CN1400454A - Holographic dynamic balancing method of flexible rotor shaft system - Google Patents
Holographic dynamic balancing method of flexible rotor shaft system Download PDFInfo
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Abstract
The invention is an axis-series holographic dynamic-balance method in the rotary mechanical-vibration diagnosis and control field. The method is based on the theory of holographic-chart information integration and on the base of getting all the sensor-vibration information on each rotor, integrates the vibration's breadth, frequency and phase information in each supporting place, and fully describes the axis-series vibration behavior in three-dimensional holographic-chart mode, and according to this, appraises the axis-series unbalance status and the adapted-weight effect, and puts forward a set of project applied to the holographic dynamic-balance of multiple-supporting axis series made up of multiple flexible rotors and then uses the computer to realize the optimization to the balance result.
Description
One, affiliated field
The invention belongs to the dynamic balancing technique in rotary machinery fault diagnosis and control field, relate to a kind of holographic dynamic balancing method of flexible rotor shaft system, be mainly used in transient equilibrium the multi-support axle system that forms by a plurality of flex rotors in the rotating machinery.
Two, background technology
Dynamic balance method and Study on Technology are important topics in this field always.About dynamically balanced theoretical research, major part still is in the dynamic balance method of double base single rotor and Study on Technology at present, and is also less to the research of whole shafting vibration, behavior and balance method thereof.The structure of rotating machinery is essentially the axle system of multispan supporting, many rotors form in the pillar industry in national economy actual productions such as electric power, chemical industry, petrochemical industry, and the balance that is for whole axle has just become a problem that urgency is to be solved.For the balance that realizes that whole axle is, people have carried out a large amount of exploration and practices.The method of using is at first to carry out transient equilibrium respectively at each rotor in the axle system at present, and then the rotor that balance is good links up.Owing to reasons such as alignment error, shafting alignments, by the good rotor of above method balance, necessarily balance is fine after they are connected as one respectively.Because the complicacy of shafting vibration behavior, adopt digital modeling to calculate to tend to produce big sum of errors approximate.For the shafting dynamic balance problem in the production is solved, people's experience has just become one uniquely can utilize means.Therefore, often need spend a huge sum of money and a large amount of time for producing the balance that goes up axle system.Even carry out spot dynamic balance owing to rely on experience fully, make the transient equilibrium effect of axle system that very big randomness arranged, finishing a transient equilibrium sometimes needs surplus the cycling start ten time, may produce the balance failure sometimes.Because the balance of axle system needs expert's experience and a large amount of artificial participation, therefore, the process that still a kind of basically manual repeatedly examination under theory instructs of the transient equilibrium of axle system is gathered.
About the balance method of single rotor, on principle, can be divided into two big classes: modal balancing method and influence coefficient method at present.The modal balancing method at first will be known the parameters such as overall vibration mode of whole system, all is very difficult by the still actual test of Modeling Calculation.Therefore in actual transient equilibrium, still adopted single rotor has been carried out dynamic balance method.Influence coefficient method needs a repeated multiple times to increase the weight of the process of test run.The influence coefficient matrix that reflects that test mass to whole axle is will be tried to achieve by flexible shaft system for many rotors, multi-support, owing to need repeatedly test run will become difficult more.Owing to have difficulties in the real balance, also have at last get back on the influence coefficient method of single rotor.
" rotor holographic dynamic balance method " (referring to Chinese invention patent ZL97108694.X) and disclosed Chinese invention patent " asymmetrical rotor holographic dynamic balance technology " (application number 00113755.7), respectively holographic spectral technology and information theory principle are applied to dynamic balance field, by information integration, realized the holographic dynamic balance of symmetry and asymmetrical rotor.Above method has all realized the breakthrough of dynamic balancing technique aspect balance quality of rotor and balance efficiency two.
Three, summary of the invention
The present invention is intended to the theory with flex rotor holographic dynamic balance method and technology, promotes and widen the balance of the flexible shaft system of a plurality of rotors compositions, makes it can be used in the balance of the axle system of many rotors, multi-support.Method and technology in above-mentioned two patents have been carried out the vibration signal of rotor the integrated fusion of information in same measuring point cross section.The present invention will be further spatially forms the 3D hologram spectrum that can complete, comprehensively reflect the shafting vibration behavior along carrying out integrated fusion on axle is the direction of rotating shaft.Realize the balance of axle system and balance result's optimization on this basis.
A balance that the objective of the invention is to the axle system that forms for multispan supporting, many rotors provides a kind of directly perceived, science, holographic dynamic balancing method of flexible rotor shaft system fast and effectively.This method is based on the integrated principle of holographic spectrum information, on the basis that obtains all sensors vibration information on the rotor, the amplitude-frequency phase information of integrated each supporting place vibration, the vibration behavior of many rotors, multi-support axle system is described and is reflected all sidedly in the mode of 3D hologram spectrum, and with this as estimating the foundation that axle is out-of-balance conditions and test mass influence, and then realize shafting balancing and shafting balancing result's optimization.
To achieve these goals, the technical scheme that the present invention takes is: the multi-support axle system that is made up of flex rotor is the general version of rotary machine rotor-supporting system, the balance of axle system is different from the balance of general double base rotor, holographic dynamic balancing method of flexible rotor shaft system of the present invention, its characteristics may further comprise the steps:
1) at first will obtain the composition axle is the vibration signal at each rotor bearing place, is instrument with holographic analysis of spectrum, distinguishes the out-of-balance conditions of each rotor in the axle system, determines that unbalance fault is leading fault in the system; Distinguish power frequency vibration unbalance and that other reason causes;
2) by field balancing process of tracking or dynamics calculation, definite counterweight that respectively increases the weight of on the face is measured the influence of face to each, and represents with the form of 3D hologram spectrum;
3) eliminate the operating load influence, decomposite the influence of each counterweight by linear operation, finally obtain and load irrelevant, by the single counterweight 1000g/0 ° of 3D hologram that causes spectrum and transition matrix thereof;
Transition matrix is the normalization matrix that the influence matrix of single counterweight on certain counterweight face calculates by angle rotation and vector convergent-divergent.
4) find out balanced surface to each supporting place vibration effect maximum, principle by first phase point minute surface symmetry, determine the direction of counterweight on each balanced surface, with its size of genetic algorithm optimization, its objective function should make the average vibratory response minimum of supporting place, make the vibratory response difference of each supporting place as far as possible little simultaneously, the two is taken into account;
5) to the residual oscillation of supporting place, repeat 4 operation (can repeatedly), the size with genetic algorithm optimization secondary counterweight reduces the vibratory response of each supporting place as far as possible,
Determine on each balanced surface the size of total counterweight and position on the balanced surface circumference (with key mutually groove be benchmark);
6) on computers selected counterweight size and phase place are carried out manual fine-tuning, determine the most rational counterweight scheme.
7) add selected counterweight, test the result who increases the weight of once more, as the balance that meets the demands finishes; Otherwise repetition above-mentioned steps.
Another characteristics of the present invention are that described holographic analysis of spectrum is:
(a) to the holographic dynamic balance of many rotors, multi-support axle system with the 3D hologram analysis of spectrum as the basis, adopt N balancing plane, come the vibration of balance N+1 supporting place, wherein N+1＞2;
(b) in balancing run, each counterweight is handled in the mode that concerns of linearity the influence of shafting vibration;
(c) concern with the symmetry of the minute surface between 2 first phase points is secondary on the formed ellipse of original vibration and on the formed ellipse of counterweight, be used as seeking the foundation that makes things convenient for of optimum balance scheme;
(d) in the equilibrium process, utilize each counterweight to offset the most unbalance vibration of relevant supporting place of vibration respectively, N+1 supporting place vibration subdued automatically, and make axle system reach satisfied counterbalance effect generally;
(e) the 3D hologram spectral technology is applied to shafting balancing, thereby reflects vibrational state, equilibrium process and the counterbalance effect of axle system intuitively, all sidedly;
(f) utilize computer mould to fit the software fine setting on balance is implemented, what substituted field apparatus repeatedly plays the parking balance test, has realized the contrast and the optimization of multiple balance scheme on computers.
Holographic dynamic balancing method of flexible rotor shaft system of the present invention, based on the integrated principle of holographic spectrum information, on the basis that obtains all sensors vibration information on each rotor, the width of cloth of integrated each supporting place vibration, frequently, phase information, the vibration behavior of axle system is described all sidedly in the mode of 3D hologram spectrum, and with this as estimating the foundation that axle is out-of-balance conditions and counterweight influence, proposed a whole set ofly to be applicable to multi-support, what is made up of a plurality of flex rotors spool is the holographic dynamic balance scheme, and then with computer realization balance result's optimization.
Four, description of drawings
Fig. 1 is genset (330MW) structural representation; Wherein (a) is the set structure sketch, and the A that (b) is (a) is to view;
Fig. 2 is the original vibration 3D hologram spectrum synoptic diagram of unit;
Fig. 3 is that the A balanced surface increases the weight of the vibration effect 3D hologram spectrum synoptic diagram to unit;
Fig. 4 is that the B balanced surface increases the weight of the vibration effect 3D hologram spectrum synoptic diagram to unit;
Fig. 5 is that the C balanced surface increases the weight of the vibration effect 3D hologram spectrum synoptic diagram to unit;
Fig. 6 is the vibration variable quantity of original cycling start to test mass cycling start 3---calculated value 3D hologram spectrum synoptic diagram;
Fig. 7 is the vibration variable quantity of original cycling start to test mass cycling start 3---actual value 3D hologram spectrum synoptic diagram;
Fig. 8 is the vibration variable quantity of test mass cycling start 1 to test mass cycling start 4---calculated value 3D hologram spectrum synoptic diagram;
Fig. 9 is the vibration variable quantity of test mass cycling start 1 to test mass cycling start 4---actual value 3D hologram spectrum synoptic diagram;
Figure 10 is that A balanced surface counterweight is adjusted 478/-74.5 3D hologram spectrum synoptic diagram for the first time;
Figure 11 is that A balanced surface counterweight is adjusted (478/-74.5+370/-175) 3D hologram spectrum synoptic diagram for the second time;
Figure 12 is that B balanced surface counterweight is adjusted 425/15 3D hologram spectrum synoptic diagram for the first time;
Figure 13 is that B balanced surface counterweight is adjusted 937/-60 3D hologram spectrum synoptic diagram for the second time;
Figure 14 is that C balanced surface counterweight is adjusted 1088/62 3D hologram spectrum synoptic diagram;
Figure 15 is the self-equilibrating phenomenon verification synoptic diagram that 2 watts are located in the spot dynamic balance process;
Figure 16 adjusts A face counterweight, makes 1 watt of test mass vibration become the secondary 3D hologram spectrum of mirror image synoptic diagram with original vibration first phase point;
Figure 17 is that simulation obtains the unit vibration 3D hologram spectrum synoptic diagram after A face counterweight applies;
Figure 18 adjusts B face counterweight, makes 3 watts of test mass vibrations become the secondary 3D hologram spectrum of mirror image synoptic diagram with original vibration first phase point;
Figure 19 is that simulation obtains the unit vibration 3D hologram spectrum synoptic diagram after B face counterweight applies;
Figure 20 adjusts C face counterweight, makes 4 watts of test mass vibrations become the secondary 3D hologram spectrum of mirror image synoptic diagram with original vibration first phase point;
Figure 21 is that simulation obtains the unit vibration 3D hologram spectrum synoptic diagram after C face counterweight applies;
Figure 22 is the counterweight stack with three faces of front gained, obtains the vibration 3D hologram spectrum synoptic diagram of rotor under three counterweight actings in conjunction;
Figure 23 is that axle is a relatively 3D hologram spectrum synoptic diagram of holographic dynamic balance fine setting effect on transient equilibrium effect and the computing machine;
Figure 24 is to use self-equilibrating phenomenon synoptic diagram in the transient equilibrium process that method of the present invention carries out.
Five, embodiment
For a more clear understanding of the present invention, the present invention is described in further detail below in conjunction with drawings and Examples.
Need to prove that it is spot dynamic balance that the present invention is mainly used in the rotary machine axle, also can be used for the off-line equilibrator transient equilibrium that is that many rotors are formed certainly.Both principles are the same.Be that spot dynamic balance is that example describes with axle below:
According to technical scheme of the present invention, following step is necessary.
(1) at first will obtain the composition axle is the vibration signal at each rotor bearing place, is instrument with holographic analysis of spectrum, distinguishes the out-of-balance conditions of each rotor in the axle system, determines that unbalance fault is leading fault in the system.Distinguish power frequency vibration unbalance and that other reasons causes.
(2) on the basis of the above work, all that determine shafting dynamic balance increase the weight of face.
(3) by field balancing process of tracking or dynamics calculation, definite counterweight that respectively increases the weight of on the face is measured the influence of face to each, and represents with the form of 3D hologram spectrum.
(4) eliminate the operating load influence, decomposite the influence of each counterweight by linear operation, finally obtain and load irrelevant, by the single counterweight 1000g/0 ° of 3D hologram that causes spectrum and transition matrix thereof;
During concrete computation migration matrix, at first the influence matrix to each counterweight face carries out linear scale, and making the counterweight size normalization is 1000g, makes the influence matrix angle be normalized to 0 degree by angle rotation and compensation again.
5) find out balanced surface to each supporting place vibration effect maximum, principle by first phase point minute surface symmetry, determine the direction of counterweight on each balanced surface, with its size of genetic algorithm optimization, its objective function should make the average vibratory response minimum of supporting place, make the vibratory response difference of each supporting place as far as possible little simultaneously, the two is taken into account;
6) to the residual oscillation of supporting place, repeat 4 operation (can repeatedly), the size with genetic algorithm optimization secondary counterweight reduces the vibratory response of each supporting place as far as possible,
Determine on each balanced surface the size of total counterweight and position on the balanced surface circumference (with key mutually groove be benchmark);
7) on computers selected counterweight size and phase place are carried out manual fine-tuning, determine the most rational counterweight scheme.
8) add selected counterweight, test the result who increases the weight of once more, as the balance that meets the demands finishes; Otherwise repetition above-mentioned steps.
Embodiment: it is example that the following inventor of being adopts the given spot dynamic balance with certain METHOD FOR TURBOGENERATOR SET of this method, and applicability and the validity of this method to the axle system of many flex rotors of reality multi-support has been described.
One), set structure sketch and sensor scheme of installation
Referring to genset shown in Figure 1 (330MW) structural representation, there is shown set structure sketch and sensor scheme of installation, wherein (a) is the set structure sketch, the A that (b) is (a) is to view.
Two), unit equilibrium process and vibration data
This transient equilibrium is carried out transient equilibrium by increasing the weight of to the high pressure rotor on three counterweight faces shown in Figure 1.Equilibrium process such as table 1 are listed:
Table 1. unit equilibrium process
| Balanced surface A | Balanced surface B | Balanced surface C | Vibration data | |
| Original vibration | ????0 | ????0 | ????0 | Table 2 |
| Test | ????478g/-74.5 | ????425g/15 | ????0 | Table 3 |
| Test | Constant | Constant | ???1088/62 | Table 4 |
| Test | Constant | ????937g/-60 | Constant | Table 5 |
| Test | Add 370g/-175 again | Constant | Constant | Table 6 |
| The full power cycling start | Constant | Constant | Constant | Table 7 |
Each time cycling start vibration data and operating mode are listed in table 2～table 7.
Table 2. increases the weight of preceding (3000rpm is zero load) fundamental vibration situation
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????116.5 | ????136 |
| ????Y | ????64 | ????28 | |
| ????2 | ????X | ????52 | ????114 |
| ????Y | ????79 | ????65 | |
| ????3 | ????X | ????117 | ????110 |
| ????Y | ????110 | ????18 | |
| ????4 | ????X | ????49 | ????-84 |
| ????Y | ????18.5 | ????176 |
Table 3. test mass cycling start (3000rpm is zero load) for the first time fundamental vibration situation
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????86 | ????117 |
| ????Y | ????55 | ????16 | |
| ????2 | ????X | ????95 | ????107 |
| ????Y | ????91 | ????37 | |
| ????3 | ????X | ????170 | ????92 |
| ????Y | ????136 | ????2 | |
| ????4 | ????X | ????105 | ????-116 |
| ????Y | ????49 | ????142 |
Table 4. test mass cycling start (3000rpm is zero load) for the second time fundamental vibration situation
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????104 | ????62 |
| ????Y | ????53 | ????-14 | |
| ????2 | ????X | ????123 | ????135 |
| ????Y | ????121 | ????36 | |
| ????3 | ????X | ????152 | ????115 |
| ????Y | ????123 | ????11 | |
| ????4 | ????X | ????28 | ????-127 |
| ????Y | ????21 | ????83 |
Table 5. test mass cycling start for the third time (3000rpm is zero load) fundamental vibration situation
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????128 | ????86 |
| ????Y | ????66.1 | ????2 | |
| ????2 | ????X | ????64 | ????-174 |
| ????Y | ????61.7 | ????70 | |
| ????3 | ????X | ????50 | ????141 |
| ????Y | ????62.4 | ????22 | |
| ????4 | ????X | ????46 | ????110 |
| ????Y | ????35 | ????20 |
The 4th test mass cycling start of table 6. (3000rpm 45MW) fundamental vibration situation
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????92.8 | ????100 |
| ????Y | ????55.5 | ????22 | |
| ????2 | ????X | ????36.6 | ????170 |
| ????Y | ????49 | ????57 | |
| ????3 | ????X | ????35.7 | ????101 |
| ????Y | ????58.6 | ????11 | |
| ????4 | ????X | ????35 | ????129 |
| ????Y | ????20.5 | ????39 |
Full power cycling start (3000rpm 300MW) fundamental vibration situation behind the 4th test mass of table 7.
| Bearing number | Sensor | Fundamental frequency amplitude (um) | Fundamental frequency phase place (deg.) |
| ????1 | ????X | ????64.2 | ????68 |
| ????Y | ????57.4 | ????-56 | |
| ????2 | ????X | ????19.2 | ????139 |
| ????Y | ????36.3 | ????34 | |
| ????3 | ????X | ????49.6 | ????82 |
| ????Y | ????78.8 | ????-9 | |
| ????4 | ????X | ????54.9 | ????104 |
| ????Y | ????37.2 | ????25 |
Three), the elimination of load influence and test mass influence finds the solution
The original vibration of unit as shown in Figure 2.By spectrogram as can be known the high pressure rotor all have imbalance, and couple unbalance is comparatively outstanding on the middle pressure rotor.Therefore, the purpose of current spot dynamic balance is by progressively adjusting A, B, and weight mass on three balanced surfaces of C reduces by four original vibrations in bearing shell place.First step study
Follow the tracks of the dynamically balanced overall process of a deuterzooid unit, from all previous parking of test mass increase and decrease, the transition matrix ra of 3D hologram spectrum when determining on balanced surface A, B, C, to apply counterweight respectively, rb and rc, and the initial vibration matrix r q0 of ready to balance and matrix of loadings rload.
It is 1000 grams that transition matrix should be converted to counterweight weight, and the phasing degree is the canonical form of 0 degree.Should in initial vibration matrix r q0, reject effects of load.
Fig. 3～Fig. 5 is the 3D hologram spectrogram that when applying counterweight on balanced surface A, B, C unit vibration is influenced.
Observe the holographic spectrogram of this three width of cloth, we can see:
1. counterweight is no matter on which balanced surface, and is opposite substantially to the vibration effect direction of two ends of rotor, promptly mainly influences the vibration of rotor in the couple mode.Identical to high pressure rotor with middle this rule of pressure rotor;
2.2 watt and 3 watts between be positive coupling, and the connection situation is better.The vibration effect at visible shaft coupling two ends always keeps substantially in the same way from the holographic spectrum of 3 width of cloth, and the vibration effect amplitude is also consistent;
3. three Weights holographic spectral shape that each watt located vibration effect is all comparatively normal, illustrates that rotor one bearing arrangement does not have other big accident defects, can expect to reduce vibration by transient equilibrium, guarantees to produce.The second step linear process
It is to carry out under the prerequisite of linear relationship that rotor axial system is carried out holographic dynamic balance.Linear processing methods is the resultant vibration that whole counterweights produce on each balanced surface of rotor, equals the independent vibration sum that each counterweight produces on rotor.Therefore, in linear system, should have
F (x, y, z ...)=f (x)+f (y)+f (z)+... relation.The linear relationship of shafting vibration also can be found out by following calculating.
As shown in Table 1, from original cycling start to the test mass cycling start on 3, three balanced surfaces counterweight all change.We can use the standardization counterweight vibration effect of gained in the first step, obtain the calculated value of vibration variable quantity according to linear relationship ratio stack, also can be directly deduct original cycling start and vibrate the actual value of trying to achieve this variable quantity with the vibration of test mass cycling start 3 from original cycling start to 3 four cross sections of test mass cycling start.Both respectively as shown in Figure 6 and Figure 7;
Comparison diagram 6 and Fig. 7 are that the vibration amplitude or the vibration first phase point phase place of each watt is all very approaching, have good accuracy.Obviously, linear hypothesis is set up, and promptly the resultant vibration that whole counterweights produce on each balanced surface of rotor equals the independent vibration sum that each counterweight produces substantially on rotor.Certainly, not exclusively equate, but error is very little, very accurate to spot dynamic balance.This just makes us holographic dynamic balance method can be applied in the transient equilibrium of on-the-spot big unit and goes.
The linear hypothesis of holographic dynamic balance has repeatable.Know that by table 14 from test mass cycling start 1 to the test mass cycling start, the counterweight of each balanced surface also all changes.Be not difficult to find out this point by simple computation.The result is referring to Fig. 8 and Fig. 9.The 3rd step computer simulation
Because in the real balance, the orientation of counterweight and size can not be accurate to result of calculation in full accord, in equilibrium process, have the restriction of environmental factor again, therefore, also need on aforementioned calculation result's basis, select the most satisfied scheme with computer simulation.The purpose of computer simulation: the one, utilize the 3D hologram spectrum parameter matrix and the initial vibration matrix that are obtained, by computer simulation, make spot dynamic balance reach the most satisfied effect easily; The 2nd, reduce the test cycling start in the shafting balancing, save a large amount of manpower and materials.
The ultimate principle of holographic dynamic balance is:
1. phase shift ellipse;
2. (IPP) is the mirror image relation between the first phase point that original vibration is oval and the first phase point of counterweight ellipse.
Know that by table 1 counterweight on the A balanced surface was done twice adjustment.Twice counterweight influence is compared with original vibration, as shown in Figure 10 and Figure 11.
By Figure 10 and Figure 11 as seen, based on the ultimate principle of holographic dynamic balance: (IPP) is the mirror image relation between the first phase point of the first phase point of original vibration ellipse and counterweight ellipse.A face counterweight is being carried out in the adjustment process, and the inherent target of adjusting is to make A interview ghost image ring the first phase point reverse side that oval first phase point is positioned at original vibration, and this target external manifestation is reduced for this face place vibration.
According to the thought of holographic dynamic balance, B balanced surface (counterweight is adjusted twice) and C balanced surface (the counterweight adjustment once) are also adjusted with above-mentioned target equally.Wherein, B face counterweight is adjusted with reference to 3 watts of vibrations, and does not consider 2 watts, locate to vibrate and be reduced, and for 2 watts so? next step will be analyzed this.The influence of the counterweight of B, C face and original vibration are relatively referring to Figure 12～shown in Figure 14.Self-equilibrating in the 4th step holographic dynamic balance
So-called self-equilibrating is meant: by adjusting the position and the size of counterweight on three balanced surfaces, eliminated the vibration on three bearing cross sections one by one, then the vibration on the 4th bearing cross section can be eliminated automatically.
In the at first transient equilibrium process, 2 watts of vibrations of locating reduce process, i.e. self-equilibrating phenomenon.As described in the 3rd step, be after target has been adjusted the counterweight of three balanced surfaces to reduce by 1,3,4 watts of vibrations, three counterweights are seen Figure 15 in the vibration sum of 2 watts of formation and the relation of 2 watts of original vibrations:
As seen, the vibration sum of three counterweight formation is opposite with original direction of vibration, can offset original about vibration of about 60%.The holographic dynamic balance method that the 5th step axle is
Axle is that holographic dynamic balance method is made balance to unit, also self-equilibrating can occur.Regulate the size and the phase place of counterweight on three balanced surfaces, make the first phase point of vibration ellipse on each bearing cross section become the mirror image pair with the formed first phase point of corresponding counterweight, with one by one, eliminate vibration on these three bearing cross sections respectively, at this moment, the energy of vibration on the 4th bearing cross section is eliminated automatically.Whole process can realize on computers.
Because the vibration at certain bearing place is excessive unit is caused the danger of damage or jumping car when this method can avoid the face that pursues to adjust counterweight one by one, and can once find three comparatively suitable counterweights of face to distribute.
During practical operation, use the vibration effect of first step gained, adjust counterweight size position by face, eliminate 3 bearing shell place vibrations successively, each time result at last superposes.The 4th bearing shell place vibration eliminated because of the self-equilibrating phenomenon.Figure 16～shown in Figure 24 is the 3D hologram spectrogram of computer simulation equilibrium process.
By Figure 16～Figure 21 as seen, if the on-the-spot counterweight of adjusting each balanced surface separately, probably can make certain bearing place vibration sharply increase (shown in 3 watts, Figure 19 among Figure 17 1 watt); This step then can carry out on computers safely and fast.By the counterbalance effect of Figure 22～Figure 24 as seen, it is feasible, comparatively accurately that the holographic dynamic balance method is applied to axle system, equally also has the characteristics of self-equilibrating, can guarantee that the vibration of the 4th bearing surface is reduced.
Holographic shafting balancing method provides new effective way for the dynamic balancing of the flexible shaft system that multi-support, many rotors form. Its superiority shows the following aspects:
(1) can once obtain the suitable counterweight of three faces, so compare with the method for adjustment of present field by using, reduce the test mass cycling start on the basis that does not reduce counterbalance effect.
(2) avoid when the face successive adjustment counterweight because of the vibration at certain bearing place excessive to the unit injury or jump the danger of car.
(3) top definite balance result can be optimized with the mode of computer simulation.
(4) whole equilibrium process carries out on computers, safety, fast, do not need very high specialized technical knowledge, have good economic benefit and practical value.
Claims (3)
1. the multi-support axle system that is made up of flex rotor is the general version of rotary machine rotor-supporting system, the balance of axle system is different from the balance of general double base rotor, holographic dynamic balancing method of flexible rotor shaft system of the present invention is characterized in that, may further comprise the steps:
1) at first will obtain the composition axle is the vibration signal at each rotor bearing place, is instrument with holographic analysis of spectrum, distinguishes the out-of-balance conditions of each rotor in the axle system, determines that unbalance fault is leading fault in the system; Distinguish power frequency vibration unbalance and that other reason causes;
2) by field balancing process of tracking or dynamics calculation, definite counterweight that respectively increases the weight of on the face is measured the influence of face to each, and represents with the form of 3D hologram spectrum;
3) eliminate the influence that operating load influences, decomposites each counterweight by linear operation, finally obtain and load irrelevant, by the single counterweight 1000g/0 ° of 3D hologram that causes spectrum and transition matrix thereof, transition matrix is the normalization matrix that the influence matrix of single counterweight on certain counterweight face calculates by angle rotation and vector convergent-divergent;
4) according to the minute surface symmetric relation of oval first phase point of original vibration and the oval first phase point of counterweight,, seek the fair-sized and the phase place of each counterweight by the conversion of transition matrix;
5) with computer simulation mode, intuitively demonstrate, axle is final vibration state when increasing the weight of by current counterweight scheme;
6) on computers selected counterweight size and phase place are carried out manual fine-tuning, determine the most rational counterweight scheme;
7) add selected counterweight, test the result who increases the weight of once more, as satisfy the balance requirement and then finish; Otherwise repetition above-mentioned steps.
2. holographic dynamic balancing method of flexible rotor shaft system according to claim 1 is characterized in that, described holographic analysis of spectrum is:
(a) to the holographic dynamic balance of many rotors, multi-support axle system with the 3D hologram analysis of spectrum as the basis, adopt N balancing plane, come the vibration of balance N+1 supporting place, wherein N+1＞2;
(b) in balancing run, each counterweight is handled in the mode that concerns of linearity the influence of shafting vibration;
(c) concern with the symmetry of the minute surface between 2 first phase points is secondary on the formed ellipse of original vibration and on the formed ellipse of counterweight, be used as seeking the foundation that makes things convenient for of optimum balance scheme;
(d) in the equilibrium process, utilize each counterweight to offset the unbalance vibration of supporting place respectively, N+1 supporting place vibration subdued automatically, and make axle system reach satisfied counterbalance effect generally;
(e) the 3D hologram spectral technology is applied to shafting balancing, thereby reflects vibrational state, equilibrium process and the counterbalance effect of axle system intuitively, all sidedly;
(f) utilize computer mould to fit the software fine setting on balance is implemented, what substituted field apparatus repeatedly plays the parking balance test, realizes the contrast and the optimization of multiple balance scheme on computers.
3. holographic dynamic balancing method of flexible rotor shaft system according to claim 1, it is characterized in that, the concrete computation process of described transition matrix is: at first the influence matrix to each counterweight face carries out linear scale, making the counterweight size normalization is 1000g, makes the influence matrix angle be normalized to 0 degree by angle rotation and compensation again.
Priority Applications (1)
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| CNB02114673XA CN1141567C (en) | 2002-07-15 | 2002-07-15 | Holographic dynamic balancing method of flexible rotor shaft system |
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Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
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| CN100468028C (en) * | 2006-03-13 | 2009-03-11 | 力帆实业(集团)股份有限公司 | Dynamic balance inspection of assembled crank link mechanism of single-cylinder engine |
| CN101639395B (en) * | 2009-08-31 | 2011-06-22 | 西安交通大学 | Improved holographic dynamic balancing method of high-speed main shaft |
| CN101929908B (en) * | 2008-12-08 | 2012-11-14 | 广东省电力工业局试验研究所 | Unbalanced azimuth estimation method based on holo-spectrum technology |
| CN104165729A (en) * | 2014-01-20 | 2014-11-26 | 西安电子科技大学 | Dynamic balancing method for high-speed rotors |
| CN104460728A (en) * | 2014-10-31 | 2015-03-25 | 西安电子科技大学 | Dynamic balance suppression method for spatial vibration of high-speed rotor bearing system |
| CN107066725A (en) * | 2017-04-11 | 2017-08-18 | 西北工业大学 | A kind of rotor structure dynamics Reverse Design based on failure gene |
| CN107367353A (en) * | 2016-05-12 | 2017-11-21 | 福建宁德核电有限公司 | On-line dynamic balancing handles rotor bow fault correction feasibility decision method and system |
| CN107389268A (en) * | 2017-06-30 | 2017-11-24 | 西安交通大学 | A kind of multiple spot spot dynamic balance method based on fast algorithm |
| CN112504647A (en) * | 2020-11-24 | 2021-03-16 | 厦门理工学院 | Multi-disk rotor system vibration signal detection device and detection method |
| CN113804354A (en) * | 2021-09-14 | 2021-12-17 | 西安交通大学 | Holographic synchronous dynamic balance method and system for flexible rotor |
| CN114563131A (en) * | 2022-03-21 | 2022-05-31 | 江苏大学 | Single-measuring-point multi-roller simultaneous dynamic balancing method and system |
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| CN100468028C (en) * | 2006-03-13 | 2009-03-11 | 力帆实业(集团)股份有限公司 | Dynamic balance inspection of assembled crank link mechanism of single-cylinder engine |
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| CN101639395B (en) * | 2009-08-31 | 2011-06-22 | 西安交通大学 | Improved holographic dynamic balancing method of high-speed main shaft |
| CN104165729A (en) * | 2014-01-20 | 2014-11-26 | 西安电子科技大学 | Dynamic balancing method for high-speed rotors |
| CN104165729B (en) * | 2014-01-20 | 2016-07-20 | 西安电子科技大学 | A kind of dynamic balance method of high speed rotor |
| CN104460728A (en) * | 2014-10-31 | 2015-03-25 | 西安电子科技大学 | Dynamic balance suppression method for spatial vibration of high-speed rotor bearing system |
| CN107367353B (en) * | 2016-05-12 | 2019-05-31 | 福建宁德核电有限公司 | On-line dynamic balancing handles rotor bow fault correction feasibility determination method and system |
| CN107367353A (en) * | 2016-05-12 | 2017-11-21 | 福建宁德核电有限公司 | On-line dynamic balancing handles rotor bow fault correction feasibility decision method and system |
| CN107066725A (en) * | 2017-04-11 | 2017-08-18 | 西北工业大学 | A kind of rotor structure dynamics Reverse Design based on failure gene |
| CN107389268A (en) * | 2017-06-30 | 2017-11-24 | 西安交通大学 | A kind of multiple spot spot dynamic balance method based on fast algorithm |
| CN107389268B (en) * | 2017-06-30 | 2019-08-09 | 西安交通大学 | A kind of multiple spot spot dynamic balance method based on fast algorithm |
| CN112504647A (en) * | 2020-11-24 | 2021-03-16 | 厦门理工学院 | Multi-disk rotor system vibration signal detection device and detection method |
| CN113804354A (en) * | 2021-09-14 | 2021-12-17 | 西安交通大学 | Holographic synchronous dynamic balance method and system for flexible rotor |
| CN113804354B (en) * | 2021-09-14 | 2022-07-12 | 西安交通大学 | Holographic synchronous dynamic balance method and system for flexible rotor |
| CN114563131A (en) * | 2022-03-21 | 2022-05-31 | 江苏大学 | Single-measuring-point multi-roller simultaneous dynamic balancing method and system |
| CN114563131B (en) * | 2022-03-21 | 2024-06-07 | 江苏大学 | Single-measuring-point multi-roller simultaneous dynamic balance method and system |
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