CN104460728B - A kind of dynamic balancing suppressing method of high speed rotor bearing system space vibration - Google Patents

Abstract

The invention discloses the dynamic balancing suppressing method of a kind of high speed rotor bearing system space vibration。The present invention is on the basis of test rotor-bearing system space oscillations, provide the incidence relation between displacement and oscillating movement track area and amount of unbalance, construct the optimization object function comprising rotor displacement and bear vibration, the synchronization realizing both in conjunction with optimization method suppresses, that has taken into account rotor rotating accuracy promotes the suppression with unbalance vibrational energy, and by the configuration of weight coefficient, control the proportion of different azimuth, different cross section top offset and vibration suppressioning effect。Instant invention overcomes conventional vibration suppressing method to rarely have and consider rotor displacement or bear vibration, and vibration-testing is most implements only for one direction or single cross section, thus there being the shortcoming that phenomenon of attending to one thing and lose sight of another occurs when causing。Compared with traditional method, the present invention can make rotor-bearing system vibration control effect reach optimum, while ensureing system running precision, also can effectively extend system service life。

Description

A kind of dynamic balancing suppressing method of high speed rotor bearing system space vibration

Technical field

The present invention relates to Fault Diagnosis of Rotating Equipment Based and vibration control method, particularly to the dynamic balancing suppressing method of a kind of high speed rotor bearing system space vibration, the method can realize the Comprehensive Control of high speed rotor absolute displacement and bearing base Relative Vibration simultaneously。

Background technology

High speed rotor bearing system space oscillation trajectory is complex, but its vibration signal presents stationary signal feature more, for instance pure unbalance vibration, and die misalignment, periodicity cut the vibration that the factor such as excitation, thermal deformation, periodically environmental disturbances causes。But when imbalance fault is very serious, rotor collides and friction in operation, and sinusoidal fluctuation originally can be changed to the vibrational waveform of non-stationary。Additionally, the flexible characteristic of unbalance rotor is in excited state, it is easier to be subject to the impact of external drive, and then cause the generation of the non-stationary signals such as tremor。Owing to being limited by technological level, above-mentioned unbalance and non-unbalance interference factor is almost inevitable, for unbalance, rotor manufacture and rigging error, material are uneven etc., and factor all can cause rotor unbalance, and additionally centrifugal bulking effect during rotor high speed rotating also can destroy original poised state。

Above-mentioned analysis shows, the vibration behavior of rotor complex space is inevitable。But, the vibration state of slewing is the important parameter that assessment equipment runs health status, if vibration is more than a definite limitation, not only affect part processing precision, also rotor own components can be damaged, sharply reduce the rotor-support-foundation system life-span, even make some assembly excessive and damage on the spot due to vibratory output。Therefore, how to suppress rotor space vibration particularly important。

Rotor-bearing system is usually a subsystem in complex electromechanical systems, only analyzes its dynamic characteristic existed before and after the fault such as unbalance under free boundary condition and is nowhere near。After rotor-bearing system installs, main shaft forms, with its bearing base, the new system intercoupled, the impact that generation be can not ignore by bearing base vibration by the dynamic characteristic of rotor-support-foundation system。And when being in the malfunctions such as imbalance when rotor, its center of inertia is not on axis of rotation, bearing base place vibration this moment is particularly evident。

Rotor absolute displacement and bearing base Relative Vibration characterize rotating accuracy, unbalance vibrational energy respectively, the existing research suppressed about rotor-bearing system space oscillations does not consider rotor displacement and bear vibration simultaneously, is all that both carry out independent analysis or optimization respectively。And rarely have the two vibration integrated considerations of class just because of existing dynamic balance method, there is the phenomenon attended to one thing and lose sight of another to occur time in balancing run。Accordingly, it would be desirable to rotor absolute displacement and bearing base Relative Vibration carried out reasonable assessment and aggregate balancing, and then effectively suppress rotor-bearing system space oscillations。

Summary of the invention

It is an object of the invention to the shortcoming overcoming above-mentioned prior art, the dynamic balancing suppressing method of a kind of high speed rotor bearing system space vibration is proposed, high speed rotor absolute displacement and bearing base Relative Vibration can be controlled simultaneously, while promoting rotor rotating accuracy, also take into account the suppression of unbalance vibrational energy。

For reaching object above, the present invention adopts the following technical scheme that and is achieved:

The dynamic balancing suppressing method of a kind of high speed rotor bearing system space vibration, comprises the steps:

Step one, gathers balancing disk surface both horizontally and vertically displacement signal δ by displacement transducer_LH,δ_LV,δ_RH,δ_RV, gather bearing outer ring place vibration signal υ by vibrating sensor_LH,υ_LV,υ_RH,υ_RV, by phase demodulation sensor acquisition phase signal。

Wherein: subscript letter represents that sensor mounting location, L represent left side, and R represents right side, and H represents that level, V represent vertical；δ_LH,δ_LV,δ_RH,δ_RVRepresent the displacement signal in left side level, left vertical, right side level, Right vertical direction respectively；υ_LH,υ_LV,υ_RH,υ_RVRepresent the vibration signal in left side level, left vertical, right side level, Right vertical direction respectively；

Step 2, respectively with level, vertical signal for oval long and short axle, builds oval with the movement locus vibrated, displacement signal is corresponding, and then according to ellipse area geometry solving formula, sets up movement locus ellipse areaIncidence relation with vibration, displacement signal；

Wherein: Superscript letters represents the signal type constituting ellipse, and δ represents that displacement, υ represent vibration, subscript letter implication is the same, namelyRepresent the move contrail fitting ellipse area that left side displacement, right side displacement, left side vibration, right side vibration signal are constituted respectively

Step 3, by adding test mass on the balancing disk of both sides, sets upAmount of unbalance P with left and right side balancing disk position_l、P_rBetween incidence relation:

$S_L^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δr}}{P}_r|$

$S_R^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δr}}{P}_r|$

$S_L^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υr}}{P}_r|$

$S_R^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υr}}{P}_r|$

Wherein: μ is the influence coefficient between various location displacement or vibration signal and balancing disk place, rotor both sides unit amount of unbalance, in the Superscript letters of μ, l, r represent relevant to left side, right side balancing disk respectively, and other upper and lower marking-up mother's implication is the same；Such asOn the left of being numerically equal to, on balancing disk, unit amount of unbalance causes the change of left side horizontal position displacement signal。

Step 4, builds rotor-bearing system space residual oscillation described function:

$f_1={\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}}+{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}}+{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}}+{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}}$

$f_2=\max ({\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}}+{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}}+{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}}+{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}})$

Wherein:Represent respectively and left side displacement, right side displacement, left side vibration, right side are vibrated the weight coefficient carrying out dynamic balancing suppression；

Step 5, builds multi-goal optimizing function, it may be assumed that

Minimizef(P_l,P_r)=β₁f₁+β₂f₂

Wherein: β₁,β₂Represent the weight coefficient that overall situation vibration and local vibration are carried out dynamic balancing suppression respectively, take β₁> β₂；

Step 6, according to the majorized function that step 5 is set up, solves the counterweight combination { P corresponding to Minimizef_l,P_r, this counterweight combination { P_l,P_rIt is optimal balance combinations of weights；

Step 7, by the balancing disk of rotor both sides, applies the optimum counterweight that step 6 obtains, and the dynamic balancing completing rotor-bearing system space oscillations suppresses operation。

The above-mentioned μ in step 3 meets following relationship:

${\left[\begin{array}{cccccccc}{\mathrm{\δ}}_{\mathrm{LH}}& {\mathrm{\δ}}_{\mathrm{LV}}& {\mathrm{\δ}}_{\mathrm{RH}}& {\mathrm{\δ}}_{\mathrm{RV}}& {\mathrm{\υ}}_{\mathrm{LH}}& {\mathrm{\υ}}_{\mathrm{LV}}& {\mathrm{\υ}}_{\mathrm{RH}}& {\mathrm{\υ}}_{\mathrm{RV}}\end{array}\right]}^T={\left[\begin{array}{cccccccc}{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υl}}\\ {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υr}}\end{array}\right]}^T\left[\begin{array}{c}{P}_l\\ P_r\end{array}\right].$

Beneficial effects of the present invention: compared with prior art, the invention have the advantages that

1, the present invention can control high speed rotor absolute displacement and bearing base Relative Vibration simultaneously, and that has taken into account rotor rotating accuracy promotes the suppression with unbalance vibrational energy；

2, the present invention adopts track area to describe rotor and bear vibration state, and considers the vibration of rotor-bearing system both sides simultaneously, includes space oscillations behavior in monitoring range, compares conventional vibration describing mode more fully；

3, the present invention is when processing rotor-bearing system space oscillations problem, constructs optimization object function, can quickly realize the comprehensive suppression of different measuring points, multi-freedom-degree vibration；

4, compared with traditional dynamic balance method, the present invention is prone to automatization and realizes, and integrated level is high, is beneficial to software and realizes, and can embed selection equipment complex TT&C system, and range of application is relatively broad。

Understanding the present invention in order to clearer, below in conjunction with accompanying drawing, the present invention is described in further detail。

Accompanying drawing explanation

Fig. 1 is the high speed rotor bearing system model sketch of the present invention；

Fig. 2 is the dynamic balancing Inhibition test front and back bearings vibration comparison diagram of the inventive method；

Fig. 3 is rotor displacement comparison diagram before and after the dynamic balancing Inhibition test of the inventive method；

Fig. 4 is the steps flow chart block diagram of the inventive method。

Description of reference numerals: 1, displacement transducer；2, vibrating sensor；3, phase demodulation sensor；4, balancing disk。

Detailed description of the invention

This embodiment gives present invention specific implementation process in engineering practice。

1, the collection of rotor displacement and bear vibration data

Being illustrated in figure 1 the high speed rotor bearing system model sketch (only drawing vertical direction sensor in figure) of the present invention, the structure of this high speed rotor bearing system is prior art, at this, its structure is no longer described in detail；Fig. 4 is the steps flow chart block diagram of the inventive method。The present invention gathers balancing disk surface both horizontally and vertically displacement signal δ by displacement transducer 1_LH,δ_LV,δ_RH,δ_RV, gather bearing outer ring vibration signal υ by vibrating sensor 2_LH,υ_LV,υ_RH,υ_RV, by phase demodulation sensor 3 acquisition phase signal；

Wherein: δ_LH,δ_LV,δ_RH,δ_RVRepresent the displacement signal in left side level, left vertical, right side level, Right vertical direction respectively；υ_LH,υ_LV,υ_RH,υ_RVRepresent the vibration signal in left side level, left vertical, right side level, Right vertical direction respectively。

2, the fusion of displacement and vibration data

Respectively with level, vertical signal for oval long and short axle, build oval with the movement locus vibrated, displacement signal is corresponding, and then according to ellipse area geometry solving formula, set up movement locus ellipse areaAs follows with the incidence relation of vibration, displacement signal:

$S_L^{\mathrm{\δ}}=\mathrm{\π}\left|{\mathrm{\δ}}_{\mathrm{LH}}\right|\·\left|{\mathrm{\δ}}_{\mathrm{LV}}\right|$

$S_R^{\mathrm{\δ}}=\mathrm{\π}\left|{\mathrm{\δ}}_{\mathrm{RH}}\right|\·\left|{\mathrm{\δ}}_{\mathrm{RV}}\right|$

$S_L^{\mathrm{\υ}}=\mathrm{\π}\left|{\mathrm{\υ}}_{\mathrm{LH}}\right|\·\left|{\mathrm{\υ}}_{\mathrm{LV}}\right|$

$S_R^{\mathrm{\υ}}=\mathrm{\π}\left|{\mathrm{\υ}}_{\mathrm{RH}}\right|\·\left|{\mathrm{\υ}}_{\mathrm{RV}}\right|$

Wherein:Represent the move contrail fitting ellipse area that left side displacement, right side displacement, left side vibration, right side vibration signal are constituted respectively。

3, the structure of multi-goal optimizing function

1) by adding test mass on both sides balancing disk 4, set upAmount of unbalance P with left and right side balancing disk 4 position_l、P_rBetween incidence relation:

$S_L^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δr}}{P}_r|$

$S_R^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δr}}{P}_r|$

$S_L^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υr}}{P}_r|$

$S_R^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υr}}{P}_r|\·|{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υl}}{P}_l+{\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υr}}{P}_r|$

μ is the influence coefficient between various location displacement or vibration signal and balancing disk place, rotor both sides unit amount of unbalance, and μ is obtained by test mass experiment, and it meets following relationship:

${\left[\begin{array}{cccccccc}{\mathrm{\δ}}_{\mathrm{LH}}& {\mathrm{\δ}}_{\mathrm{LV}}& {\mathrm{\δ}}_{\mathrm{RH}}& {\mathrm{\δ}}_{\mathrm{RV}}& {\mathrm{\υ}}_{\mathrm{LH}}& {\mathrm{\υ}}_{\mathrm{LV}}& {\mathrm{\υ}}_{\mathrm{RH}}& {\mathrm{\υ}}_{\mathrm{RV}}\end{array}\right]}^T={\left[\begin{array}{cccccccc}{\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δl}}& {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υl}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υl}}\\ {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\δr}}& {\mathrm{\μ}}_{\mathrm{LH}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{LV}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{RH}}^{\mathrm{\υr}}& {\mathrm{\μ}}_{\mathrm{RV}}^{\mathrm{\υr}}\end{array}\right]}^T\left[\begin{array}{c}{P}_l\\ P_r\end{array}\right].$

Wherein: in the Superscript letters of μ, l, r represent relevant to left side, right side balancing disk 4 respectively, and other upper and lower marking-up mother's implication is the same。NamelyOn the left of being numerically equal to, on balancing disk 4, unit amount of unbalance causes the change of left side horizontal position displacement signal, and other mu-factor member's implication repeats no more；

2) rotor-bearing system space residual oscillation described function is built

$f_1={\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}}+{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}}+{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}}+{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}}$

$f_2=\max ({\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}}+{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}}+{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}}+{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}})$

Wherein:Represent respectively and left side displacement, right side displacement, left side vibration, right side are vibrated the weight coefficient carrying out dynamic balancing suppression；These coefficient values are determined jointly by rotor-bearing system diverse location vibration transfer function and on-the-spot application demand；

3) multi-goal optimizing function Minimizef (P is built_l,P_r)=β₁f₁+β₂f₂

Wherein: β₁,β₂Represent the weight coefficient that overall situation vibration and local vibration are carried out dynamic balancing suppression respectively, take β₁> β₂；

4) according to step 3) majorized function set up, utilize population intelligent optimization algorithm to solve optimal balance combinations of weights { P_l,P_r}。

4, the dynamic balancing of space oscillations suppresses

By the balancing disk 4 of rotor both sides, being applied through the optimum counterweight that Optimization Solution obtains, the dynamic balancing completing rotor-bearing system space oscillations suppresses operation。

After implementing dynamic balancing operation, as shown in Figures 2 and 3, light color three dimensions vibrogram is the state before dynamic balancing suppresses, and dark three dimensions vibrogram is the effect after suppressing。From Fig. 2 and Fig. 3 it can be seen that the present invention is by building optimization object function, can quickly realize the comprehensive suppression of different measuring points, multi-freedom-degree vibration；Controlling while achieving high speed rotor absolute displacement and bearing base Relative Vibration, that has taken into account rotor rotating accuracy promotes the suppression with unbalance vibrational energy。Additionally, the present invention adopts track area to describe rotor and bear vibration state, and consider the vibration of system both sides simultaneously, include space oscillations behavior in monitoring range, compare conventional vibration describing mode more fully。

Parts, technique and the letter representation that embodiment does not describe in detail belongs to the well-known components of the industry and conventional means and general knowledge, does not describe one by one here。Exemplified as above is only illustration to the present invention, is not intended that the restriction to protection scope of the present invention, every belongs within protection scope of the present invention with the same or analogous design of the present invention。

Claims (2)

1. the dynamic balancing suppressing method of a high speed rotor bearing system space vibration, it is characterised in that: comprise the steps:

Step one, gathers balancing disk surface both horizontally and vertically displacement signal peak-to-peak value δ by displacement transducer_LH,δ_LV,δ_RH,δ_RV, gather bearing outer ring place vibration signal peak-to-peak value υ by vibrating sensor_LH,υ_LV,υ_RH,υ_RV, by phase demodulation sensor acquisition phase signal；

Wherein: subscript letter represents that sensor mounting location, L represent left side, and R represents right side, and H represents that level, V represent vertical；δ_LH,δ_LV,δ_RH,δ_RVRepresent the displacement signal in left side level, left vertical, right side level, Right vertical direction respectively；υ_LH,υ_LV,υ_RH,υ_RVRepresent the vibration signal in left side level, left vertical, right side level, Right vertical direction respectively；

Step 2, respectively with level, vertical signal for oval long and short axle, builds oval with the movement locus vibrated, displacement signal is corresponding, and then according to ellipse area geometry solving formula, sets up movement locus ellipse areaIncidence relation with vibration, displacement signal；

Wherein: Superscript letters represents the signal type constituting ellipse, and δ represents that displacement, υ represent vibration, subscript letter implication is the same, namelyRepresent the movement locus ellipse area that left side displacement, right side displacement, left side vibration, right side vibration signal are constituted respectively；

Step 3, by adding test mass on the balancing disk of both sides, sets upAmount of unbalance P with left and right side balancing disk position_l、P_rBetween incidence relation:

$S_L^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{LH}^{\mathrm{\δ}l}{P}_l+{\mathrm{\μ}}_{LH}^{\mathrm{\δ}r}{P}_r|\·|{\mathrm{\μ}}_{LV}^{\mathrm{\δ}l}{P}_l+{\mathrm{\μ}}_{LV}^{\mathrm{\δ}r}{P}_r|$

$S_R^{\mathrm{\δ}}=\mathrm{\π}|{\mathrm{\μ}}_{RH}^{\mathrm{\δ}l}{P}_l+{\mathrm{\μ}}_{RH}^{\mathrm{\δ}r}{P}_r|\·|{\mathrm{\μ}}_{RV}^{\mathrm{\δ}l}{P}_l+{\mathrm{\μ}}_{RV}^{\mathrm{\δ}r}{P}_r|$

$S_L^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{LH}^{\mathrm{\υ}l}{P}_l+{\mathrm{\μ}}_{LH}^{\mathrm{\υ}r}{P}_r|\·|{\mathrm{\μ}}_{LV}^{\mathrm{\υ}l}{P}_l+{\mathrm{\μ}}_{LV}^{\mathrm{\υ}r}{P}_r|$

$S_R^{\mathrm{\υ}}=\mathrm{\π}|{\mathrm{\μ}}_{RH}^{\mathrm{\υ}l}{P}_l+{\mathrm{\μ}}_{RH}^{\mathrm{\υ}r}{P}_r|\·|{\mathrm{\μ}}_{RV}^{\mathrm{\υ}l}{P}_l+{\mathrm{\μ}}_{RV}^{\mathrm{\υ}r}{P}_r|$

Wherein: For influence coefficient between unit amount of unbalance and rotor-bearing system various location displacement or vibration signal on the balancing disk of rotor both sides, in Superscript letters, l, r represent relevant to left side, right side balancing disk respectively, and other upper and lower marking-up mother's implication is the same；Such asRepresent the influence coefficient between unit amount of unbalance and left side horizontal position displacement signal on the balancing disk of left side；

Step 4, builds rotor-bearing system space residual oscillation described function:

$f_1={\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}}+{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}}+{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}}+{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}}$

$f_2=max({\mathrm{\α}}_L^{\mathrm{\δ}}{S}_L^{\mathrm{\δ}},{\mathrm{\α}}_R^{\mathrm{\δ}}{S}_R^{\mathrm{\δ}},{\mathrm{\α}}_L^{\mathrm{\υ}}{S}_L^{\mathrm{\υ}},{\mathrm{\α}}_R^{\mathrm{\υ}}{S}_R^{\mathrm{\υ}})$

Wherein:Represent respectively and left side displacement, right side displacement, left side vibration, right side are vibrated the weight coefficient carrying out dynamic balancing suppression；

Step 5, builds multi-goal optimizing function, it may be assumed that

Minimizef(P_l,P_r)=β₁f₁+β₂f₂

Wherein: β₁,β₂Represent the weight coefficient that overall situation vibration and local vibration are carried out dynamic balancing suppression respectively, take β₁> β₂；

Step 6, according to the majorized function that step 5 is set up, solves Minimizef (P_l,P_r) corresponding to counterweight combination { P_l,P_r, this counterweight combination { P_l,P_rIt is optimal balance combinations of weights；

Step 7, by the balancing disk of rotor both sides, applies the optimal balance combinations of weights that step 6 obtains, and the dynamic balancing completing rotor-bearing system space oscillations suppresses operation。

2. the dynamic balancing suppressing method of a kind of high speed rotor bearing system space as claimed in claim 1 vibration, it is characterised in that: in described step 3 Meet following relationship:

${\left[\begin{array}{cccccccc}{\mathrm{\δ}}_{LH}& {\mathrm{\δ}}_{LV}& {\mathrm{\δ}}_{RH}& {\mathrm{\δ}}_{RV}& {\mathrm{\υ}}_{LH}& {\mathrm{\υ}}_{LV}& {\mathrm{\υ}}_{RH}& {\mathrm{\υ}}_{RV}\end{array}\right]}^T={\left[\begin{array}{cccccccc}{\mathrm{\μ}}_{LH}^{\mathrm{\δ}l}& {\mathrm{\μ}}_{LV}^{\mathrm{\δ}l}& {\mathrm{\μ}}_{RH}^{\mathrm{\δ}l}& {\mathrm{\μ}}_{RV}^{\mathrm{\δ}l}& {\mathrm{\μ}}_{LH}^{\mathrm{\υ}l}& {\mathrm{\μ}}_{LV}^{\mathrm{\υ}l}& {\mathrm{\μ}}_{RH}^{\mathrm{\υ}l}& {\mathrm{\μ}}_{RV}^{\mathrm{\υ}l}\\ {\mathrm{\μ}}_{LH}^{\mathrm{\δ}r}& {\mathrm{\μ}}_{LV}^{\mathrm{\δ}r}& {\mathrm{\μ}}_{RH}^{\mathrm{\δ}r}& {\mathrm{\μ}}_{RV}^{\mathrm{\δ}r}& {\mathrm{\μ}}_{LH}^{\mathrm{\υ}r}& {\mathrm{\μ}}_{LV}^{\mathrm{\υ}r}& {\mathrm{\μ}}_{RH}^{\mathrm{\υ}r}& {\mathrm{\μ}}_{RV}^{\mathrm{\υ}r}\end{array}\right]}^T\left[\begin{array}{c}{P}_l\\ P_r\end{array}\right].$