CN108509661A - A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient - Google Patents
A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient Download PDFInfo
- Publication number
- CN108509661A CN108509661A CN201710099723.5A CN201710099723A CN108509661A CN 108509661 A CN108509661 A CN 108509661A CN 201710099723 A CN201710099723 A CN 201710099723A CN 108509661 A CN108509661 A CN 108509661A
- Authority
- CN
- China
- Prior art keywords
- shafting
- counterweight
- bearing
- parameter
- mathematical model
- 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
Links
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
Landscapes
- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Sliding-Contact Bearings (AREA)
Abstract
A kind of shafting dynamic balance disclosed in the present application aggravates to influence the emulated computation method and device of coefficient, establishes the kinetic model of shafting, which considers influence of the sliding bearing dynamic stiffness of shafting to entire shafting dynamic stiffness.Dynamics Simulation Analysis is carried out by the dynamics data model to foundation, shafting dynamic balance is calculated and aggravates to influence coefficient.Shafting dynamic balance is obtained relative to test method to aggravate to influence coefficient, the application can obtain more comprehensive shafting dynamic balance and aggravate to influence coefficient, and cost is relatively low, and not have security risk by emulation technology.
Description
Technical field
This application involves simulation technical field, aggravate to influence the imitative of coefficient more specifically to a kind of shafting dynamic balance
True computational methods and device.
Background technology
The revolving body of motor and steam turbine generator is made of multiple rotors mostly, referred to as shafting.In ideal conditions
With when not rotating when shafting rotates, the pressure to bearing generation is the same, and such shafting is the shafting of balance.But in engineering
Various shaftings, due to the error that generates during material is uneven or blank defect, processing and assembly, or even just have when design non-
The many factors such as symmetrical geometry so that when rotated, the centrifugal intertia force that each small particle generates thereon is or not shafting
It can cancel out each other, centrifugal intertia force is applied to mechanically by bearing, causes to vibrate, and produces noise, accelerates bearing wear, contracting
Short mechanical life, sexual behavior can be damaged when serious therefore.The dynamic balancing of shafting be on two rectifying planes of shafting simultaneously
It is corrected balance, to ensure the residual unbalance, after correcting, in dynamic in the prescribed limit in allowable amount of unbalance.
In shaft into before action balance, needing the exacerbation for first understanding shafting to influence coefficient.In a certain exacerbation of shafting
Plane adds Unit Weight, when a certain rotating speed, the variation for causing some direction of certain bearing to vibrate, referred to as in the rotating speed this
Plane, which aggravates the exacerbation on this direction, influences coefficient.But existing shafting dynamic balance aggravates to influence the calculation of coefficient
That the multiple start and stop of unit are needed by test method, destroying for times vacuum repeatedly establishes vacuum, multiple counterweight could obtain compared with
Comprehensively to influence coefficient, cost is higher, and security risk is higher.
Invention content
In view of this, the application proposes that a kind of shafting dynamic balance aggravates to influence the emulated computation method and device of coefficient, it is intended to
By the technology of emulation, obtains more comprehensive shafting dynamic balance and aggravate to influence coefficient, realization reduces cost, avoids security risk
Purpose.
To achieve the goals above, it is proposed that scheme it is as follows：
A kind of shafting dynamic balance aggravates the emulated computation method of influence coefficient, including：
The dynamics mathematical model of shafting is established, the dynamics mathematical model is：
Wherein, [M1] be the shafting mass matrix, [K1] be the shafting stiffness matrix, { Q1And { Q2It is wide
Adopted power, { U1It is motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] it is the shafting
Turn round matrix, c11、c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the bearing
Stiffness parameters,
Dynamics Simulation Analysis is carried out to the dynamics mathematical model, the shafting dynamic balance is calculated and aggravates to influence system
Number.
Preferably, it is described establish the dynamics mathematical model of shafting before, further include：Calculate the damping parameter c11、
c12、c21And c22, and calculate the stiffness parameters k11、k12、k21And k22。
Preferably, described to calculate the damping parameter c11、c12、c21And c22, and calculate the stiffness parameters k11、k12、
k21And k22Including for：
Receive the structural parameters and work operating parameter of the bearing；
According to the structural parameters of the bearing and work operating parameter, and combine Lubrication Film Thickness equation, Reynolds equation,
The damping parameter c is calculated in energy equation, temperature-viscosity equation and torque equilibrium equation11、c12、c21And c22, Yi Jiji
Calculation obtains the stiffness parameters k11、k12、k21And k22
Export the damping parameter c11、c12、c21And c22And the stiffness parameters k11、k12、k21And k22。
Preferably, described that Dynamics Simulation Analysis is carried out to the dynamics mathematical model, calculate the shafting dynamic balance
Aggravating, which influences coefficient, includes：
It determines that the rotating speed of the shafting is N, and determines the simple harmonic quantity generated when the first counterweight face θ degree counterweight W of the shafting
Centrifugal force Q；
Harmonic excitation analysis is carried out to the dynamics mathematical model, obtains the vibratory response of the shafting, the vibration
Response includes vibration amplitude and vibration phase；
According to the vibratory response, it is N to calculate the shafting in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W
Influence coefficient.
Preferably, described that Dynamics Simulation Analysis is carried out to the dynamics mathematical model, calculate the shafting dynamic balance
Aggravating, which influences coefficient, includes：
It determines that the rotating speed of the shafting is N, and determines the first counterweight face θ degree counterweights W of the shafting；
To the dynamics mathematical model into action balance simulation calculation, the vibratory response of the shafting is obtained, it is described to shake
Dynamic response includes vibration amplitude and vibration phase；
According to the vibratory response, it is N to calculate the shafting in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W
Influence coefficient.
A kind of shafting dynamic balance aggravates the simulation calculation device of influence coefficient, including：
Shafting model module, the dynamics mathematical model for establishing shafting, the dynamics mathematical model are：
Wherein, [M1] be the shafting mass matrix, [K1] be the shafting stiffness matrix, { Q1And { Q2It is wide
Adopted power, { U1It is motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] it is the shafting
Turn round matrix, c11、c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the bearing
Stiffness parameters,
It is dynamic flat to calculate the shafting for carrying out Dynamics Simulation Analysis to the dynamics mathematical model for analysis module
Weighing apparatus aggravates to influence coefficient.
Preferably, described device further includes：
Bearing rigidity module, for it is described establish the dynamics mathematical model of shafting before, calculate the damping parameter c11、
c12、c21And c22, and calculate the stiffness parameters k11、k12、k21And k22。
Preferably, the bearing rigidity module includes：
Parameter receiving module, the structural parameters for receiving the bearing and work operating parameter；
Parameter processing module for the structural parameters and work operating parameter according to the bearing, and combines bearing film
The damping parameter c is calculated in thickness equation, Reynolds equation, energy equation, temperature-viscosity equation and torque equilibrium equation11、
c12、c21And c22, and the stiffness parameters k is calculated11、k12、k21And k22；
Parameter output module, for exporting the damping parameter c11、c12、c21And c22And the stiffness parameters k11、
k12、k21And k22。
Preferably, the analysis module includes：
First parameter determination module for determining that the rotating speed of the shafting is N, and determines the first counterweight face of the shafting
The simple harmonic quantity centrifugal force Q generated when θ degree counterweight W；
First analysis module obtains the shafting for carrying out harmonic excitation analysis to the dynamics mathematical model
Vibratory response, the vibratory response include vibration amplitude and vibration phase；
First computing module is N for according to the vibratory response, calculating the shafting in rotating speed, and the first counterweight
Exacerbation when the θ degree counterweight W of face influences coefficient.
Preferably, the analysis module includes：
Second parameter determination module for determining that the rotating speed of the shafting is N, and determines the first counterweight face of the shafting
θ degree counterweights W；
Second analysis module, for, into action balance simulation calculation, obtaining the shafting to the dynamics mathematical model
Vibratory response, the vibratory response includes vibration amplitude and vibration phase；
Second computing module is N for according to the vibratory response, calculating the shafting in rotating speed, and the first counterweight
Exacerbation when the θ degree counterweight W of face influences coefficient.
It can be seen from the above technical scheme that a kind of shafting dynamic balance disclosed in the present application aggravates to influence the emulation of coefficient
Computational methods and device establish the kinetic model of shafting.Dynamics simulation is carried out by the dynamics data model to foundation
Analysis is calculated shafting dynamic balance and aggravates to influence coefficient.Shafting dynamic balance is obtained relative to test method to aggravate to influence coefficient,
The application can be obtained more comprehensive shafting dynamic balance and aggravate to influence coefficient, and cost is relatively low, and not had by emulation technology
There is security risk.
Description of the drawings
In order to illustrate the technical solutions in the embodiments of the present application or in the prior art more clearly, to embodiment or will show below
There is attached drawing needed in technology description to be briefly described, it should be apparent that, the accompanying drawings in the following description is only this
Some embodiments of application for those of ordinary skill in the art without creative efforts, can be with
Obtain other attached drawings according to these attached drawings.
Fig. 1 is a kind of flow chart of the emulated computation method of shafting dynamic balance exacerbation influence coefficient disclosed in the present embodiment；
Fig. 2 is the cross section axle center coordinate schematic diagram of armature spindle disclosed in the present embodiment；
Fig. 3 is that another shafting dynamic balance disclosed in the present embodiment aggravates to influence the flow of the emulated computation method of coefficient
Figure；
Fig. 4 is a kind of simplified diagram of tilting-pad bearing disclosed in the present embodiment；
Fig. 5 is a kind of flow chart calculating bearing rigidity parameter and damping parameter method disclosed in the present embodiment；
Fig. 6 is a kind of schematic diagram of the simulation calculation device of shafting dynamic balance exacerbation influence coefficient disclosed in the present embodiment；
Fig. 7 is that another shafting dynamic balance disclosed in the present embodiment aggravates to influence the signal of the simulation calculation device of coefficient
Figure.
Specific implementation mode
Below in conjunction with the attached drawing in the embodiment of the present application, technical solutions in the embodiments of the present application carries out clear, complete
Site preparation describes, it is clear that described embodiments are only a part of embodiments of the present application, instead of all the embodiments.It is based on
Embodiment in the application, it is obtained by those of ordinary skill in the art without making creative efforts every other
Embodiment shall fall in the protection scope of this application.
The present embodiment discloses a kind of emulated computation method of shafting dynamic balance exacerbation influence coefficient, shown in Figure 1, packet
It includes：
Step S11：Establish the dynamics mathematical model of shafting.
Dynamics mathematical model is：
Wherein, [M1] be shafting mass matrix, [K1] be shafting stiffness matrix, { Q1And { Q2It is generalized force, { U1}
For motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] be the shafting revolution matrix,
c11、c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the stiffness parameters of bearing,
It supports the rigidity of the bearing of shafting and damps the critical speed that can all influence shafting, therefore, establishing the dynamic of shafting
When mechanical model, the stiffness parameters of bearing and damping parameter are taken into account so that the kinetic model of the shafting of foundation is more
Accurately.
Using bearing axis as the fixed coordinate system OXYZ of Z axis, any one cross section axle center o of armature spindleiCoordinate is
(xi, yi), as shown in Figure 2；Corner of any one cross section of armature spindle in XOZ planes is θyi, armature spindle it is any one
Corner of a cross section in YOZ planes is θxi, then any one cross section displacement of armature spindle indicates with two vectors：
Rotor is divided into N number of node, N-1 shaft part, the motion vector of cross section combines composition at each node
{U1And { U2}：
{U1}=[x1,θy1,x2,θy2,…,xN,θyN]T
{U2}=[y1,-θx1,y2,-θx2,…,yN,-θxN]T
It should be noted that ideally, the axle center of armature spindle is overlapped with bearing axis, and therefore, the seat of cross section
Mark is all (0,0), and cross section and the angle of XOZ planes or YOZ planes are all 90 °, and corner is all zero, i.e. cross section and XOZ is flat
On the basis of 90 °, it is corner that opposite 90 °, which change angle, for face or YOZ planes.
Step S12：Dynamics Simulation Analysis is carried out to dynamics mathematical model, shafting dynamic balance is calculated and aggravates to influence system
Number.
Counterweight is carried out in a certain exacerbation position, simulation analysis acquisition is then carried out by the dynamics mathematical model to foundation
Response of the kinetic model to counterweight, and then calculate the influence coefficient under the counterweight.
A kind of emulated computation method of shafting dynamic balance exacerbation influence coefficient, first establishes the dynamic of shafting disclosed in the present embodiment
Then mechanical model carries out Dynamics Simulation Analysis by the dynamics data model to foundation, shafting dynamic balance is calculated
It aggravates to influence coefficient.Shafting dynamic balance is obtained relative to test method to aggravate to influence coefficient, the application, can be with by emulation technology
It obtains more comprehensive shafting dynamic balance to aggravate to influence coefficient, and cost is relatively low, and there is no security risk
The present embodiment discloses another shafting dynamic balance and aggravates to influence the emulated computation method of coefficient, shown in Figure 3, institute
Before the method for stating establishes the dynamics mathematical model of shafting, further include：
Step S10：Calculate the damping parameter c of bearing11、c12、c21And c22, and calculate the stiffness parameters k of bearing11、k12、
k21And k22。
Specifically, according to the structural parameters of bearing and work operating parameter, and combine Lubrication Film Thickness equation, Reynolds side
Bearing damp parameter c is calculated in journey, energy equation, temperature-viscosity equation and torque equilibrium equation11、c12、c21And c22, and
Stiffness parameters k is calculated11、k12、k21And k22。
For example, calculating the stiffness parameters and damping parameter of tilting-pad bearing, Fig. 4 is the simplified diagram of tilting-pad bearing,
Branch null circle 1, axle journal 2, fulcrum 3, tile fragment 4, O-bearing centre；Oj- journal centre；Oi,Oi'-tile fragment swings forward and backward Inner arc
Center；Rz- fulcrum radius of circle；R-axle journal radius；R-tile fragment inner circle radius；E-bearing eccentricity；α-tile fragment subtended angle；βi—
Position of the fulcrum angle；The adjacent watt of span angle γ-；δi- tile fragment pivot angle；θ-bearing the attitude angle；Used load on W-bearing；ω—
Axle journal angular speed；Zi- tile fragment simplifies fulcrum, and corresponding subscript number (i=1,2,3) is tile fragment number.
According to the structural parameters of bearing and work operating parameter, and combine Lubrication Film Thickness equation, Reynolds equation, energy
Bearing damp parameter c is calculated in equation, temperature-viscosity equation and torque equilibrium equation11、c12、c21And c22, and calculate
To stiffness parameters k11、k12、k21And k22Detailed process it is as shown in Figure 5：
Step S21：The structural parameters and work operating parameter of receiving bearing.
Structural parameters include bearing radius R, axle journal radius r, fulcrum radius of circle r ', position of the fulcrum angle betai, bearing width B,
Circumferential angular position of the i-th piece of watt of two edge along vertical initial pointi1And φi2.The operating parameter that works includes oil film temperature tl, bearing
Temperature t on watt body surface faces.Angular velocity of rotation ω etc..
Step S22：Finite Difference Meshes division is carried out to Pressure solution region, and determines difference gridding node coordinate and has
The first nodal information of limit.This is a kind of finite element method, is the prior art, therefore, the application repeats no more.
Step S23:Set one group of the bearing attitude angle θ, the pivot angle δ of i-th piece of bearing shelli, the occurrence of bearing eccentric distance e, root
According to Lubrication Film Thickness equation, oil film thickness h is calculated.
Lubrication Film Thickness equation obtains tilting-pad bearing according to the structural parameters of tilting-pad bearing and is not considering tile fragment bullet
Dimensionless oil film thickness h when property or thermoelastic deformation：
H=c- (c-c') cos (βi-φi)+ecos(φi-θ)+rδisin(βi-φi)
Wherein, radius clearance c=R-r, R are bearing radius, and r is axle journal radius, turn to match gap c'=r'-r, r ' is fulcrum
Radius of circle, φiFor the circumferential angular coordinate of the i-th piece of watt of upper edge vertical initial point, βiFor position of the fulcrum angle, θ is the bearing attitude angle, δiFor
The pivot angle of i-th piece of bearing shell, e are bearing eccentricity.
Step S24：One group of temperature field is set, each node viscosity is calculated.Temperature-viscosity method only has one variable of temperature, often
A temperature corresponds to only one viscosity number.
Temperature-viscosity equation can be that an experiment is bent for a certain specific temperature of lubricating oil and the relationship of viscosity
Line can also be the approximate equation of a fitting, need determines according to actual conditions.
Step S25：Solve Reynolds equation.By Reynolds equation finite difference, pressure distribution is solved by Renolds boundary condition condition.
Reynolds equation, it is assumed that lubricating oil is incompressible Newtonian fluid, stable state Laminar Flow and without sliding, and inertia force is neglected
Slightly disregard, the physical parameter of lubricating oil is constant.Then for tilting-pad bearing, each tile fragment oil film pressure distribution can be by following form
Reynolds equation indicate：
Wherein, p is oil film pressure, and ω is angular velocity of rotation, and μ is film viscosity, φiFor i block watt upper edge vertical initial points
Circumferential angular coordinate, z are bearing axial coordinates, and t is time variable.
Step S26：According to the pressure distribution solved in step S25, and the temperature t on the bearing liner body surface face of inputs
Deng doing difference to energy equation, find out oil film Temperature Distribution.
Energy equation indicates oil film energy equation in the form of oil film pressure：
Wherein, tlFor oil film temperature, ρ is lubrication oil density, cvFor lubricating oil specific heat, ktFor bearing fluid-solid interface
The heat transfer coefficient at place, tsFor the temperature on bearing liner body surface face.
Step S27：Judge whether oil film Temperature Distribution meets convergent requirement.Specifically, the oil film temperature that step S26 is found out
The oil film temperature field that degree is distributed in setting compares, and step S28 is carried out if meeting precision, if being unsatisfactory for required precision,
Step S24 to step S26 is executed using the oil film Temperature Distribution found out as the temperature field of new settings, until the oil film temperature found out
Distribution meets required precision.
Step S28：According to the other parameters of the pressure distribution and input that are found out when meeting precision, torque is solved.It is ideal
State torque is zero, and S29 is entered step if the torque solved meets required precision, otherwise, adjustment tile fragment pivot angle δiValue, weight
Multiple step S23 to step S27, until the torque of solution meets required precision.
Torque equilibrium equation, when disregarding each section frictional resistance and tile fragment dead weight causes torque, the equalising torque of tile fragment
Equation is：
B is bearing width, φi1And φi2Circumferential angular coordinate of respectively the i-th piece of watt of two edge along vertical initial point.
Step S29:According to the structural parameters of the bearing of input, oil film forced area is acquired, is asked in conjunction with when meeting precision
The pressure distribution gone out, calculates load capacity, compared with preset rotor weight, S210 is entered step if meeting the requirements,
Otherwise, bearing attitude angle θ is adjusted, repeats step S23 to step S27 until meeting the requirements.
Step S210：The microvariations of fetch bit shifting and speed respectively, calculate the damping parameter c of bearing11、c12、c21And c22, with
And stiffness parameters k11、k12、k21And k22。
Step S211：C is calculated in output11、c12、c21、c22、k11、k12、k21And k22。
Dynamics Simulation Analysis is carried out to the dynamics mathematical model, the shafting dynamic balance is calculated and aggravates to influence system
Number.Concrete methods of realizing is as follows：
Using ANSYS software implementation methods：
Step S31：It is generated when determining that the shafting rotating speed is N, and determining the first counterweight face θ degree counterweight W of the shafting
Simple harmonic quantity centrifugal force Q.
Rotating speed Interval Discrete is divided into different segments and calculated by discrete speeds section, as needed the rotating speed analyzed to be
0 --- Nrpm, using Δ n as frequency interval, i.e. Ni=i Δs n, i=1,2,3 ..., determine different rotating speeds NiUnder shafting model；
Emulation is in W kilograms of 0 degree of the faces A plus counterweight, the simple harmonic quantity centrifugal force generated by counterweight under applying the rotating speed in the faces A；
Step S32：Harmonic excitation analysis is carried out to dynamics mathematical model, obtains the vibratory response of the shafting, it is described
Vibratory response includes vibration amplitude and vibration phase.
Shaft dynamics mathematical model carries out harmonic excitation analysis, you can obtains under the rotating speed, 0 degree of the faces A plus matches
The vibratory response of shafting when W kilograms heavy.
Step S33：According to vibratory response, it is N to calculate shafting in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W
Influence coefficient.
To different rotating speeds NiUnder shafting model carry out simulation analysis, obtain different rotating speeds NiUnder, in 0 degree of the faces A plus counterweight W
Kilogram when shafting vibratory response.It can be obtained rotating speed of the shafting in W kilograms of 0 degree of the faces A plus counterweight pass corresponding with vibration amplitude
The correspondence of system and rotating speed and vibration phase.The concept that influence coefficient is aggravated according to dynamic balancing, can obtain different rotating speeds
The lower measuring point aggravates the faces A to influence coefficient.And so on, two-sided exacerbation can be calculated, with mutually exacerbation, the influence system reversely aggravated
Number.Two-sided exacerbation is that two faces are aggravated；It is to be aggravated in the same angle position in two faces with mutually exacerbation；Reverse phase aggravates i.e. two
It is aggravated in 180 ° of positions of difference in a face.
Using the implementation method of ARMD softwares：
Step S41：It determines that the rotating speed of institute's shafting is N, and determines the first counterweight face θ degree counterweights W of shafting；
Step S42：To institute's dynamics mathematical model into action balance simulation calculation, the vibratory response of shafting is obtained, is vibrated
Response includes vibration amplitude and vibration phase；
Step S43：According to institute's vibratory response, it is N to calculate shafting in rotating speed, and adding when the first counterweight face θ degree counterweight W
Ghost image rings coefficient.
ARMD is professional rotor software, is directly changed rotor counterweight, you can realize the emulation of out-of-balance force, and ANSYS is
General finite meta software, essence is more abstract, is unable to the rotation of Straight simulation rotor, therefore emulate by the form of exciting force
It is uneven.
For embodiment of the method above-mentioned, for simple description, therefore it is all expressed as a series of combination of actions, still
Those skilled in the art should understand that the application is not limited by the described action sequence, because according to the application, it is certain
Step can be performed in other orders or simultaneously.
The present embodiment discloses a kind of simulation calculation device of shafting dynamic balance exacerbation influence coefficient, shown in Figure 6, packet
It includes：
Shafting model module 11, the dynamics mathematical model for establishing shafting, dynamics mathematical model are：
Wherein, [M1] be shafting mass matrix, [K1] be shafting stiffness matrix, { Q1And { Q2It is generalized force, { U1}
For motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] be shafting revolution matrix, c11、
c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the stiffness parameters of bearing,
Analysis module 12 calculates shafting dynamic balance and aggravates for carrying out Dynamics Simulation Analysis to dynamics mathematical model
Influence coefficient.
The present embodiment discloses another shafting dynamic balance and aggravates to influence the simulation calculation device of coefficient, shown in Figure 7, packet
It includes：Shafting model module 11, analysis module 12 and bearing rigidity module 13.
Bearing rigidity module 13 is used for before establishing the dynamics mathematical model of shafting, calculates damping parameter c11、c12、c21
And c22And calculated rigidity parameter k11、k12、k21And k22。
Specifically, bearing rigidity module 13 includes：
Parameter receiving module, structural parameters and work operating parameter for receiving bearing；Parameter processing module is used for root
According to the structural parameters and work operating parameter of bearing, and combine Lubrication Film Thickness equation, Reynolds equation, energy equation, temperature
Damping parameter c is calculated in viscosity equation and torque equilibrium equation11、c12、c21And c22, and stiffness parameters k is calculated11、
k12、k21And k22；Parameter output module, for exporting damping parameter c11、c12、c21And c22And stiffness parameters k11、k12、k21With
k22。
Specifically, analysis module 12 includes：
First parameter determination module for determining that the rotating speed of shafting is N, and determines the first counterweight face θ degree counterweights W of shafting
When the simple harmonic quantity centrifugal force Q that generates；First analysis module obtains axis for carrying out harmonic excitation analysis to dynamics mathematical model
The vibratory response of system, vibratory response include vibration amplitude and vibration phase；First computing module, for according to vibratory response, meter
It is N that shafting, which is calculated, in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W influences coefficient.
Alternatively, analysis module 12 includes：
Second parameter determination module for determining that the rotating speed of shafting is N, and determines the first counterweight face θ degree counterweights of shafting
W；Second analysis module is vibrated for, into action balance simulation calculation, obtaining the vibratory response of shafting to dynamics mathematical model
Response includes vibration amplitude and vibration phase；Second computing module is used for according to vibratory response, and it is N to calculate shafting in rotating speed,
And exacerbation when the first counterweight face θ degree counterweight W influences coefficient.
For device embodiments, since it essentially corresponds to embodiment of the method, so related place is referring to method reality
Apply the part explanation of example.The apparatus embodiments described above are merely exemplary, wherein described be used as separating component
The unit of explanation may or may not be physically separated, and the component shown as unit can be or can also
It is not physical unit, you can be located at a place, or may be distributed over multiple network units.It can be according to actual
It needs that some or all of module therein is selected to achieve the purpose of the solution of this embodiment.Those of ordinary skill in the art are not
In the case of making the creative labor, you can to understand and implement.
Herein, relational terms such as first and second and the like be used merely to by an entity or operation with it is another
One entity or operation distinguish, and without necessarily requiring or implying between these entities or operation, there are any this reality
Relationship or sequence.Moreover, the terms "include", "comprise" or its any other variant are intended to the packet of nonexcludability
Contain, so that the process, method, article or equipment including a series of elements includes not only those elements, but also includes
Other elements that are not explicitly listed, or further include for elements inherent to such a process, method, article, or device.
In the absence of more restrictions, the element limited by sentence "including a ...", it is not excluded that including the element
Process, method, article or equipment in there is also other identical elements.
Each embodiment is described by the way of progressive in this specification, the highlights of each of the examples are with other
The difference of embodiment, just to refer each other for identical similar portion between each embodiment.
The foregoing description of the disclosed embodiments enables professional and technical personnel in the field to realize or use the application.
Various modifications to these embodiments will be apparent to those skilled in the art, as defined herein
General Principle can in other embodiments be realized in the case where not departing from spirit herein or range.Therefore, the application
It is not intended to be limited to the embodiments shown herein, and is to fit to and the principles and novel features disclosed herein phase one
The widest range caused.
Claims (10)
1. a kind of shafting dynamic balance aggravates to influence the emulated computation method of coefficient, which is characterized in that including：
The dynamics mathematical model of shafting is established, the dynamics mathematical model is：
Wherein, [M1] be the shafting mass matrix, [K1] be the shafting stiffness matrix, { Q1And { Q2It is generalized force,
{U1It is motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] be the shafting revolution
Matrix, c11、c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the rigid of the bearing
Parameter is spent,
Dynamics Simulation Analysis is carried out to the dynamics mathematical model, the shafting dynamic balance is calculated and aggravates to influence coefficient.
2. according to the method described in claim 1, it is characterized in that, it is described establish the dynamics mathematical model of shafting before, also
Including：Calculate the damping parameter c11、c12、c21And c22, and calculate the stiffness parameters k11、k12、k21And k22。
3. according to the method described in claim 2, it is characterized in that, described calculate the damping parameter c11、c12、c21And c22, with
And calculate the stiffness parameters k11、k12、k21And k22Including for：
Receive the structural parameters and work operating parameter of the bearing；
According to the structural parameters of the bearing and work operating parameter, and combine Lubrication Film Thickness equation, Reynolds equation, energy
The damping parameter c is calculated in equation, temperature-viscosity equation and torque equilibrium equation11、c12、c21And c22, and calculate
To the stiffness parameters k11、k12、k21And k22
Export the damping parameter c11、c12、c21And c22And the stiffness parameters k11、k12、k21And k22。
4. according to the method described in claim 1, it is characterized in that, described imitative to dynamics mathematical model progress dynamics
True analysis, calculating the shafting dynamic balance exacerbation influence coefficient includes：
It determines that the rotating speed of the shafting is N, and determines the simple harmonic quantity centrifugation generated when the first counterweight face θ degree counterweight W of the shafting
Power Q；
Harmonic excitation analysis is carried out to the dynamics mathematical model, obtains the vibratory response of the shafting, the vibratory response
Including vibration amplitude and vibration phase；
According to the vibratory response, it is N to calculate the shafting in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W influences
Coefficient.
5. according to the method described in claim 1, it is characterized in that, described imitative to dynamics mathematical model progress dynamics
True analysis, calculating the shafting dynamic balance exacerbation influence coefficient includes：
It determines that the rotating speed of the shafting is N, and determines the first counterweight face θ degree counterweights W of the shafting；
To the dynamics mathematical model into action balance simulation calculation, the vibratory response of the shafting is obtained, the vibration is rung
Should include vibration amplitude and vibration phase；
According to the vibratory response, it is N to calculate the shafting in rotating speed, and exacerbation when the first counterweight face θ degree counterweight W influences
Coefficient.
6. a kind of shafting dynamic balance aggravates to influence the simulation calculation device of coefficient, which is characterized in that including：
Shafting model module, the dynamics mathematical model for establishing shafting, the dynamics mathematical model are：
Wherein, [M1] be the shafting mass matrix, [K1] be the shafting stiffness matrix, { Q1And { Q2It is generalized force,
{U1It is motion vector,For velocity vector,For vector acceleration, G1=-[C1], [C1] be the shafting revolution
Matrix, c11、c12、c21And c22For the damping parameter of the bearing of the support shafting, k11、k12、k21And k22For the rigid of the bearing
Parameter is spent,
Analysis module calculates the shafting dynamic balance and adds for carrying out Dynamics Simulation Analysis to the dynamics mathematical model
Ghost image rings coefficient.
7. device according to claim 6, which is characterized in that further include：
Bearing rigidity module, for it is described establish the dynamics mathematical model of shafting before, calculate the damping parameter c11、c12、
c21And c22, and calculate the stiffness parameters k11、k12、k21And k22。
8. device according to claim 7, which is characterized in that the bearing rigidity module includes：
Parameter receiving module, the structural parameters for receiving the bearing and work operating parameter；
Parameter processing module for the structural parameters and work operating parameter according to the bearing, and combines Lubrication Film Thickness
The damping parameter c is calculated in equation, Reynolds equation, energy equation, temperature-viscosity equation and torque equilibrium equation11、c12、
c21And c22, and the stiffness parameters k is calculated11、k12、k21And k22；
Parameter output module, for exporting the damping parameter c11、c12、c21And c22And the stiffness parameters k11、k12、k21
And k22。
9. device according to claim 6, which is characterized in that the analysis module includes：
First parameter determination module for determining that the rotating speed of the shafting is N, and determines the first counterweight face θ degree of the shafting
The simple harmonic quantity centrifugal force Q generated when counterweight W；
First analysis module obtains the vibration of the shafting for carrying out harmonic excitation analysis to the dynamics mathematical model
Response, the vibratory response includes vibration amplitude and vibration phase；
First computing module is N for according to the vibratory response, calculating the shafting in rotating speed, and the first counterweight face θ degree
Exacerbation when counterweight W influences coefficient.
10. device according to claim 6, which is characterized in that the analysis module includes：
Second parameter determination module for determining that the rotating speed of the shafting is N, and determines the first counterweight face θ degree of the shafting
Counterweight W；
Second analysis module, for, into action balance simulation calculation, obtaining shaking for the shafting to the dynamics mathematical model
Dynamic response, the vibratory response include vibration amplitude and vibration phase；
Second computing module is N for according to the vibratory response, calculating the shafting in rotating speed, and the first counterweight face θ degree
Exacerbation when counterweight W influences coefficient.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710099723.5A CN108509661A (en) | 2017-02-23 | 2017-02-23 | A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201710099723.5A CN108509661A (en) | 2017-02-23 | 2017-02-23 | A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN108509661A true CN108509661A (en) | 2018-09-07 |
Family
ID=63373571
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201710099723.5A Pending CN108509661A (en) | 2017-02-23 | 2017-02-23 | A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN108509661A (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111190944A (en) * | 2020-01-08 | 2020-05-22 | 北京仿真中心 | Data mining method and system |
| CN114182489A (en) * | 2021-12-16 | 2022-03-15 | 海信（山东）冰箱有限公司 | Pulsator washing machine simulation method and device, computer readable medium and washing machine |
| CN114182488A (en) * | 2021-12-16 | 2022-03-15 | 海信（山东）冰箱有限公司 | Drum washing machine simulation method and device, computer readable medium and washing machine |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0837262B1 (en) * | 1996-10-21 | 2003-04-16 | ABB Solyvent Ventec | Weight-responsive dynamic balancing device for rotating machines,in particular for industrial ventilators |
| CN104535262A (en) * | 2015-01-20 | 2015-04-22 | 湖南科技大学 | Complete machine trial-mass-free virtual dynamic balance method for turbine machinery N+1 supporting shafting |
| CN104568313A (en) * | 2015-01-20 | 2015-04-29 | 湖南科技大学 | Influence coefficient dynamic balance method on rotating machine with multiple plane, multiple-points and multiple revolving speed shafting |
-
2017
- 2017-02-23 CN CN201710099723.5A patent/CN108509661A/en active Pending
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0837262B1 (en) * | 1996-10-21 | 2003-04-16 | ABB Solyvent Ventec | Weight-responsive dynamic balancing device for rotating machines,in particular for industrial ventilators |
| CN104535262A (en) * | 2015-01-20 | 2015-04-22 | 湖南科技大学 | Complete machine trial-mass-free virtual dynamic balance method for turbine machinery N+1 supporting shafting |
| CN104568313A (en) * | 2015-01-20 | 2015-04-29 | 湖南科技大学 | Influence coefficient dynamic balance method on rotating machine with multiple plane, multiple-points and multiple revolving speed shafting |
Non-Patent Citations (2)
| Title |
|---|
| 殷勍: "基于ANSYS的涡轮增压器转子***动力学特性研究", 《中国优秀硕士学位论文全文数据库 工程科技Ⅱ辑》 * |
| 陈涛 等: "非均布变包角可倾瓦轴承性能分析", 《舰船科学技术》 * |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN111190944A (en) * | 2020-01-08 | 2020-05-22 | 北京仿真中心 | Data mining method and system |
| CN114182489A (en) * | 2021-12-16 | 2022-03-15 | 海信（山东）冰箱有限公司 | Pulsator washing machine simulation method and device, computer readable medium and washing machine |
| CN114182488A (en) * | 2021-12-16 | 2022-03-15 | 海信（山东）冰箱有限公司 | Drum washing machine simulation method and device, computer readable medium and washing machine |
| CN114182488B (en) * | 2021-12-16 | 2023-11-21 | 海信冰箱有限公司 | Drum washing machine simulation method and device, computer readable medium and washing machine |
| CN114182489B (en) * | 2021-12-16 | 2024-04-19 | 海信冰箱有限公司 | Pulsator washing machine simulation method and device, computer readable medium and washing machine |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Al-Shudeifat et al. | New breathing functions for the transverse breathing crack of the cracked rotor system: approach for critical and subcritical harmonic analysis | |
| Sperling et al. | Simulation of two-plane automatic balancing of a rigid rotor | |
| Han et al. | Dynamic response of cracked rotor-bearing system under time-dependent base movements | |
| Avramov et al. | Nonlinear dynamics of one disk asymmetrical rotor supported by two journal bearings | |
| Khanlo et al. | The effects of lateral–torsional coupling on the nonlinear dynamic behavior of a rotating continuous flexible shaft–disk system with rub–impact | |
| CN109829262A (en) | A kind of rotor-bearing system nonlinear dynamic analysis method | |
| CN108509661A (en) | A kind of shafting dynamic balance aggravates the emulated computation method and device of influence coefficient | |
| Zou et al. | Coupled longitudinal–transverse dynamics of a marine propulsion shafting under primary and internal resonances | |
| CN107133387A (en) | The imbalance compensation algorithm of rotor unbalance coefficient variable step polygon iterated search | |
| Bin et al. | Virtual dynamic balancing method without trial weights for multi-rotor series shafting based on finite element model analysis | |
| Filimonikhin et al. | Application of the empirical criterion for the occurrence of auto-balancing for axisymmetric rotor on two isotropic elastic supports | |
| CN103292958A (en) | Model based rotor non-trial-mass unbalance parameter identification method | |
| RU2426976C2 (en) | Procedure and device for automatic rotor balancing | |
| Hundal et al. | Balancing of flexible rotors having arbitrary mass and stiffness distribution | |
| Panovko et al. | Resonant adjustment of vibrating machines with unbalance vibroexciter. Problems and solutions | |
| Michalczyk | Inaccuracy in self-synchronisation of vibrators of two-drive vibratory machines caused by insufficient stiffness of vibrators mounting | |
| Yun et al. | Investigation on a no trial weight spray online dynamic balancer | |
| JP4140380B2 (en) | Dynamic imbalance calculation method and dynamic balance test equipment | |
| Hong et al. | Vibration failure analysis of multi-disk high-speed rotor based on rotary inertia load model | |
| CN109847952B (en) | Dynamic balance method of double-shaft precision centrifuge turntable based on driving current | |
| Li et al. | Investigation on the stability of periodic motions of a flexible rotor-bearing system with two unbalanced disks | |
| Khanlo et al. | Disk position nonlinearity effects on the chaotic behavior of rotating flexible shaft-disk systems | |
| Strautmanis et al. | Modelling of transient and steady-state modes of a vertical rotor with an automatic balancing device | |
| Pavlenko | ROTOR MACHINERY DYNAMICS | |
| Arena et al. | On the stability of magnetically levitated rotating rings |
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 | ||
| RJ01 | Rejection of invention patent application after publication | ||
| RJ01 | Rejection of invention patent application after publication |
Application publication date: 20180907 |