CN110823451A - Rigid rotor balancing method and control system thereof - Google Patents
Rigid rotor balancing method and control system thereof Download PDFInfo
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/30—Compensating imbalance
- G01M1/32—Compensating imbalance by adding material to the body to be tested, e.g. by correcting-weights
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Abstract
The invention relates to the technical field of rigid rotors, in particular to a rigid rotor balancing method and a control system thereof, which comprises the following steps: s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and acquiring a trial counterweight vibration amplitude and a trial counterweight vibration phase, and inputting the amplitudes and phases into an EXCEL table; s2, converting the initial vibration amplitude and the initial vibration phase and the trial counterweight vibration amplitude and the trial counterweight vibration phase into a complex form of a rectangular coordinate system; s3, obtaining an influence factor K of the rigid rotor of the equipment and a complex form of the weight block G; s4, obtaining the inner amplitude G and the degree angle W of the object G to be weighed of the rigid rotor of the equipment; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W. The dynamic balance calculation method of the rigid rotor influence coefficient method developed by using the EXCEL built-in engineering function and the mathematical trigonometric function brings greater convenience to the field dynamic balance calculation and effectively improves the reliability of work.
Description
Technical Field
The invention relates to the technical field of rigid rotors, in particular to a rigid rotor balancing method and a control system thereof.
Background
The event that modern large rotating machines are forced to stop due to excessive vibration in operation often happens. The most common cause of excessive vibration is rotor mass imbalance. It is important to find the vector distribution of the rotor mass unbalance points and balance the weights at the correct positions to eliminate the unbalance. Therefore, how to quickly and efficiently trim a rigid rotor to avoid a shutdown event caused by rotor mass imbalance is a problem that needs to be solved at present.
Disclosure of Invention
In view of the above, the present invention provides a rigid rotor balancing method and a control system thereof, which are used to solve the defect that the vibration of the existing large-scale machine exceeds the standard due to the unbalanced mass of the rigid rotor.
A rigid rotor balancing method, comprising the steps of:
s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added, storing the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the equipment in a database, and then respectively inputting the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the monitoring and measuring equipment stored in the database into an EXCEL table;
s2, converting the initial vibration amplitude and the initial vibration phase, and the trial counterweight vibration amplitude and the trial counterweight vibration phase input in the last step into COMPLEX forms in a rectangular coordinate system respectively by using a COMPLEX function;
s3, calculating a complex difference value before and after the trial balance weight block P by utilizing an IMSUB function, and calculating an influence factor K of the rigid rotor of the equipment and a complex form of the balance weight block G by utilizing an IMDIV function;
s4, obtaining an inner amplitude G and a degree angle W of a weight block G to be weighed of the rigid rotor of the equipment by utilizing an IMABS function, an IMARGUMENT function and a DEGRES function; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W.
Further, as a preferred embodiment of the present invention, the specific process of step S1 is: s11, respectively acquiring initial vibration amplitude A of the rigid rotor of the equipment by using a vibration data acquisition analyzer0And initial vibration phase w0And stored in a database; s12, adding a trial weight object P to the rigid rotor of the equipment, and then respectively acquiring the trial weight vibration amplitude A of the rigid rotor of the equipment again1And trial balance vibration phase w1And stored again in the database; s13, acquiring the initial vibration amplitude A of the rigid rotor of the equipment in the database0With initial vibration phase w0Trial balance vibration amplitude A1With trial balance of vibration phase w1And inputting the trial balance weight blocks P into the EXCEL table respectively。
Further, as a preferred embodiment of the present invention, the specific process of step S2 is: s21, utilizing the COMPLEX function to input the initial vibration amplitude A of the previous step0With initial vibration phase w0Converting into complex z in rectangular coordinate system0(ii) a S22, using COMPLEX function to input the trial counterweight vibration amplitude A in the previous step1With trial balance of vibration phase w1Converting into complex z in rectangular coordinate system1(ii) a S23, using COMPLEX function to test the mass G of the mass PpAnd phase wpConverting into complex z in rectangular coordinate systemp。
Further, as a preferred embodiment of the present invention, the specific process of step S21 is: s211, calculating the complex number z0Real coefficient of
S212, recalculating the complex number z0Imaginary coefficient ofS213, using the COMPLEX function Z ═ a, b, dividing the COMPLEX number Z0Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z0＝(x0,y0)。
Further, as a preferred embodiment of the present invention, the specific process of step S22 is: s221, first calculating a complex number z1Real coefficient of
S222, recalculating the complex number z1Imaginary coefficient of
S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function Z1Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z1＝(x1,y1)。
Further, as a preferred embodiment of the present invention, the specific process of step S23 is: s221, first calculating a complex number zpReal coefficient of
S222, recalculating the complex number zpImaginary coefficient of
S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function ZpRespectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain zp＝(xp,yp)。
Further, as a preferred embodiment of the present invention, the specific process of step S3 is: s31, calculating the complex difference z before and after adding the test weight P by using the IMSUB function2＝z1-z0(ii) a S32, calculating the complex form of the influence factor K of the rigid rotor of the equipment by utilizing the IMDIV functionS33, calculating the complex form of the object G to be weighted of the rigid rotor of the equipment by utilizing the IMDIV function
Further, as a preferred embodiment of the present invention, the specific process of step S4 is: s41, calculating the complex form of the object G to be weighed of the rigid rotor of the equipment to be converted into the inner amplitude G of the polar coordinate system by utilizing an IMABS function; s42, calculating the arc angle of the polar coordinate system converted from the complex form of the mass G to be weighed of the rigid rotor of the equipment by using an IMARGUMENT function; s43, converting the polar coordinate system arc angle of the object G to be weighed of the rigid rotor of the equipment into a polar coordinate system degree angle W by using a DEGRES function; s44, placing and fixing the weight-to-be-weighed object G with the weight of G on the rigid rotor of the equipment according to the inner amplitude G and the degree angle W of the weight-to-be-weighed object G of the rigid rotor of the equipment.
A control system of a rigid rotor balancing method comprises an equipment rigid rotor, a vibration data acquisition analyzer for measuring the vibration amplitude and the vibration phase of the equipment rigid rotor, a database for storing data information and an ECEL table for calculation; the vibration data acquisition analyzer is used for measuring vibration amplitude and vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P and storing the vibration amplitude and the vibration phase in the database, the ECEL table is used for calling the vibration amplitude and the vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P in the database, the internal amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are obtained by calculation through a data function in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W.
Further, as a preferred embodiment of the present invention, the data information stored in the database includes an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, a trial weight vibration amplitude and a trial weight vibration phase of the rigid rotor of the equipment after the trial weight P is added, a mass and a phase of the trial weight P, an IMSUB function, an IMSUM function, an impudu function, an IMDIV function pair, an IMABS function, an IMARGUMENT function, and a degees function.
According to the technical scheme, the invention has the beneficial effects that: compared with the prior art, the rigid rotor balancing method disclosed by the invention has the advantages that the initial vibration amplitude and the initial vibration phase of the rigid rotor of the equipment are utilized, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the rigid rotor of the equipment are converted and calculated after the trial counterweight block P is added, the inner amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are quickly calculated by means of the ECEL table and the functions and data information stored in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W, so that the weight balancing purpose of the rigid rotor is quickly achieved, the defect that the vibration of the existing large-scale machine exceeds the standard due to the mass unbalance of the rigid rotor can be effectively overcome, and the purpose of reducing the vibration times of the large-scale machine exceeding the standard is achieved.
Detailed Description
The following is a detailed description of the above-mentioned aspects of the present invention by way of example, and it is specifically noted that numerous modifications and improvements may be made in accordance with the principles of the present invention, which are also considered to be within the scope of the embodiments of the present invention.
According to the rigid rotor balancing method and the control system thereof disclosed by the invention, the invention specifically discloses the following specific embodiments:
the first embodiment is as follows: a rigid rotor balancing method, comprising the steps of:
s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added, storing the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the equipment in a database, and then respectively inputting the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the monitoring and measuring equipment stored in the database into an EXCEL table; the specific process of step S1 is: s11, respectively acquiring initial vibration amplitude A of the rigid rotor of the equipment by using a vibration data acquisition analyzer0And initial vibration phase w0And stored in a database; s12, adding a trial weight object P to the rigid rotor of the equipment, and then respectively acquiring the trial weight vibration amplitude A of the rigid rotor of the equipment again1And trial balance vibration phase w1And stored again in the database; s13, acquiring the initial vibration amplitude A of the rigid rotor of the equipment in the database0With initial vibration phase w0Trial balance vibration amplitude A1With trial balance of vibration phase w1And inputting the trial balance weight blocks P into the EXCEL table respectively.
S2, converting the initial vibration amplitude and the initial vibration phase, and the trial counterweight vibration amplitude and the trial counterweight vibration phase input in the last step into COMPLEX forms in a rectangular coordinate system respectively by using a COMPLEX function; the specific process of step S2 is: s21, utilizing the COMPLEX function to input the initial vibration amplitude A of the previous step0With initial vibration phase w0Converting into complex z in rectangular coordinate system0(ii) a S22, using COMPLEX function to input the trial counterweight vibration amplitude A in the previous step1Vibrating with a trial balancePhase w1Converting into complex z in rectangular coordinate system1(ii) a S23, using COMPLEX function to test the mass G of the mass PpAnd phase wpConverting into complex z in rectangular coordinate systemp. The specific process of step S21 is: s211, calculating the complex number z0Real coefficient of
S212, recalculating the complex number z0Imaginary coefficient of
S213, using the COMPLEX function Z ═ a, b, dividing the COMPLEX number Z0Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z0＝(x0,y0). The specific process of step S22 is: s221, first calculating a complex number z1Real coefficient of
S222, recalculating the complex number z1Imaginary coefficient of
S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function Z1Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z1＝(x1,y1). The specific process of step S23 is: s221, first calculating a complex number zpReal coefficient of
S222, recalculating the complex number zpImaginary coefficient ofS223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function ZpRespectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain zp＝(xp,yp)。
S3, calculating the complex difference before and after adding the trial balance weight P by utilizing the IMSUB function, and respectively calculating to obtain the equipment by utilizing the IMDIV functionThe influence factor K of the rigid rotor and the complex form of the counterweight G; the specific process of step S3 is: s31, calculating the complex difference z before and after adding the test weight P by using the IMSUB function2＝z1-z0(ii) a S32, calculating the complex form of the influence factor K of the rigid rotor of the equipment by utilizing the IMDIV function
S33, calculating the complex form of the object G to be weighted of the rigid rotor of the equipment by utilizing the IMDIV function
S4, obtaining an inner amplitude G and a degree angle W of a weight block G to be weighed of the rigid rotor of the equipment by utilizing an IMABS function, an IMARGUMENT function and a DEGRES function; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W. The specific process of step S4 is: s41, calculating the complex form of the object G to be weighed of the rigid rotor of the equipment to be converted into the inner amplitude G of the polar coordinate system by utilizing an IMABS function; s42, calculating the arc angle of the polar coordinate system converted from the complex form of the mass G to be weighed of the rigid rotor of the equipment by using an IMARGUMENT function; s43, converting the polar coordinate system arc angle of the object G to be weighed of the rigid rotor of the equipment into a polar coordinate system degree angle W by using a DEGRES function; s44, placing and fixing the weight-to-be-weighed object G with the weight of G on the rigid rotor of the equipment according to the inner amplitude G and the degree angle W of the weight-to-be-weighed object G of the rigid rotor of the equipment.
The invention also comprises a control system of the rigid rotor balancing method, wherein the system comprises the rigid rotor of the equipment, a vibration data acquisition analyzer for measuring the vibration amplitude and the vibration phase of the rigid rotor of the equipment, a database for storing data information and an ECEL table for calculation; the vibration data acquisition analyzer is used for measuring vibration amplitude and vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P and storing the vibration amplitude and the vibration phase in the database, the ECEL table is used for calling the vibration amplitude and the vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P in the database, the internal amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are obtained by calculation through a data function in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W.
More specifically, the data information stored in the database includes an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight mass P is added, a mass and a phase of the trial counterweight mass P, an IMSUB function, an IMSUM function, an impudurt function, an IMDIV function pair, an IMABS function, an imargumet function, and a degees function. Wherein, the IMSUB function, IMSUM function, IMPRODUCT function, IMDIV function pair, IMABS function, IMAGEMENT function and DERAGES function are all existing known functions, and the IMSUB function, IMSUM function, IMPRODUCT function, IMDIV function pair, IMABS function, IMARGUMENT function and DERAGES function are all integrated in the office software and EXCEL system.
The specific experiment is as follows: the invention discloses a rigid rotor balancing method and a control system thereof, and for better illustration, the embodiment adopts concrete operation demonstration.
A W furnace type natural circulation subcritical II type boiler of a Babucoke Wilcoxs Limited company of a power plant in Hunan is provided with an adjustable axial flow fan with a driven drum ASN-2880/1600 type movable blade, a vibration measuring point of a fan bearing box is gradually increased to 4.7mm/s in 2016 and exceeds an alarm value of a vibration measuring point of the fan by 4.6mm/s, a DCS system is directly alarmed, an initial vibration value A0 is actually measured to 156um and ∠ 58 in the field by using a dynamic balancer, the influence coefficient of the historical dynamic balance of the fan is calculated to be weighted P257G and ∠, the fan is started again after the balance of the fan is stopped, the weighted vibration value A1 is measured to be 97um and ∠ 135, the values A0 and P, A1 are obtained so far, the influence coefficient method is substituted for dynamic balance calculation, an EXCEL table is automatically calculated to be weighted G244G and ∠ G, the secondary fan is started to be weighted P257G and ∠ G, the weighted balance angle is calculated to be equivalent to a measured to be equivalent to a theoretical vibration value of a theoretical vibration value.
The calculation process is shown in table 1:
table 1 a rigid rotor balancing method and a control system thereof
As can be seen from table 1, with the rigid rotor balancing method and the control system thereof disclosed in the embodiments of the present invention, a new idea of calculation is provided for engineers by using a rigid rotor influence coefficient method dynamic balance calculation program developed by an EXCEL built-in engineering function and a mathematical trigonometric function, and greater convenience is brought to on-site dynamic balance calculation along with the development of a mobile office terminal. And effectively improve the reliability of work.
Therefore, compared with the prior art, the rigid rotor balancing method and the rigid rotor balancing system disclosed by the invention have the advantages that the initial vibration amplitude and the initial vibration phase of the rigid rotor of the equipment, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added are converted and calculated, the inner amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are quickly calculated by means of functions and data information stored in an ECEL table and a database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W, so that the weight balancing purpose of the rigid rotor is quickly achieved, the defect that vibration exceeds the standard of the existing large-scale machinery due to mass unbalance of the rigid rotor can be effectively overcome, and the purpose of reducing the times that vibration of the large-scale machinery exceeds the standard can be achieved.
The previous description of the disclosed embodiments is provided to enable any person skilled in the art to make or use the present invention. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the generic principles defined herein may be applied to other embodiments without departing from the spirit or scope of the invention. Thus, the present invention is not intended to be limited to the embodiments shown herein but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.
Claims (10)
1. A rigid rotor balancing method, comprising the steps of:
s1, acquiring an initial vibration amplitude and an initial vibration phase of the rigid rotor of the equipment, and a trial counterweight vibration amplitude and a trial counterweight vibration phase of the rigid rotor of the equipment after the trial counterweight block P is added, storing the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the equipment in a database, and then respectively inputting the initial vibration amplitude, the initial vibration phase, the trial counterweight vibration amplitude and the trial counterweight vibration phase of the monitoring and measuring equipment stored in the database into an EXCEL table;
s2, converting the initial vibration amplitude and the initial vibration phase, and the trial counterweight vibration amplitude and the trial counterweight vibration phase input in the last step into COMPLEX forms in a rectangular coordinate system respectively by using a COMPLEX function;
s3, calculating a complex difference value before and after the trial balance weight block P by utilizing an IMSUB function, and calculating an influence factor K of the rigid rotor of the equipment and a complex form of the balance weight block G by utilizing an IMDIV function;
s4, obtaining an inner amplitude G and a degree angle W of a weight block G to be weighed of the rigid rotor of the equipment by utilizing an IMABS function, an IMARGUMENT function and a DEGRES function; and placing and fixing the finally obtained weight-to-be-weighed mass G with the weight G on the rigid rotor of the equipment according to the direction of the degree angle W.
2. The rigid rotor balancing method according to claim 1, wherein the specific process of step S1 is as follows: s11, respectively acquiring initial vibration amplitude A of the rigid rotor of the equipment by using a vibration data acquisition analyzer0And initial vibration phase w0And stored in a database; s12, adding a trial weight object P to the rigid rotor of the equipment, and then respectively acquiring the trial weight vibration amplitude A of the rigid rotor of the equipment again1And trial balance vibrationDynamic phase w1And stored again in the database; s13, acquiring the initial vibration amplitude A of the rigid rotor of the equipment in the database0With initial vibration phase w0Trial balance vibration amplitude A1With trial balance of vibration phase w1And inputting the trial balance weight blocks P into the EXCEL table respectively.
3. The rigid rotor balancing method according to claim 2, wherein the specific process of step S2 is as follows: s21, utilizing the COMPLEX function to input the initial vibration amplitude A of the previous step0With initial vibration phase w0Converting into complex z in rectangular coordinate system0(ii) a S22, using COMPLEX function to input the trial counterweight vibration amplitude A in the previous step1With trial balance of vibration phase w1Converting into complex z in rectangular coordinate system1(ii) a S23, using COMPLEX function to test the mass G of the mass PpAnd phase wpConverting into complex z in rectangular coordinate systemp。
4. A rigid rotor balancing method according to claim 3, wherein the specific process of step S21 is as follows: s211, calculating the complex number z0Real coefficient of
S212, recalculating the complex number z0Imaginary coefficient of
S213, using the COMPLEX function Z ═ a, b, dividing the COMPLEX number Z0Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z0＝(x0,y0)。
5. The rigid rotor balancing method according to claim 4, wherein the specific process of step S22 is as follows: s221, first calculating a complex number z1Real coefficient of
S222, recalculating the complex number z1Imaginary coefficient ofS223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function Z1Respectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain z1＝(x1,y1)。
6. The rigid rotor balancing method according to claim 5, wherein the specific process of step S23 is as follows: s221, first calculating a complex number zpReal coefficient ofS222, recalculating the complex number zpImaginary coefficient of
S223 dividing the COMPLEX number Z into (a, b) by using the COMPLEX function ZpRespectively substituting the real coefficient and the imaginary coefficient into a COMPLEX function to obtain zp＝(xp,yp)。
7. The rigid rotor balancing method according to claim 6, wherein the specific process of step S3 is as follows: s31, calculating the complex difference z before and after adding the test weight P by using the IMSUB function2＝z1-z0(ii) a S32, calculating the complex form of the influence factor K of the rigid rotor of the equipment by utilizing the IMDIV function
S33, calculating the complex form of the object G to be weighted of the rigid rotor of the equipment by utilizing the IMDIV function
8. The rigid rotor balancing method according to claim 7, wherein the specific process of step S4 is as follows: s41, calculating the complex form of the object G to be weighed of the rigid rotor of the equipment to be converted into the inner amplitude G of the polar coordinate system by utilizing an IMABS function; s42, calculating the arc angle of the polar coordinate system converted from the complex form of the mass G to be weighed of the rigid rotor of the equipment by using an IMARGUMENT function; s43, converting the polar coordinate system arc angle of the object G to be weighed of the rigid rotor of the equipment into a polar coordinate system degree angle W by using a DEGRES function; s44, placing and fixing the weight-to-be-weighed object G with the weight of G on the rigid rotor of the equipment according to the inner amplitude G and the degree angle W of the weight-to-be-weighed object G of the rigid rotor of the equipment.
9. The control system of a rigid rotor balancing method according to claim 8, comprising a rigid rotor of the apparatus, a vibration data acquisition analyzer for measuring vibration amplitude and vibration phase of the rigid rotor of the apparatus, a database for storing data information, and an ECEL table for calculation; the vibration data acquisition analyzer is used for measuring vibration amplitude and vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P and storing the vibration amplitude and the vibration phase in the database, the ECEL table is used for calling the vibration amplitude and the vibration phase of the rigid rotor of the equipment before and after the rigid rotor adds the test counterweight block P in the database, the internal amplitude G and the degree angle W of the counterweight block G of the rigid rotor of the equipment are obtained by calculation through a data function in the database, and the finally obtained counterweight block G with the weight of G is placed and fixed on the rigid rotor of the equipment according to the direction of the degree angle W.
10. A control system for a rigid rotor balancing method according to claim 9, wherein the data stored in the database includes the initial vibration amplitude and initial vibration phase of the rigid rotor of the plant, the trial weight vibration amplitude and trial weight vibration phase of the rigid rotor of the plant after adding the trial weight P, the mass and phase of the trial weight P, and the IMSUB function, IMSUM function, impudu function, IMDIV function pair, IMABS function, imargumet function, and degees function.
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