CN1067764C - Dynamic rigidity coefficient method and appts. of rotary machinery dynamic balance - Google Patents

Abstract

The present invention relates to a dynamic rigidity coefficient method for dynamic balance of rotary machines and a device thereof, which belongs to the field of machines and is suitable for a rotary machine set with continuous distributed mass and multi-span support of rotors. The present invention is characterized in that by utilizing the theory that an equivalent dynamic rigidity coefficient K<d> in a vibrating matrix equation: [K<d>]{X<s>}={R'} in an equivalent supporting base mechanical model is a constant under a definite operating condition, a dedicated computer which is provided with a preposition signal processor and four calculating modules is used to directly calculate a precise K<d> or select an approximate K<d> according to a measured supporting base vibrating amount X<s> and a supporting base dynamic force R', an optimal grouping counter weight U on a selected correction plane is optimized and calculated, and a residual supporting base vibrating amount is predicted. The present invention has the advantages of high balance precision, no need of trial weighting, need of one to two times of weighting starting, shortened balancing period, wide range of application, etc.

Description

Dynamically balanced dynamic rigidity coefficient balance method of rotating machinery and balance device

The invention provides dynamically balanced dynamic rigidity coefficient balance method of a kind of rotating machinery and balance device, belong to the rotating machinery dynamic balancing technique of mechanical field.

Modern age, the rotating machinery dynamic balance method mainly contained two kinds, and a kind of is method of model balancing, and another kind is an influence coefficient method; at present; improved dynamic balance method is called associating balancing method (UBA method), is that above-mentioned two kinds of methods are combined; vibration shape influence coefficient method and vibration shape circule method are arranged; though wherein vibration shape circule method can be found out ' high point ' and ' emphasis ' quickly on polar coordinates, it is comparatively reliable that examination is for the first time increased the weight of, in the multi-support system; still need examination several times to increase the weight of, open several times, shut down.The patent that have people such as nineteen eighty-three HIT Sato Kazuo deliver more approaching: introduced in " method of rotating machinery balance and device thereof " ' obtaining theoretical method and the application thereof that influence coefficient carries out balance ' by the impedance matrix of bearing spider with the present invention; Tang of Tsing-Hua University tin was wide at " ASME " (85-DET-120 in 1985,7P) introduced the method for ' calculate the dynamic effects coefficient, and then calculating counterweight ' in " determining rotatory mechanical system bottom bracket equiva lent impedance and influence coefficient " that magazine is delivered with stiffness coefficient and the ratio of damping measured by calculating with test; They are at common feature: measured vibrational state amount is shaft vibration amount and bearing dynamic anti-force, and all on axle, two measuring points that are mutually the right angle will be put to measuring point at least in each bearing place.Their common shortcoming is in the transient equilibrium of multi-support rotation unit: all need repeatedly to try to increase the weight of, balance quality is low, opens, shuts down often.

The purpose of this invention is to provide dynamically balanced dynamic rigidity coefficient balance method of a kind of rotating machinery and balance device, improve the precision of EQUILIBRIUM CALCULATION FOR PROCESS, make rotating machinery (unit) open, stop number of times and reduce to 1-2 time effectively.

The basis of ' the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery ' provided by the invention its measurements and calculations is set up a Fig. 1 and is illustrated, the continuous rotor multispan of reflection distributed mass is bearing in the Equivalent Elasticity damping supporting seat model on several same orientation, it is the rotor-bearing system kinetic model, rotor-bearing system is divided into two subsystems, be rotor-support-foundation system and support system, its interphase is taken on rotor journal and the bearing bearing shell oil film surface of contact, two subsystems are set up the equation of motion of oneself respectively, therebetween by a pair of bonding force: bearing dynamic anti-force R and bearing dynamic force R's '

{ R}=-{R ' }-----(1) relational expression interrelates, with the vibration matrix equation of equivalent bearing mechanical model shown in Figure 2:

[K _d] { X _s}={ R ')--bearing dynamic force R ', the accurate equivalent dynamic rigidity coefficient K of bearing are calculated in-(2) _dAnd bearing residual oscillation amount X _s, be characterized in: with this Equivalent Elasticity damping support model, replaced four stiffness coefficients of anisotropy bearing and the bearing model of four ratio of damping, it only needs a stiffness coefficient and a ratio of damping, therefore, and each vibration of supports amount X _sMeasuring point only need one, the measuring point of bearing dynamic force R ' also only needs one, these two measuring points must be placed on same the radial line of supporting-point; Measuring point on each bearing all will be placed on the plane of same axis excessively, and promptly its position angle is φ; Equivalence dynamic rigidity coefficient K _dIn [1] corresponding to V ₁Plant under the operating load situation, [2] are at selected ω _kUnder the rotating speed, [3] have under the situation of definite selected correcting plane position and number m is a constant.

In order to calculate bearing dynamic force R ' and vibration of supports amount X _s, on considering rotor-support-foundation system, the given exciting force that always increases the weight of to be produced, also need take into account the caused additional uneven exciting force of rotor-support-foundation system unbalance response.For this reason, rotor-support-foundation system is reduced to lump quality rotator model shown in Figure 3.With rotor-bearing system dynamic equilibrium condition and condition of compatible deformation: $\underset{j=1}{\overset{m}{\mathrm{\&Sigma;}}}\stackrel{-}{F_j}+\underset{i=1}{\overset{n}{\mathrm{\&Sigma;}}}\stackrel{-}{R_i}=0,\mathrm{\&Sigma;}\stackrel{-}{M_x}=0,\mathrm{\&Sigma;}\stackrel{-}{M_y}=0;\left[{\stackrel{-}{\mathrm{\&delta;}}}_{\mathrm{ij}}\right]\left\{{\stackrel{-}{R}}_i\right\}+\left\{{\stackrel{-}{S}}_{\mathrm{ip}}\right\}=\left\{{\stackrel{-}{X}}_{\mathrm{si}}\right\}---\left(3\right)$ And the transfer matrix that calculates the rotor-support-foundation system unbalance response: ${\left\{\stackrel{-}{Z}\right\}}_i={\left\{\stackrel{-}{T}\right\}}_{i-1}{\left[\stackrel{-}{T}\right]}_{i-2},\&CenterDot;\&CenterDot;\&CenterDot;,{\left[\stackrel{-}{T}\right]}_1\left[\stackrel{-}{P}\right]{\left\{\stackrel{-}{Z}\right\}}_1---\left(4\right)$ Calculate bearing dynamic force and vibration of supports amount, in the formula: F _jThe aequum U an of-Di j correcting plane _jThe inertial force that produces and since the rotor dynamic deformation cause

Additional uneven exciting force;

R _i-Di i indeterminate or static determinacy bearing dynamic anti-force;

M _x, M _yAll external force of-rotor and couple are respectively in the moment on ozy plane and ozx plane;

X _s-each bearing is at F _jVibratory output under the effect;

δ _IjFlexibility under the unit load of each relevant point of-rotor can be calculated by Mohr integration or transfer matrix method;

S _Ip-rotor unbalance inertial force also can be calculated by Mohr integration or transfer matrix method at the deformation values of each relevant point;

ω _k-Di k balancing speed: ${\left\{\stackrel{-}{Z}\right\}}_1=[\stackrel{-}{x},{\stackrel{-}{\mathrm{\&theta;}}}_y,{\stackrel{-}{M}}_y,{\stackrel{-}{\mathrm{\&theta;}}}_x,{\stackrel{-}{M}}_x,{\stackrel{-}{\mathrm{\&theta;}}}_y,l{]}_1^T$ --the initial state vector ${\left[\stackrel{-}{Z}\right]}_i=[\stackrel{-}{x},{\stackrel{-}{\mathrm{\&theta;}}}_y,{\stackrel{-}{M}}_y,{\stackrel{-}{\mathrm{\&theta;}}}_x,\stackrel{-}{y},{\stackrel{-}{\mathrm{\&theta;}}}_x,{\stackrel{-}{M}}_x,{\stackrel{-}{\mathrm{\&theta;}}}_y,l{]}_i^T$ --I cross section state vector ${\left[\stackrel{-}{T}\right]}_i={\left[\stackrel{-}{B}\right]}_i{\left[\stackrel{-}{D}\right]}_i$ ----disk and shaft part composition element transfer matrix

[B] _i--------no quality shaft part field battle array

[D] _i--------garden battle array of making an inventory

[P]--------initial matrix is used balance target equation peace treaty Shu Fangcheng again: $\max \left\{\right|{\stackrel{-}{\mathrm{\&epsiv;}}}_{\mathrm{si}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})\left|\right\}\&RightArrow;\min$ ${\stackrel{-}{\mathrm{\&epsiv;}}}_{\mathrm{si}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})={\stackrel{-}{X}}_{\mathrm{si}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})+{\stackrel{-}{X}}_{0i}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})$ $\left[{\stackrel{-}{K}}_d\right]\left\{{\stackrel{-}{x}}_s\right\}=\left\{\stackrel{-}{R^{\&prime;}}\right\}$ $\left[G_r\right]\left\{\stackrel{-}{x}\right\}+\left[C_r\right]\left\{\stackrel{\&CenterDot;}{x}\right\}+\mathrm{\&omega;}\left[J\right]\left\{\stackrel{\&CenterDot;}{x}\right\}+\left[K_r\right]\left\{x\right\}=\left\{F\right\}-\left\{R\right\}$ $\left\{{\stackrel{-}{F}}_j\right\}={\mathrm{\&omega;}}^2\left\{{\stackrel{-}{U}}_j\right\}$ Come computation optimization the best on selected correcting plane to become set of weights U, in the formula: X _OiThe original vibration of supports amount of----i bearing measuring point record;

X _SiVibration of supports amount behind the increasing the weight of of----i bearing measuring point record;

ε _SiThe remaining vibration of supports amount of----i bearing measuring point record;

I=1,2 ..., n,---bearing measuring point number;

K=1, ...,, K+1, K+2, K combined critical speed;

Rated speed under the K+1----zero load;

Rotating speed during the K+2----full load;

C=1,2 ..., the c operating condition, refer generally under the various loads and operating mode at full capacity steady in a long-term under;

The correcting plane number that m----is selected;

G _r----rotor quality;

The position angle of φ----supporting place measuring point;

U _j=m _jr _j--the aequum (mass-redius product) of correcting plane;

[G _r] the quality battle array of----rotor-support-foundation system;

[G _r] the damping battle array of----rotor-support-foundation system;

[K _r] Stiffness Matrix of----rotor-support-foundation system;

{ R}----bearing dynamic anti-force array; [the external force array of F}----rotor-support-foundation system;

The relevant matrix of flywheel moment of [J]----rotor-support-foundation system, J is an antisymmetric matrix, each element is a polar moment of inertia;

{x}, $\left\{\stackrel{\&CenterDot;}{x}\right\},\left\{\stackrel{\&OverBar;}{x}\right\}$ The vibratory output array of-rotor-support-foundation system; Wherein x} is a rotor vibration displacement response battle array, $\left\{\stackrel{\&CenterDot;}{x}\right\}$ Be rotor oscillation speed responsive battle array, { x} is a rotor oscillation acceleration responsive battle array;

The method of computation optimization is:

With known support system equivalence dynamic rigidity coefficient [K _d], just can adopt coordinate to rotate the direction search method by formula (5), constantly change F _j, { R} can obtain at { R ' } the vibration of supports amount that produced under the effect (watt shake) { X again by formula (2) to utilize aforementioned (3), (4) formula can obtain bearing dynamic anti-force _s, warp and the former { X that shakes ₀Superposition, can calculate residual oscillation amount { ε _Si, if be tending towards reducing, then continue this direction optimization, otherwise change F _jAnother coordinate direction respectively supports residual oscillation amount { ε until obtaining to make _SiThe optimum balance amount U that is all hour _j, each correcting plane is searched for down successively, until under the operating mode of selected plane, obtains the best set of weights value { U of one-tenth _j.

For this reason, all computing formula also need measure the position number of distance between each measuring point, each selected rectifying plane and increase the weight of radius, axle is the axial dimension of each section and the inside and outside footpath size of rotating shaft.

Then " the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery " of the present invention's proposition finished by following three steps at least:

The first step ties up to corresponding to V unbalanced rotor and axle _cPlant under the operating load situation, at selected ω _kUnder the rotating speed, selected under the situation of the position of correcting plane and number m, measured the original vibration of supports quantity of state of each bearing, said vibration of supports quantity of state comprises vibration of supports amount X _sWith bearing dynamic force R '; And original vibration of supports quantity of state is meant original vibration of supports amount X ₀With the dynamic R of original bearing ₀'; And be confirmed to be mass unbalance with conventional means;

Second step: according to each the original vibration of supports amount X that measures ₀With each the original bearing dynamic force R that measures ₀' substitution formula (2) calculates the accurate equivalent dynamic rigidity coefficient K of each bearing _d, the best of being obtained on the selected correcting plane by formula (3), (4), (5) becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing again _Si

The 3rd step: after selected plane adds the best set of weights U of one-tenth, measure the remaining vibration of supports amount ε of each bearing _SiLess than permissible value, balance finishes.

If the vibrational state amount of each measured bearing is only measured original vibration of supports amount X in the first step ₀, then second step just needed the original vibration of supports amount X according to each bearing of measuring ₀With a selected Approximate Equivalent dynamic rigidity coefficient K _d, calculate and on selected correcting plane, be approximated to set of weights U ₁, the 3rd step added at selected correcting plane and is approximated to set of weights U ₁After (as just increasing the weight of), measure the first vibration of supports amount X that increases the weight of of each bearing ₁, if X ₁Value is less than permissible value, and then balance finishes, if X ₁Value just need be carried out for the 4th step, according to each the original vibration of supports amount X that measures still greater than permissible value ₀With each the first vibration of supports amount X that increases the weight of that measures ₁Between variable quantity X _sCalculate the accurate equivalent dynamic rigidity coefficient K of each bearing _dThereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing _SiThe 5th step added the best set of weights U of one-tenth at selected correcting plane, measured the remaining vibration of supports amount ε of each bearing _SiLess than permissible value, balance finishes.

Approximate Equivalent dynamic rigidity coefficient K _dChoose optional one of the two kinds of situations of stating of taking off: the unit that [1] was crossed for former lack of equilibrium is to take to have same model unit in the database, and unit of the same type is once used accurate equivalent dynamic rigidity coefficient K on its balance history _dNumerical value, as the Approximate Equivalent dynamic rigidity coefficient, can obtain the scene with it and be balanced the rotation unit and on selected correcting plane, be approximated to set of weights U ₁, as just increasing the weight of.[2] for the unit of crossing with forward horizontal stand, (has a correcting plane position at least with its balance record, a balancing speed and two measuring point vibratory output change records), be balanced with formula (2), (3), (4), (5) scene of calculating and be approximated to set of weights U on the Approximate Equivalent dynamic rigidity coefficient of rotation unit relevant bearing and the selected correcting plane ₁, as just increasing the weight of.

The invention provides the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery, its functional-block diagram illustrates at Fig. 4, and it comprises conventional vibratory output sensor, vibration force sensor (404), eddy current head (405) and photometer head measuring elements such as (406); Vibration survey signal front processor (407)～(415) that the with dashed lines frame table shows; With a special-purpose principal computer (416); Wherein, special-purpose principal computer (416) has and vibration survey signal front processor special purpose interface, display or printer interface, and has a computing machine that comprises bearing dynamic force computing module (418), bearing equivalence dynamic rigidity coefficient computing module (419), becomes set of weights and remaining vibration of supports amount computing module (420) and exclusive data library management and maintenance program module four software modules such as (421), it can finish all calculating in the aforementioned equilibrium step according to program shown in Figure 5, and this computing machine is portable computer preferably.Its measuring-signal front processor is made up of attenuator (407), amplifier (408), shaping amplifier (409), wave filter (410), phase-locked loop circuit (411), analog to digital converter (412), central data processing single chip (413), RAM storage chip (414) and EPROM chip (415), and their single line connects the vibration of supports amount X that measures according to the vibratory output sensor _sCalculate bearing dynamic force R ' and utilize bearing dynamic force R ' data computing software that the vibration force sensor directly measures therein module admittedly; Bearing equivalence dynamic rigidity coefficient computing module is the original vibration of supports amount X that measures according to the vibratory output sensor that has according to formula (2) establishment ₀Value and the bearing dynamic force R ' value that calculates by bearing dynamic force computing module or be solidificated in wherein module with the software for calculation that bearing dynamic force R ' value that the vibration force sensor is directly measured calculates bearing equivalence dynamic rigidity coefficient;

Becoming set of weights and remaining vibration of supports amount computing module is that the original vibration of supports amount Xo value of measuring according to the vibratory output sensor according to having of formula (5) establishment, the numerical value of each bearing equivalence dynamic rigidity coefficient Kd, selected correcting plane position and number m and Vc kind operation conditions parameter come computation optimization to go out selecting the best that correcting plane need add to become the software for calculation of set of weights and remaining vibration of supports amount to be solidificated in wherein module; Exclusive data library management and maintenance program module are to have storage and call the structural parameters of various rotary machine rotor one supporting systems and the management of the accurate equivalent dynamic rigidity coefficient of each bearing of transient equilibrium history record and maintenance program are solidificated in wherein module.

Advantage of the present invention and beneficial effect are:

[1] balance quality height.Because the present invention has adopted the accurate equivalent dynamic rigidity coefficient and the optimized calculation method of bearing, has simplified measurements and calculations, improved the accuracy that calculating optimum becomes set of weights.Only survey the vibratory output and the dynamic force of bearing common-azimuth, become set of weights and precompute remaining vibration of supports amount, can both reach the good criteria of vibration permissible value with the straightforward computation optimization the best of accurate equivalent dynamic rigidity coefficient.

[2] do not need examination to increase the weight of.Be to calculate with the Approximate Equivalent dynamic rigidity coefficient to be approximated to set of weights, just can calculate best one-tenth set of weights, do not need calculating influence coefficient as just increasing the weight of the back for the first time.

[3] reduce the on-the-spot number of starts that is balanced unit effectively, shortened the balance duration.This method only need add and restarts 1～2 time, and promptly only need open, shut down 1～2 time, behind the 3rd step or the 5th step starting up, be the balance success.

Of the present invention applied widely, it both had been applicable to the transient equilibrium of rigid rotator and axle system thereof, was applicable to the transient equilibrium of flexible rotor and axle system thereof again; Can be used for hard bearing dynamic balancing machine, use in the transient equilibrium at the scene again, also can be used for the hot transient equilibrium of Turbo-generator Set.

Description of drawings:

Fig. 1: the kinetic model figure of rotor-supporting system

Among the figure: G _S1, G _S2, G _SnRepresent the 1 2nd and the mass of vibration of n bearing respectively, C _O1, C _O2, C _OnRepresent the 1 2nd and the equivalent oil-film damping coefficient of n bearing respectively, C _S1, C _S2, C _SnRepresent the 1 2nd and the equivalent basic ratio of damping of n bearing respectively, K _O1, K _O2, K _OnRepresent the 1 2nd and the equivalent oil film rigidity coefficient of n bearing respectively, K _S1, K _S2, K _SnRepresent the 1 2nd and the equivalent soil rigidity coefficient of n bearing respectively, ω _k----angular velocity of rotor during-balance, the azimuth view 2 on axis plane is crossed at φ-----measuring point place: the mechanical model figure of support system

Among the figure: K _d-bearing equivalence dynamic rigidity coefficient

X _sThe vibratory output of-bearing under R ' effect

Dynamic force Fig. 3 that R '-bearing bore: rotor-support-foundation system mechanical model figure

Among the figure: F _jAequum U on the-Di j correcting plane _jInertial force (the F that is produced _j=U _jω _k ²)

R ₁-Di i indeterminate or static determinacy bearing dynamic anti-force;

M-correcting plane number

N-bearing number

Fig. 4: rotating machinery dynamic poise device functional-block diagram

Among the figure: 401-is balanced rotor, and 402, the left and right supporting system of 403-,

The 404-vibration transducer, 405-eddy current head, the 406-photometer head,

The 407-attenuator, 408-amplifier, 409-shaping amplifier

The 410-wave filter, the 411-phase-locked loop circuit, the 412-analog to digital converter,

The 413-8098 single-chip microcomputer, the 414-RAM storage chip, the 415-EPROM chip,

The 416-principal computer, the 417-CRT display, the computing module of 418-bearing dynamic force,

The computing module of 419-bearing equivalence dynamic rigidity coefficient,

420-becomes the computing module of set of weights and residual oscillation amount,

421-whirler set type size equivalence dynamic rigidity coefficient increases the weight of the database management module of operating mode, Fig. 5: dynamic rigidity coefficient EQUILIBRIUM CALCULATION FOR PROCESS program master block diagram

The invention will be further described with embodiment below:

Embodiment 1, to the calculating that just increases the weight of on two rectifying planes of the Hebei first 9# of power plant genset (200MW) spreading axle, be before increasing the weight of when utilizing major overhaul balance of the same type, after the vibration change records, use these data, in special purpose computer of the present invention, calculate the Approximate Equivalent dynamic rigidity coefficient Kd of relevant bearing earlier, calculate the first weight on these two rectifying planes again, as a result, once increase the weight of success, the bearing residual oscillation amount of measuring is all superior under cold conditions and hot situation.

Embodiment 2, to the calculating that just increases the weight of on two rectifying planes of the northeast second 3# of power plant unit (200MW) spreading axle, it is used accurate equivalent dynamic rigidity coefficient when utilizing Hebei first power plant unit balance of the same type, Approximate Equivalent dynamic rigidity coefficient Kd as this unit, calculate and just increase the weight of, after adding, each vibration of supports amount of unit changes, and then shake and just increase the weight of the vibratory output of each bearing of back according to each bearing of this unit former, just can utilize the accurate equivalent dynamic rigidity coefficient that calculates each bearing of this unit in the special purpose computer of the present invention, with the best counterweight on these two rectifying planes, after adding, each vibration of supports of unit drops to below 30 microns by 59 microns, and secondary increases the weight of unit and reaches good vibration standard.

Embodiment 3, third 3# of the power plant unit (200MW), six rectifying planes in northeast (are pressed rotor low-pressure side rectifying plane P3 promptly, two rectifying plane J3 of spreading axle and J4, two rectifying plane L4 of low pressure rotor and L5, and low pressure rotor and generator amature shaft coupling rectifying plane L6) on the calculating that increases the weight of simultaneously, utilize the equivalent dynamic rigidity coefficient and the original vibration values of each bearing of this unit of the unit of being stored in the special purpose computer database of the present invention of the same type exactly, calculate the best counterweight on these six rectifying planes, once increase the weight of, each vibration of supports of unit as a result, drop to 17.2 microns by 30 microns, reach outstanding vibration standard.

Embodiment 4, and (hard supporting) carries out dynamic balance running to a 100MW rotor of steam turbo generator on large-scale flexible rotor dynamic balance running platform.Measure at first, simultaneously at the vibratory output X of measuring point on each bearing under the certain load operating mode, under certain balancing speed _sWith bearing dynamic force R ', then, the position dimension of four selected correcting planes is input in the special purpose computer of the present invention, very fast, this computing machine becomes set of weights through the best that the middle distance preface of Fig. 5 calculates on four correcting planes, and has estimated the remaining vibration of supports amount of each bearing, the result, once add restart, measure rotor, bearing residual oscillation amount is superior, balance finishes.

Claims (10)

1. dynamically balanced dynamic rigidity coefficient balance method of rotating machinery, it is characterized in that: the basis of its measurements and calculations is to set up a rotor-bearing system kinetic model, rotor-bearing system is divided into two subsystems, be rotor-support-foundation system and support system, two subsystems are set up the equation of motion of oneself respectively, its interphase is taken on rotor journal and the bearing bearing shell oil film surface of contact, therebetween by a pair of bonding force: { R}=-{R ' } relational expression of bearing dynamic anti-force R and bearing dynamic force R ' interrelates, and uses the vibration matrix equation of bearing: { K _d] { X _s}={ R ' } calculating bearing dynamic force R ', the accurate equivalent dynamic rigidity coefficient K of bearing _dAnd vibration of supports amount X _sBe characterized in: with an equivalent flexible damping support model, replaced four stiffness coefficients of anisotropy bearing and the bearing model of four ratio of damping, this Equivalent Elasticity damping support model only needs a stiffness coefficient and a ratio of damping, therefore, each vibration of supports amount X _sMeasuring point only need one, the measuring point of bearing dynamic force R ' also only needs one, these two measuring points must be placed on same the radial line of supporting-point; Measuring point on each bearing all will be placed on the plane of same axis excessively, and promptly its position angle is φ; Equivalence dynamic rigidity coefficient K _dIn (1) corresponding to V _cPlant under the operating load situation, (2) are at selected ω _kUnder the rotating speed, (3) have under the situation of definite selected correcting plane position and number m is a constant, with rotor-bearing system dynamic equilibrium condition and condition of compatible deformation: $\underset{j=1}{\overset{m}{\mathrm{\&Sigma;}}}{\stackrel{-}{F}}_j+\underset{i=1}{\overset{n}{\mathrm{\&Sigma;}}}{\stackrel{-}{R}}_i=0,\mathrm{\&Sigma;}{\stackrel{-}{M}}_x=0,\mathrm{\&Sigma;}{\stackrel{-}{M}}_y=0,\&lsqb;{\stackrel{-}{\mathrm{\&delta;}}}_{\mathrm{ij}}\&rsqb;\left\{{\stackrel{-}{R}}_i\right\}+\left\{{\stackrel{-}{S}}_{\mathrm{ip}}\right\}={\{\stackrel{-}{X}}_{\mathrm{si}}\},$ And the transfer matrix that calculates the rotor-support-foundation system unbalance response: ${\left\{\stackrel{-}{Z}\right\}}_i={\left\{\stackrel{-}{T}\right\}}_{i-1}{\&lsqb;\stackrel{-}{T}\&rsqb;}_{i-2},\&CenterDot;\&CenterDot;\&CenterDot;,{\left[\stackrel{-}{T}\right]}_1\left[\stackrel{-}{P}\right]{\left\{\stackrel{-}{Z}\right\}}_1$ Calculate bearing dynamic force and vibration of supports amount, use balance target equation again: $\max \left\{\right|{\stackrel{-}{\mathrm{\&epsiv;}}}_{\mathrm{si}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})\left|\right\}\&RightArrow;\min$ ${\stackrel{-}{\mathrm{\&epsiv;}}}_{\mathrm{si}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})=\stackrel{-}{X_{\mathrm{si}}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})+\stackrel{-}{X_{\mathrm{Oi}}}({\mathrm{\&omega;}}_k,V_c,m,\mathrm{\&phi;})$ $\left[\stackrel{-}{K_d}\right]\left\{\stackrel{-}{x_s}\right\}=\left\{\stackrel{-}{R^{\&prime;}}\right\}$ $\left[G_r\right]\left\{\stackrel{-}{x}\right\}+\left[C_r\right]\left\{\stackrel{\&CenterDot;}{x}\right\}+\mathrm{\&omega;}\left[J\right]\left\{\stackrel{\&CenterDot;}{x}\right\}+\left[K_r\right]\left\{x\right\}=\left\{F\right\}-\left\{R\right\}$ $\left\{\stackrel{-}{F_j}\right\}={{\mathrm{\&omega;}}^2}_k\left\{\stackrel{-}{U_j}\right\}$ Come computation optimization the best on selected correcting plane to become set of weights U, in the formula: F _jThe inertial force that aequum U produced an of-Di j correcting plane and since the rotor dynamic deformation cause

Additional uneven exciting force;

R _i-Di i indeterminate or static determinacy bearing dynamic anti-force;

M _x, M _yAll external force of-rotor and couple are respectively in the moment on ozy plane and ozx plane;

X _s-each bearing is at F _jVibratory output under the effect;

δ _jFlexibility under the unit load of each relevant point of-rotor can be calculated by Mohr integration or transfer matrix method;

S _1P-rotor unbalance inertial force also can be calculated by Mohr integration or transfer matrix method at the deformation values of each relevant point;

K balancing speed of ak-. ${\left\{\stackrel{-}{Z}\right\}}_1=[\stackrel{-}{x},\stackrel{-}{{\mathrm{\&theta;}}_y},\stackrel{-}{M_y},\stackrel{-}{{\mathrm{\&theta;}}_x},\stackrel{-}{y},\stackrel{-}{{\mathrm{\&theta;}}_x},\stackrel{-}{M_x},\stackrel{-}{{\mathrm{\&theta;}}_y},l{]}_1^T$ ---the initial state vector ${\left[\stackrel{-}{Z}\right]}_1=[\stackrel{-}{x},\stackrel{-}{{\mathrm{\&theta;}}_y},\stackrel{-}{M_y},\stackrel{-}{{\mathrm{\&theta;}}_x},\stackrel{-}{y},\stackrel{-}{{\mathrm{\&theta;}}_x},\stackrel{-}{M_x},\stackrel{-}{{\mathrm{\&theta;}}_y},l{]}_1^r$ ---I cross section state vector ${\left[\stackrel{-}{T}\right]}_1={\left[\stackrel{-}{B}\right]}_i{\left[\stackrel{-}{D}\right]}_i$ ---disk and shaft part composition element transfer matrix

[B] _i--------no quality shaft part field battle array

[D] _i--------garden battle array of making an inventory

[P]--------initial matrix

X _OiThe original vibration of supports amount of----i bearing measuring point record;

X _SiVibration of supports amount behind the increasing the weight of of----i bearing measuring point record;

ε _SiThe remaining vibration of supports amount of----i bearing measuring point record;

I=1,2 ..., n,---bearing measuring point number;

K=1 ..., K+1, K+2, K combined critical speed;

Rated speed under the K+1----zero load;

Rotating speed during the K+2----full load;

C=1,2 ..., the c operating condition, refer generally under the various loads and operating mode at full capacity steady in a long-term under;

The correcting plane number that m----is selected;

G _r----rotor quality;

The position angle of φ----supporting place measuring point;

U _j=m _jr _j--the aequum (mass-redius product) of correcting plane;

[G _r] the quality battle array of----rotor-support-foundation system;

[C _r] the damping battle array of----rotor-support-foundation system;

[K _r] Stiffness Matrix of----rotor-support-foundation system;

{ R}----bearing dynamic anti-force array; { the external force array of F}----rotor-support-foundation system;

The relevant matrix of flywheel moment of [J]----rotor-support-foundation system, J is an antisymmetric matrix, each element is a polar moment of inertia; { x}, { x}, { the vibratory output array of x}-rotor-support-foundation system; Wherein x} is a rotor vibration displacement response battle array, $\left\{\stackrel{\&CenterDot;}{x}\right\}$ Be rotor oscillation speed responsive battle array, $\left\{\stackrel{\&CenterDot;}{x}\right\}$ It is rotor oscillation acceleration responsive battle array;

Like this, the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery is finished by following three steps at least:

The first step: measure the original vibration of supports quantity of state of each bearing in unbalanced rotor and the axle system, said vibration of supports quantity of state comprises vibration of supports amount X _sWith bearing dynamic force R '; And original vibration of supports quantity of state is meant original vibration of supports amount X ₀With original bearing dynamic force R ₀'; And be confirmed to be mass unbalance with conventional means;

Second step: according to each the original vibration of supports amount X that measures ₀With each the original bearing dynamic force R that measures ₀' calculate the accurate equivalent dynamic rigidity coefficient K of each bearing _dThereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing _Si

The 3rd step: after selected plane adds the best set of weights U of one-tenth, measure the remaining vibration of supports amount ε of each bearing _SiLess than permissible value, balance finishes.

2, the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery as claimed in claim 1, its feature: the vibrational state amount of each measured bearing is only measured original vibration of supports amount X in the first step ₀, then second step just needed the original vibration of supports amount X according to each bearing of measuring ₀With a selected Approximate Equivalent dynamic rigidity coefficient K _d, calculate and on selected correcting plane, be approximated to set of weights U ₁, the 3rd step added at selected correcting plane and is approximated to set of weights U ₁After (as just increasing the weight of), measure the first vibration of supports amount X that increases the weight of of each bearing ₁, if X ₁Value is less than permissible value, and then balance finishes, if X ₁Value just need be carried out for the 4th step, according to each the original vibration of supports amount X that measures still greater than permissible value ₀With each the first vibration of supports amount X that increases the weight of that measures ₁Between variable quantity X _sCalculate the accurate equivalent dynamic rigidity coefficient K of each bearing _dThereby the best of obtaining on the selected correcting plane becomes set of weights U and the remaining vibration of supports amount ε that precomputes each bearing _Si: the 5th step added the best set of weights U of one-tenth at selected correcting plane, measured the remaining vibration of supports amount ε of each bearing _SiLess than permissible value, balance finishes.

3, the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery as claimed in claim 1, it waits to levy: Approximate Equivalent dynamic rigidity coefficient K _dBe to take to have same model unit in the database, unit of the same type once used accurate equivalent dynamic rigidity coefficient K on its balance history _dNumerical value, can obtain the scene with it and be balanced the rotation unit and on selected correcting plane, be approximated to set of weights U ₁, as just increasing the weight of.

4, the dynamically balanced dynamic rigidity coefficient balance method of rotating machinery as claimed in claim 1, it is held to levy and is: all calculation procedures also need be measured the distance between each measuring point, the position of each selected rectifying plane and increase the weight of radius, axle be the axial dimension of each section and rotating shaft in, outside dimension.

5, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery is characterized in that: it comprises conventional vibratory output sensor, vibration force sensor (404), eddy current head (405), and photometer head measuring elements such as (406); A vibration survey signal front processor (407)～(415); With a special-purpose principal computer (416); Wherein special purpose computer (416) has and vibration survey signal front processor special purpose interface, display interface device, printer interface, and has a computing machine that comprises bearing dynamic force computing module (418), bearing equivalence dynamic rigidity coefficient computing module (419), becomes set of weights and remaining vibration of supports amount computing module (420) and exclusive data library management and maintenance program module four software modules such as (421)

6, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery as claimed in claim 5, it is characterized in that: its measuring-signal front processor is by attenuator (407), amplifier (408), shaping amplifier (409), wave filter (410), phase-locked loop circuit (411), analog to digital converter (412), central data processing single chip (413), RAM storage chip (414) and EPROM44 chip (415) are formed, their single line annexation is: the one tunnel is that attenuator (407) connects shaping amplifier (409) and connects phase-locked loop circuit (411) and connect analog to digital converter (412) and be connected to central data processing single chip (413): the same amplifier (408) of two-way connects wave filter (410) and is connected to central data processing single chip (413) in addition, and two feedback lines of central data processing single chip (413) are connected to two amplifiers (408) respectively; The two other line of phase-locked loop circuit (411) is connected to respectively on two wave filters (410); RAM storage chip (414) has bidirectional cable and central data processing monolithic telephone-moving (413) to be connected respectively with EPROM chip (415); On two amplifiers (408), there is vibration to pass the interface of vessel (404), the interface that eddy current head (405) are arranged on attenuator (407), the interface that photometer head is arranged on shaping amplifier (409) has the interface that links to each other with private host calculation machine on central data processing single chip (413).

7, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery as claimed in claim 5 is characterized in that: the computing module (418) of bearing dynamic force R ' is to have the vibration of supports amount X that measures according to the vibratory output sensor ₀Calculate bearing dynamic force R ' and utilize bearing dynamic force R ' data computing software that the vibration force sensor directly measures therein module admittedly.

8, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery as claimed in claim 5 is characterized in that: bearing equivalence dynamic rigidity coefficient computing module (419) is to have the original vibration of supports amount X that measures according to the vibratory output sensor ₀Value and the bearing dynamic force R ' value that calculates by bearing dynamic force computing module or be solidificated in wherein module with the software for calculation that bearing dynamic force R ' value that the vibration force sensor is directly measured calculates bearing equivalence dynamic rigidity coefficient.

9, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery as claimed in claim 5 is characterized in that: becoming set of weights and remaining vibration of supports amount computing module (420) is to have the original vibration of supports amount X that measures according to the vibratory output sensor ₀Value, each bearing equivalence dynamic rigidity coefficient K _dNumerical value, selected correcting plane position and number m and V _cKind of operation conditions parameter comes computation optimization to go out the best that need add at selected correcting plane to become the software for calculation of set of weights and remaining vibration of supports amount to be solidificated in wherein module.

10, the dynamically balanced dynamic rigidity coefficient balance device of a kind of rotating machinery as claimed in claim 5 is characterized in that: exclusive data library management and maintenance program module (421) are to have storage and call the structural parameters of various rotary machine rotor one supporting systems and the management of the accurate equivalent dynamic rigidity coefficient of each bearing of transient equilibrium history record and maintenance program are solidificated in wherein module.

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