CN104460728A - Dynamic balance suppression method for spatial vibration of high-speed rotor bearing system - Google Patents

Abstract

The invention discloses a dynamic balance suppression method for spatial vibration of a high-speed rotor bearing system. On the basis of testing spatial vibration of the high-speed rotor bearing system, the incidence relation between the displacement and vibration motion track area and the amount of unbalance is given, an optimized objective function involving rotor displacement and bearing vibration is established, synchronous suppression of rotor displacement and bearing vibration is achieved in combination with an optimization method, both promotion of rotor rotation precision and suppression of unbalance vibration energy are taken into consideration, and the proportions of displacement and vibration suppression effects in different directions and on different sections are controlled through configuration of weight coefficients. The dynamic balance suppression method overcomes the defects that according to traditional vibration suppression methods, rotor displacement or bearing vibration is seldom taken into comprehensive consideration, most of vibration tests are implemented only in a single direction or on a single section, and consequently it is unable to attend to everything at once occasionally. Compared with the traditional methods, the dynamic balance suppression method has the advantages that the vibration control effect of the rotor bearing system can be optimal, and the service life of the system can be prolonged effectively while the running accuracy of the system is guaranteed.

Description

A kind of transient equilibrium 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, the transient equilibrium suppressing method of particularly 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 comparatively complicated, but its vibration signal presents stationary signal feature more, and the vibration that the factor such as excitation, thermal deformation, periodically environmental interference causes is cut in such as pure unbalance vibration, and die misalignment, periodicity.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.In addition, the flexible characteristic of unbalance rotor is in excited state, is more easily subject to the impact of external drive, and then causes the generation of the non-stationary signals such as flutter.Owing to limiting by technological level, above-mentioned unbalance and non-unbalance disturbing factor is almost inevitable, for unbalance, the factors such as rotor manufacture and rigging error, material are uneven all can cause rotor unbalance, and centrifugal bulking effect when rotor high-speed rotates in addition also can destroy original equilibrium state.

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

The subsystem of rotor-bearing system normally in complex electromechanical systems, only analyzes its dynamic perfromance existed before and after the fault such as unbalance and is nowhere near under free boundary condition.After rotor-bearing system installs, main shaft and its bearing base form the new system intercoupled, and bearing base vibration will produce the impact of can not ignore to the dynamic perfromance 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 is this moment 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 carry out independent analysis or optimization to both respectively.And rarely have the vibration integrated consideration of two classes just because of existing dynamic balance method, there is the phenomenon of attending to one thing and lose sight of another to occur time in balancing run.Therefore, need to carry out reasonable assessment and overall equilbrium to rotor absolute displacement and bearing base Relative Vibration, and then effectively suppress rotor-bearing system space oscillations.

Summary of the invention

The object of the invention is to the shortcoming overcoming above-mentioned prior art, the transient equilibrium 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 lifting rotor rotating accuracy, also take into account the suppression of unbalance vibrational energy.

For reaching above object, the present invention takes following technical scheme to be achieved:

A transient equilibrium suppressing method for high speed rotor bearing system space vibration, comprises the steps:

Step one, gathers balancing disk surface level and vertical direction displacement signal δ by displacement transducer _lH, δ _lV, δ _rH, δ _rV, gather bearing outer ring place vibration signal υ by vibration transducer _lH, υ _lV, υ _rH, υ _rV, by phase demodulation sensor acquisition phase signal.

Wherein: subscript letter represents sensor mounting location, L represents left side, and R represents right side, and H represents level, and V represents 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 the long and short axle of ellipse, build the movement locus ellipse corresponding with vibration, displacement signal, and then according to ellipse area geometry solving formula, set up movement locus ellipse area with the incidence relation of vibration, displacement signal;

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

Step 3, by adding test mass on the balancing disk of both sides, sets up with the amount of unbalance P of 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 displacement of diverse location place or the influence coefficient between vibration signal and unit of balancing disk place, rotor both sides amount of unbalance, in the Superscript letters of μ, l, r represent relevant to left side, right side balancing disk respectively, and the female implication of other upper and lower marking-up is the same; Such as be numerically equal to unit amount of unbalance on the balancing disk of left side and cause 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 the weight coefficient carrying out transient equilibrium suppression is vibrated to left side displacement, right side displacement, left side vibration, right side;

Step 5, builds multi-goal optimizing function, that is:

Minimize f(P _l,P _r)＝β ₁f ₁+β ₂f ₂

Wherein: β ₁, β ₂represent weight coefficient overall situation vibration and local vibration being carried out to transient equilibrium suppression respectively, get β ₁> β ₂;

Step 6, according to the majorized function that step 5 is set up, solves the counterweight combination { P corresponding to Minimize f _l, P _r, this counterweight combination { P _l, P _rbe 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 transient equilibrium completing rotor-bearing system space oscillations suppresses operation.

μ in above-mentioned 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 effect of the present invention: compared with prior art, the present invention has the following advantages:

1, the present invention can control high speed rotor absolute displacement and bearing base Relative Vibration simultaneously, has taken into account the lifting of rotor rotating accuracy and the suppression of 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 tradition vibration describing mode more comprehensive;

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

4, compared with traditional dynamic balance method, the present invention is easy to robotization and realizes, and integrated level is high, is beneficial to software simulating, and can embed and select equipment complex TT&C system, range of application is comparatively extensive.

For a more clear understanding of the present invention, below in conjunction with accompanying drawing, the present invention is described in further detail.

Accompanying drawing explanation

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

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

Fig. 3 be the inventive method transient equilibrium Inhibition test before and after rotor displacement comparison diagram;

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

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

Embodiment

This embodiment gives the specific implementation process of the present invention in engineering practice.

1, the collection of rotor displacement and bear vibration data

Be illustrated in figure 1 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, no longer describes in detail its structure at this; Fig. 4 is the steps flow chart block diagram of the inventive method.The present invention gathers balancing disk surface level and vertical direction displacement signal δ by displacement transducer 1 _lH, δ _lV, δ _rH, δ _rV, gather bearing outer ring vibration signal υ by vibration transducer 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 the long and short axle of ellipse, build the movement locus ellipse corresponding with vibration, displacement signal, and then according to ellipse area geometry solving formula, set up movement locus ellipse area as 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 formed respectively.

3, the structure of multi-goal optimizing function

1) by adding test mass on both sides balancing disk 4, set up with the amount of unbalance P of 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 displacement of diverse location place or the influence coefficient between vibration signal and unit of balancing disk place, rotor both sides amount of unbalance, and μ is tested by test mass and obtains, 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, the female implication of other upper and lower marking-up is the same.Namely be numerically equal to unit amount of unbalance on the balancing disk 4 of left side and cause the change of left side horizontal position displacement signal, other mu-factor member 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 the weight coefficient carrying out transient equilibrium suppression is vibrated to left side displacement, right side displacement, left side vibration, right side; These coefficient values are determined jointly by rotor-bearing system diverse location vibration transfer function and rig-site utilization demand;

3) multi-goal optimizing function Minimize f (P is built _l, P _r)=β ₁f ₁+ β ₂f ₂

Wherein: β ₁, β ₂represent weight coefficient overall situation vibration and local vibration being carried out to transient equilibrium suppression respectively, get β ₁> β ₂;

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 transient equilibrium of space oscillations suppresses

By the balancing disk 4 of rotor both sides, be applied through the optimum counterweight that Optimization Solution obtains, the transient equilibrium completing rotor-bearing system space oscillations suppresses operation.

After implementing transient equilibrium operation, as shown in Figures 2 and 3, light three dimensions vibrorecord is the state before transient equilibrium suppresses, and dark three dimensions vibrorecord is the effect after suppression.From Fig. 2 and Fig. 3, the present invention, by building optimization object function, can realize the comprehensive suppression of different measuring points, multi-freedom-degree vibration fast; Control while achieving high speed rotor absolute displacement and bearing base Relative Vibration, taken into account the lifting of rotor rotating accuracy and the suppression of unbalance vibrational energy.In addition, the present invention adopts track area to describe rotor and bear vibration state, and considers the vibration of system both sides simultaneously, includes space oscillations behavior in monitoring range, compares tradition vibration describing mode more comprehensive.

The parts that embodiment does not describe in detail, technique and letter representation belong to the well-known components of the industry and conventional means and general knowledge, do not describe one by one here.More than exemplifying is only illustrate of the present invention, does not form the restriction to protection scope of the present invention, everyly all belongs within protection scope of the present invention with the same or analogous design of the present invention.

Claims (2)

1. a transient equilibrium suppressing method for high speed rotor bearing system space vibration, is characterized in that: comprise the steps:

Step one, gathers balancing disk surface level and vertical direction 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 vibration transducer _lH, υ _lV, υ _rH, υ _rV, by phase demodulation sensor acquisition phase signal;

Wherein: subscript letter represents sensor mounting location, L represents left side, and R represents right side, and H represents level, and V represents 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 the long and short axle of ellipse, build the movement locus ellipse corresponding with vibration, displacement signal, and then according to ellipse area geometry solving formula, set up movement locus ellipse area with the incidence relation of vibration, displacement signal;

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

Step 3, by adding test mass on the balancing disk of both sides, sets up with the amount of unbalance P of 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 displacement of diverse location place or the influence coefficient between vibration signal and unit of balancing disk place, rotor both sides amount of unbalance, in the Superscript letters of μ, l, r represent relevant to left side, right side balancing disk respectively, and the female implication of other upper and lower marking-up is the same; Such as be numerically equal to unit amount of unbalance on the balancing disk of left side and cause 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 the weight coefficient carrying out transient equilibrium suppression is vibrated to left side displacement, right side displacement, left side vibration, right side;

Step 5, builds multi-goal optimizing function, that is:

Minimize f(P _l,P _r)＝β ₁f ₁+β ₂f ₂

Wherein: β ₁, β ₂represent weight coefficient overall situation vibration and local vibration being carried out to transient equilibrium suppression respectively, get β ₁> β ₂;

Step 6, according to the majorized function that step 5 is set up, solves the counterweight combination { P corresponding to Minimize f _l, P _r, this counterweight combination { P _l, P _rbe 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 transient equilibrium completing rotor-bearing system space oscillations suppresses operation.

2. the transient equilibrium suppressing method of a kind of high speed rotor bearing system space vibration as claimed in claim 1, is characterized in that: the μ in described step 3 meets following relationship:

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