,q3) gxn33=Gv(qs3,q3)
Gyn11=Gu(qs1,q1) gyn21=Gu(qs2,q1) gyn31=Gu(qs3,q1)
Gyn12=Gu(qs1,q2), gyn22=Gu(qs2,q2), gyn32=Gu(qs3,q2)
Gyn13=Gu(qs1,q3) gyn23=Gu(qs2,q3) gyn33=Gu(qs3,q3)
Simultaneous formula (1)~(6), solve Y (qs4)、X(qs4), it can obtain after abbreviation
It can be obtained by formula (7) and (8)：
In formula (8) and (10), direct measurement parameter has X (qs1)、X(qs2)、X(qs3)、X(qs4)、Y(qs1)、Y(qs2)、 Y(qs3)、Y(qs4), by the direct calculating parameter of model have gxn11, gxn12, gxn13, gxn21, gxn22, gxn23, gxn31, gxn32、gxn33、gyn11、gyn12、gyn13、gyn21、gyn22、gyn23、gyn31、gyn32、 gyn33。
(3) so rolling bearing rigidity, damping are respectively：
kxx=real (ksxx)、kyy=real (ksyy)、cxx=imag (ksxx)/ω、cyy=imag (ksyy)/ω；
In the rolling bearing rigidity, damped coefficient expression formula, real () is represented to take real, and imag () is represented The imaginary part of plural number.

Claims (7)

  1. A kind of 1. bearing module recognition methods based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system, it is characterised in that the party Method comprises the following steps：
    (1) the unbalance response data of 4 measuring points in the rotating shaft including bearing measuring point are obtained；
    (2) to the unbalance response data nondimensionalization of 4 measuring points, and frequency domain is transformed to, obtains 4 measuring point vectors；
    (3) rolling bearing coefficient vector is calculated；
    (4) the rolling bearing coefficient vector is utilized, obtains bearing rigidity and damping.
  2. 2. the method as described in claim 1, it is characterised in that the unbalance response data of 4 measuring points are：
    In the unbalance response date expression of 4 measuring points, zs4Represent position of the bearing in rotating shaft, zs1、zs2、zs3Table Show the position of other 3 measuring points of rotating shaft, w represents axis of rotation frequency, β1、β2、β3、β4Represent the phase of 4 measuring point unbalance responses Position.
  3. 3. the method as described in claim 1, it is characterised in that 4 measuring point vectors are：
    In 4 measuring point vector expressions, L is shaft length,
  4. 4. the method as described in claim 1, it is characterised in that rotor-support-foundation system rolling bearing coefficient vector calculation formula is：
    ksxx=-[EI (X (qs3)·gxn12·gxn23-X(qs3)·gxn13·gxn22-X(qs2)·gxn12· gxn33+X(qs2)·gxn13·gxn32+X(qs1)·gxn22·gxn33-X(qs1)·gxn23·gxn32)]/[L3·X (qs4)·(gxn11·gxn22·gxn33-gxn11·gxn23·gxn32-gxn12·gxn21·gxn33+gxn12· gxn23·gxn31+gxn13·gxn21·gxn32-gxn13·gxn22·gxn31)]；
    In the rotor-support-foundation system rolling bearing coefficient vector calculation formula, E represents rotating shaft modulus of elasticity, and I represents that shaft vibration is used to Amount, ksxx=kxx+i·w·cxx、ksyy=kyy+i·w·cyy, kxx、、kyyRepresent bearing rigidity coefficient, cxx、cyyRepresent left axle Hold damped coefficient,
    Gu(q,qi)、Gv(q,qi) it is Green Function,z1Represent coordinate of the left bearing in z-axis, z2Represent seat of the left bearing on z axles Mark, z3Represent coordinate of the eccentric rotating disk in z-axis.
  5. 5. method as claimed in claim 4, it is characterised in that for Euler-Bernoulli rotator models, Green's function Gu (q,qi)、Gv(q,qi) be：
    The Green's function Gu(q,qi)、Gv(q,qi) in expression formula, sjFor equation s4- k=0 root, i values 1,2,3, u (q-qi) For Heaviside function.
  6. 6. method as claimed in claim 4, it is characterised in that for Rayleigh rotator models, Green's function Gu(q,qi)、 Gv(q,qi) be：
    The Green's function Gu(q,qi)、Gv(q,qi) in,
    f1(s)=s7+2L1s5+(L1 2-P2-K)s3-KL1S,
    f2(s)=s6+2L1S4+(L1 2-P2-K)s2-KL1,
    F (s)=s8+2L1·s6+(-2K+L1 2-P2)s4-2L1K·s2+K2,
    sj(j=1-8) it is the root of Equation f (s)=0, u (q-qi) it is Heaviside function,
  7. 7. the method as described in claim 1, it is characterised in that rolling bearing rigidity, damping are respectively：kxx=real (ksxx)、 kyy=real (ksyy)、cxx=imag (ksxx)/ω、cyy=imag (ksyy)/ω；
    In the rolling bearing rigidity, damped coefficient expression formula, real () represents to take real, and imag () represents plural number Imaginary part.
CN201710858574.6A 2017-09-20 2017-09-20 Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods Pending CN107526902A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201710858574.6A CN107526902A (en) 2017-09-20 2017-09-20 Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201710858574.6A CN107526902A (en) 2017-09-20 2017-09-20 Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods

Publications (1)

Publication Number Publication Date
CN107526902A true CN107526902A (en) 2017-12-29

Family

ID=60737068

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201710858574.6A Pending CN107526902A (en) 2017-09-20 2017-09-20 Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods

Country Status (1)

Country Link
CN (1) CN107526902A (en)

Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105865783A (en) * 2016-03-23 2016-08-17 湖南大学 Method for measuring characteristics of sliding bearing film

Patent Citations (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN105865783A (en) * 2016-03-23 2016-08-17 湖南大学 Method for measuring characteristics of sliding bearing film

Non-Patent Citations (1)

* Cited by examiner, † Cited by third party
Title
AIMINGWANG等: "Dynamic analysis and numerical experiments for balancing of the continuous single-disc and single-span rotor-bearing system", 《MECHANICAL SYSTEMS AND SIGNAL PROCESSING》 *

Similar Documents

Publication Publication Date Title
Huang et al. The application of ball-type balancers for radial vibration reduction of high-speed optic disk drives
Saleem et al. Detection of unbalance in rotating machines using shaft deflection measurement during its operation
Ma et al. Numerical and experimental analysis of the first-and second-mode instability in a rotor-bearing system
Meng et al. An investigation on dynamic characteristics of a gas turbine rotor using an improved transfer matrix method
Zhang et al. Dynamic analysis of composite rod fastening rotor system considering multiple parameter influence
Liu et al. Study on the dynamic problems of double-disk rotor system supported by deep groove ball bearing
Tiwari Conditioning of regression matrices for simultaneous estimation of the residual unbalance and bearing dynamic parameters
Yue et al. Unbalance identification of speed-variant rotary machinery without phase angle measurement
Al Abbood A new mathematical analysis of two–plane balancing for long rotors without phase data
CN107526902A (en) Based on continuous dynamic (dynamical) rolling bearing rotor-support-foundation system bearing module recognition methods
Bingang et al. A new practical modal method for rotor balancing
CN116256173A (en) Bearing stress state measuring method and related device based on resonance attenuation method
Zheng et al. Research on dynamic balancing simulation of rotary shaft based on ADAMS
CN109847952B (en) Dynamic balance method of double-shaft precision centrifuge turntable based on driving current
Lavrenko et al. Determination of dynamic characteristics of the centrifuge shaft
Sui et al. Laser-based measurement for micro-unbalance of cylindrical rollers of the high-speed precision rolling bearings
CN107748810A (en) A kind of rotor unbalance responds continuous dynamics calculation method
Zhang et al. A two-step identification method for crack parameter identification of train axles
Montoya Santiyanes et al. Oversampled Modal Approach of a Turbocharger Rotor from the Experimental Lateral Vibrations.
Luo et al. Stability analysis of nonlinear stiffness rotor-bearing system with pedestal looseness fault
Ding et al. A linear regression model for the identification of unbalance changes in rotating machines
Gong et al. Analysis on vibration response of bearing coupling faults in rotor-bearing system
Zhang et al. Research on the verification method of the rotor dynamics model of the locomotive turbocharger
Harish Chandra et al. Damping identification in rotors from run-up beat responses using Hilbert transforms
Yue et al. Harmonic Response Analysis of a Dual-Rotor System with Mass Unbalance

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
WD01 Invention patent application deemed withdrawn after publication

Application publication date: 20171229

WD01 Invention patent application deemed withdrawn after publication