Method for acquiring phase-free field dynamic balance scheme of rotor of rotary machine

Abstract

The method for acquiring the phase-free field dynamic balance scheme of the rotor of the rotating machine comprises the following steps of: installing a weight indicator on a rotor counterweight disc, measuring a vibration value of the weight indicator, and calculating an equivalent weight and an equivalent phase of the weight indicator; establishing an on-site dynamic balance parameter calculation module, and obtaining an on-site dynamic balance scheme through the on-site dynamic balance parameter calculation module according to the vibration value of the indicated weight, the equivalent weight of the indicated weight and the equivalent phase; the field dynamic balance scheme comprises the final counterweight hole number of the counterweight disc and the final counterweight mass corresponding to the final counterweight hole number; according to the method, on-site dynamic balance scheme acquisition can be carried out based on vibration data acquired by any vibration test equipment, and the method can adapt to rotating machines of various manufacturers and various models.

Description

Technical Field

[0001] The invention belongs to the technical field of on-site dynamic balancing of rotating machinery, and in particular relates to a method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor. Background Art

[0002] Rotating machinery includes steam turbines, gas turbines, compressors and other devices. Its function is energy conversion, which is used to convert chemical energy, thermal energy, etc. into mechanical energy. During the processing, manufacturing and assembly of rotating machinery rotors, the rotor mass will be unbalanced due to inconsistent material properties, processing and assembly errors. When the rotor rotates, the unbalanced mass generates centrifugal disturbance force, which is transmitted to the housing and base through the bearings, causing vibration and reducing the service life of the equipment. For rotating machinery rotors, excessive imbalance will also cause an increase in the load on the internal components and bearings of the rotating machinery, and may even cause damage to the internal components and bearings of the rotating machinery, thereby affecting the safe operation of the equipment.

[0003] The commonly used on-site dynamic balancing analysis software on the market are all integrated into dedicated vibration testing systems. The disadvantage of this type of system is that the software and hardware are bound together, and it can only perform online on-site dynamic balancing for a single speed, and cannot be adapted to rotating machinery of various manufacturers and models. Summary of the invention

[0004] In order to solve the problem that the on-site dynamic balancing analysis software in the prior art can only perform online on-site dynamic balancing for a single speed, a method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor is proposed.

[0005] Step 1: Start the rotating machinery and obtain the initial vibration value of the rotor;

[0006] Step 2: Install No. 1 indicator weight in the mth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after No. 1 indicator weight is installed; the equivalent weight of No. 1 indicator weight and the equivalent phase of No. 1 indicator weight are calculated according to the weight of the indicator weight in each counterweight hole of the rotor counterweight plate after No. 1 indicator weight is installed and the phase of the counterweight hole; m∈[1,2,3,···,N], N is the total number of counterweight holes of the rotor counterweight plate;

[0007] Step 3: Remove the No. 1 weight on the rotor counterweight plate, install the No. 2 weight on the nth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after the No. 2 weight is installed; the equivalent weight of the No. 2 weight and the equivalent phase of the No. 2 weight are calculated according to the weight of the weight in each counterweight hole of the rotor counterweight plate after the No. 2 weight is installed and the phase of the counterweight hole; n∈[1,2,3,···,N];

[0008] Step 4: Establish an on-site dynamic balancing parameter calculation module, input the rotor initial vibration value, No. 1 weight vibration value, No. 1 weight equivalent weight, No. 1 weight equivalent phase, No. 2 weight vibration value, No. 2 weight equivalent weight and No. 2 weight equivalent phase into the on-site dynamic balancing parameter calculation module to obtain the on-site dynamic balancing plan; the on-site dynamic balancing plan includes the final counterweight hole number of the counterweight plate and the final counterweight mass corresponding to the final counterweight hole number.

[0009] Beneficial Effects

[0010] The method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor of the present application includes installing a weight indicator on a rotor counterweight plate, measuring the vibration value of the weight indicator, and calculating the equivalent weight and equivalent phase of the weight indicator; establishing an on-site dynamic balancing parameter calculation module, and obtaining an on-site dynamic balancing solution through the on-site dynamic balancing parameter calculation module according to the vibration value of the weight indicator, the equivalent weight of the weight indicator, and the equivalent phase; the on-site dynamic balancing solution includes the final counterweight hole number of the counterweight plate and the final counterweight mass corresponding to the final counterweight hole number; the method can obtain an on-site dynamic balancing solution based on vibration data obtained by any vibration testing equipment, and can be adapted to rotating machinery of various manufacturers and models. BRIEF DESCRIPTION OF THE DRAWINGS

[0011] Figure 1 This is a flow chart of a method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to a specific implementation method of the present application;

[0012] Figure 2 It is the weight information input interface of the on-site dynamic balancing parameter calculation module of the specific implementation mode of this application. DETAILED DESCRIPTION

[0013] The following will be combined with the attached embodiment of the present invention Figure 1 To Attachment Figure 2 , illustrate this implementation mode, and clearly and completely describe the technical solutions in the embodiments of the present invention:

[0014] A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor, comprising:

[0015] Step 1: Start the rotating machinery and obtain the initial vibration value of the rotor;

[0016] Step 2: Install No. 1 indicator weight in the mth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after No. 1 indicator weight is installed; the equivalent weight of No. 1 indicator weight and the equivalent phase of No. 1 indicator weight are calculated according to the weight of the indicator weight in each counterweight hole of the rotor counterweight plate after No. 1 indicator weight is installed and the phase of the counterweight hole; m∈[1,2,3,···,N], N is the total number of counterweight holes of the rotor counterweight plate;

[0017] Step 3: Remove the No. 1 weight on the rotor counterweight plate, install the No. 2 weight on the nth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after the No. 2 weight is installed; the equivalent weight of the No. 2 weight and the equivalent phase of the No. 2 weight are calculated according to the weight of the weight in each counterweight hole of the rotor counterweight plate after the No. 2 weight is installed and the phase of the counterweight hole; n∈[1,2,3,···,N];

[0018] Step 4: Establish an on-site dynamic balancing parameter calculation module, input the rotor initial vibration value, No. 1 weight vibration value, No. 1 weight equivalent weight, No. 1 weight equivalent phase, No. 2 weight vibration value, No. 2 weight equivalent weight and No. 2 weight equivalent phase into the on-site dynamic balancing parameter calculation module to obtain the on-site dynamic balancing plan; the on-site dynamic balancing plan includes the final counterweight hole number of the counterweight plate and the final counterweight mass corresponding to the final counterweight hole number.

[0019] Further, obtaining the initial vibration value of the rotor includes: starting the rotating machinery, increasing the rotor power from 0 to the rated power within a set time, and obtaining a rotor vibration spectrum through measurement; obtaining the rotor vibration peak value and the rotor speed and rotor power corresponding to the rotor vibration peak value according to the rotor vibration spectrum; allowing the rotor to stably operate at the rotor speed and rotor power for t minutes, and taking the average value of the rotor fundamental frequency from t / 2 to t minutes as the rotor initial vibration value α L1 .

[0020] Specifically, after starting the rotating machinery, the rotor is slowly increased from the minimum operating speed to the rated power within 285S to 315S; the rotor runs stably for no less than ten minutes at the vibration peak, and the average value of the rotor fundamental frequency in the last 5 to 10 minutes is taken as the rotor initial vibration value α L1 .

[0021] Further, a No. 1 indicator weight is installed in the mth counterweight hole of the rotor counterweight plate, and the vibration value of the No. 1 indicator weight is measured, including:

[0022] Install No. 1 weight indicator on the mth weight hole of the rotor weight plate, start the rotating machine, and increase the rotor power from 0 to the rated power within the set time. Obtain the first rotor vibration spectrum after the No. 1 weight indicator is installed by measurement; obtain the rotor vibration peak value after the No. 1 weight indicator is installed and the first rotor speed and the first rotor power corresponding to the rotor vibration peak value according to the first rotor vibration spectrum; allow the rotor to run stably at the first rotor speed and the first rotor power for t minutes, and take the average value of the first rotor fundamental frequency from t / 2 to t minutes as the vibration value α of No. 1 weight indicator L2 Specifically, install the No. 1 indicator weight in the mth counterweight hole of the rotor counterweight plate. If the mass of the indicator weight 1 is too large to be installed in the mth counterweight hole, the same mass counterweight can be installed in the mth and m+1th counterweight holes at the same time;

[0023] Further, the equivalent weight of the No. 1 indicator weight and the equivalent phase of the No. 1 indicator weight are calculated based on the indicator weight weight in each counterweight hole of the rotor counterweight plate after the No. 1 indicator weight is installed and the phase of the counterweight hole;

[0024] The counterweight holes on the rotor counterweight plate are numbered, and the counterweight hole numbers increase in the opposite direction of the counterweight plate rotation. The position phase of the first counterweight hole is set to zero; the phase of the i-th counterweight hole is expressed as: η si =(N i -1)×360 / N; where η si is the phase of the ith counterweight hole, N i is the i-th counterweight hole, N is the total number of counterweight holes, i∈[1,2,3,···,N], m∈[1,2,3,···,N];

[0025] No. 1 weight equivalent weight m 1s The calculation method is:

[0026] Among them, m 1si The weight of the ith counterweight hole after the No. 1 counterweight is installed;

[0027] No. 1 weight equivalent phase η 1s The calculation method is:

[0028] Determine parameter f 1 Is it greater than 0? If the parameter f 1 If greater than 0,

[0029]

[0030] If the parameter f 1 If it is less than 0,

[0031]

[0032] parameter

[0033] Further, a No. 2 weight is installed at the nth weight hole of the rotor weight plate, and a vibration value of the No. 2 weight is measured, including: installing the No. 2 weight at the nth weight hole of the rotor weight plate, starting the rotating machinery, so that the rotor power is increased from 0 to the rated power within a set time, and obtaining a second rotor vibration spectrum after the No. 2 weight is installed through measurement; obtaining the rotor vibration peak value after the No. 2 weight is installed and the second rotor speed and the second rotor power corresponding to the rotor vibration peak value according to the second rotor vibration spectrum; the rotor is allowed to stably operate at the second rotor speed and the second rotor power for t minutes, and the average value of the rotor fundamental frequency from t / 2 to t minutes is used as the vibration value α of the No. 2 weight. L3 ; n∈[1,2,3,···,N].

[0034] Further, the equivalent weight of the No. 2 indicator weight and the equivalent phase of the No. 2 indicator weight are calculated based on the indicator weight in each counterweight hole of the rotor counterweight plate after the No. 2 indicator weight is installed and the phase of the counterweight hole, including:

[0035] No. 2 weight equivalent weight m 2s The calculation method is:

[0036] Among them, m 2si The weight of the weight in the ith counterweight hole after the No. 2 weight indicator is installed;

[0037] No. 2 weight equivalent phase η 2s The calculation method is:

[0038] Determine parameter f 2 Is it greater than 0? If the parameter f 2 If greater than 0,

[0039]

[0040] If the parameter f 2 If it is less than 0,

[0041]

[0042] parameter

[0043] Furthermore, the combined mass of weight 1 and weight 2 is equal to m Sj , m Sj =9549MG / r×n, where M is the rotor mass, G is the selected accuracy level, r is the correction radius, and n is the rotor speed; specifically, the mass difference between weight 1 and weight 2 does not exceed 50%

[0044] Furthermore, the angle between the nth counterweight hole of the rotor counterweight plate and the mth counterweight hole of the rotor counterweight plate is not less than 45°.

[0045] Furthermore, the on-site dynamic balancing parameter calculation module is an on-site dynamic balancing parameterization calculation tool written in C++ language in the QTCreator software;

[0046] The on-site dynamic balancing parameter calculation module includes: a weight information input unit, a vibration information input unit and an on-site dynamic balancing solution calculation unit;

[0047] The weight information input unit is used to receive the input equivalent weight of weight No. 1, equivalent phase of weight No. 1, equivalent weight of weight No. 2 and equivalent phase of weight No. 2, and input the equivalent weight of weight No. 1, equivalent phase of weight No. 1, equivalent weight of weight No. 2 and equivalent phase of weight No. 2 to the on-site dynamic balancing solution calculation unit;

[0048] The vibration information input unit is used to receive the input of the initial vibration value α of the rotor. L1 、No. 1 weight vibration value α L2 and No. 2 weight vibration value α L3 , the initial vibration value of the rotor α L1 、No. 1 weight vibration value α L2 and No. 2 weight vibration value α L3 Input to the on-site dynamic balancing solution calculation unit;

[0049] The on-site dynamic balancing scheme calculation unit is used to calculate the on-site dynamic balancing scheme based on the input rotor initial vibration value, No. 1 indicator weight vibration value, No. 1 indicator weight equivalent weight, No. 1 indicator weight equivalent phase, No. 2 indicator weight vibration value, No. 2 indicator weight equivalent weight and No. 2 indicator weight equivalent phase; the on-site dynamic balancing scheme includes the counterweight plate counterweight hole number and the counterweight mass corresponding to the counterweight hole number.

[0050] Specifically, a graphical interface of the on-site dynamic balancing parametric calculation module is established in the QTCreator software, including a balancing disk information input area, a weight information input area, a vibration information input area, a calculation result display area and a vibration value estimation area; program code is written based on the C++ language in the QTCreator software, and the balancing disk counterweight hole quantity and radius information input function is implemented in the balancing disk information input area. The display name uses the QLabel control, and the display name cannot be modified after the software is generated. The counterweight hole quantity input uses the QLineEdit control, and the above controls in this area are all placed in the QVBoxLayout control; program code is written based on the C++ language in the QT Creator software, and the input function of the mass and phase of the weight 1 and 2 is implemented in the weight information input area. The display names all use the QLabel control, and the input areas all use the QLineEdit control, and the above controls in this area are all placed in the QHBoxLayout control; program code is written based on the C++ language in the QTCreator software, and the measured initial vibration value α of the rotor is implemented in the vibration information input area. L1 、No. 1 weight vibration value α L2 and No. 2 weight vibration value α L3Input function, display names all use QLabel controls, input areas all use QLineEdit controls, and the above controls in this area are placed in a QHBoxLayout control; program code is written based on C++ language in QTCreator software, and the on-site dynamic balancing plan is obtained by formula. Display names all use QLabel controls, input areas all use QLineEdit controls, and the above controls in this area are placed in a QHBoxLayout control; program code is written based on C++ language in QTCreator software to obtain the final counterweight hole number of the counterweight plate and the final counterweight mass corresponding to the final counterweight hole number. Display names all use QLabel controls, input areas all use QLineEdit controls, and the above controls in this area are placed in a QHBoxLayout control; program code is written based on C++ language in QTCreator software to implement the custom counterweight mass and phase input function in the vibration value estimation area, and complete the function of displaying the estimated vibration value of the corresponding counterweight plan

[0051] Further, the on-site dynamic balancing solution calculation unit calculates the on-site dynamic balancing solution according to the input rotor initial vibration value, No. 1 weight indication vibration value, No. 1 weight indication equivalent weight, No. 1 weight indication equivalent phase, No. 2 weight indication vibration value, No. 2 weight indication equivalent weight and No. 2 weight indication equivalent phase, including:

[0052] Let integer a and integer b be: a∈[1,2,3,···,500]; b∈[0,1,2,···,359];

[0053] x1=m sj ×5 / a×cos(b×π / 180)+m 1s ×cos(η 1s ×π / 180)

[0054] x2=m sj ×5 / a×sin(b×π / 180)+m 1s ×sin(η 1s ×π / 180)

[0055] y1=m sj ×5 / a×cos(b×π / 180)+m 2s ×cos(η 2s ×π / 180)

[0056] y2=m sj ×5 / a×sin(b×π / 180)+m 2s ×sin(η 2s ×π / 180)

[0057]

[0058]

[0059] z=(x-α L2 ) 2 +(y-α L3 ) 2 , calculate the integer a and integer b corresponding to the minimum value of z, and assign a z = a and b z = b;

[0060] m zz =m sj ×5 / a z ; η zz =b z

[0061] Among them, x1 is process parameter No. 1, x2 is process parameter No. 2, y1 is process parameter No. 3, y2 is process parameter No. 4, x is the calculated value of the vibration amplitude of weight 1, y is the calculated value of the vibration amplitude of weight 2; z is the sum of squares of the vibration value differences, m zz is the final weight calculation value, η zz is the final weight phase calculation value;

[0062] Determine INT(η ZZ ×N / 360+1) is greater than N;

[0063] If INT(η ZZ ×N / 360+1) is greater than N, then N ZZ1 =INT(η ZZ ×N / 360+1)-N;

[0064] If INT(η ZZ ×N / 360+1) is less than or equal to N, then N ZZ1 =INT(η ZZ ×N / 360+1);

[0065] Judge N ZZ1 +1 is greater than N;

[0066] If N ZZ1 +1 is greater than N then N ZZ2 =N ZZ1 +1-N; if N ZZ1 +1 is less than or equal to N then N ZZ2 =N ZZ1 +1;

[0067] h=η ZZ -(INT(η ZZ ×N / 360+1)-1)×360 / N)×π / 180; determine whether h is equal to 0, if h=0, then m ZZ2=0,m ZZ1 =m ZZ ; if h≠0, m ZZ2 =m zz / (sin(g) / tan(h)+cos(g)),m ZZ1 =m zz2 × sin(g) / sin(h);

[0068] Where, INT is rounded down, h is process parameter No. 5, g is process parameter No. 6, g = 360 / N × π / 180-h; N ZZ1 is the first final counterweight hole number, m ZZ1 is the first final weight corresponding to the first final weight hole number, N ZZ2 The second final weight hole number, m ZZ2 is the second final weight corresponding to the second final balancing weight hole number.

[0069] Although the present invention is described herein with reference to specific embodiments, it should be understood that these embodiments are merely examples of the principles and applications of the present invention. It should therefore be understood that many modifications may be made to the exemplary embodiments and that other arrangements may be devised without departing from the spirit and scope of the present invention as defined by the appended claims. It should be understood that the various dependent claims and features described herein may be combined in a manner different from that described in the original claims. It should also be understood that features described in conjunction with individual embodiments may be used in other described embodiments.

Claims

1. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor, characterized in that: include: Step 1: Start the rotating machinery and obtain the initial vibration value of the rotor; Step 2: Install No. 1 indicator weight in the mth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after No. 1 indicator weight is installed; the equivalent weight of No. 1 indicator weight and the equivalent phase of No. 1 indicator weight are calculated according to the weight of the indicator weight in each counterweight hole of the rotor counterweight plate after No. 1 indicator weight is installed and the phase of the counterweight hole; m∈[1,2,3,···,N], N is the total number of counterweight holes of the rotor counterweight plate; Step 3: Remove the No. 1 weight on the rotor counterweight plate, install the No. 2 weight on the nth counterweight hole of the rotor counterweight plate, and measure the rotor vibration value after the No. 2 weight is installed; the equivalent weight of the No. 2 weight and the equivalent phase of the No. 2 weight are calculated according to the weight of the weight in each counterweight hole of the rotor counterweight plate after the No. 2 weight is installed and the phase of the counterweight hole; n∈[1,2,3,···,N]; Step 4: Establish an on-site dynamic balancing parameter calculation module, input the rotor initial vibration value, No. 1 weight vibration value, No. 1 weight equivalent weight, No. 1 weight equivalent phase, No. 2 weight vibration value, No. 2 weight equivalent weight and No. 2 weight equivalent phase into the on-site dynamic balancing parameter calculation module to obtain the on-site dynamic balancing plan; the on-site dynamic balancing plan includes the final counterweight hole number of the counterweight plate and the final counterweight mass corresponding to the final counterweight hole number.

2. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 1, characterized in that: Obtain the initial vibration value of the rotor, including: Start the rotating machinery, increase the rotor power from 0 to the rated power within the set time, and obtain the rotor vibration spectrum through measurement; obtain the rotor vibration peak value and the rotor speed and rotor power corresponding to the rotor vibration peak value according to the rotor vibration spectrum; make the rotor run stably at the rotor speed and rotor power for t minutes, and take the average value of the rotor fundamental frequency from t / 2 to t minutes as the rotor initial vibration value α L1 .

3. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 2, characterized in that: Install No. 1 weight at the mth weight hole of the rotor weight plate and measure the vibration value of No. 1 weight, including: Install No. 1 weight indicator on the mth weight hole of the rotor weight plate, start the rotating machine, and increase the rotor power from 0 to the rated power within the set time. Obtain the first rotor vibration spectrum after the No. 1 weight indicator is installed by measurement; obtain the rotor vibration peak value after the No. 1 weight indicator is installed and the first rotor speed and the first rotor power corresponding to the rotor vibration peak value according to the first rotor vibration spectrum; allow the rotor to run stably at the first rotor speed and the first rotor power for t minutes, and take the average value of the first rotor fundamental frequency from t / 2 to t minutes as the vibration value α of No. 1 weight indicator L2 .

4. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 3, characterized in that: According to the weight of the No. 1 weight in each counterweight hole of the rotor counterweight plate after the No. 1 weight is installed and the phase of the counterweight hole, the equivalent weight of the No. 1 weight and the equivalent phase of the No. 1 weight are calculated, including: The counterweight holes on the rotor counterweight plate are numbered, and the counterweight hole numbers increase in the opposite direction of the counterweight plate rotation. The position phase of the first counterweight hole is set to zero; the phase of the i-th counterweight hole is expressed as: η si =(N i -1)×360 / N; where η si is the phase of the ith counterweight hole, N i is the i-th counterweight hole, N is the total number of counterweight holes, i∈[1,2,3,···,N]; No. 1 weight equivalent weight m 1s The calculation method is: Among them, m 1si The weight of the weight in the ith counterweight hole after the No. 1 weight indicator is installed; No. 1 weight equivalent phase η 1s The calculation method is: Determine whether the parameter f1 is greater than 0. If the parameter f1 is greater than 0, If the parameter f1 is less than 0, parameter 5. The method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 4, characterized in that: Install No. 2 weight on the nth weight hole of the rotor weight plate and measure the vibration value of No. 2 weight, including: Install No. 2 weight indicator at the nth weight hole of the rotor weight plate, start the rotating machine, and increase the rotor power from 0 to the rated power within the set time. Obtain the second rotor vibration spectrum after the No. 2 weight indicator is installed by measurement; obtain the rotor vibration peak value after the No. 2 weight indicator is installed and the second rotor speed and the second rotor power corresponding to the rotor vibration peak value according to the second rotor vibration spectrum; allow the rotor to run stably at the second rotor speed and the second rotor power for t minutes, and take the average value of the rotor fundamental frequency from t / 2 to t minutes as the vibration value α of the No. 2 weight indicator L3 ; n∈[1,2,3,···,N].

6. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 5, characterized in that: According to the weight of the No. 2 weight in each counterweight hole of the rotor counterweight plate after the No. 2 weight is installed and the phase of the counterweight hole, the equivalent weight of the No. 2 weight and the equivalent phase of the No. 2 weight are calculated, including: No. 2 weight equivalent weight m 2s The calculation method is: Among them, m 2si The weight of the weight in the ith counterweight hole after the No. 2 weight indicator is installed; No. 2 weight equivalent phase η 2s The calculation method is: Determine whether the parameter f2 is greater than 0. If the parameter f2 is greater than 0, If the parameter f2 is less than 0, parameter 7. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 6, characterized in that: The combined mass of weight 1 and weight 2 is equal to m Sj , m Sj =9549MG / r×n, where M is the rotor mass, G is the selected accuracy grade, r is the correction radius, and n is the rated speed of the rotor.

8. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 7, characterized in that: The angle between the nth counterweight hole of the rotor counterweight plate and the mth counterweight hole of the rotor counterweight plate shall not be less than 45°.

9. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 8, characterized in that: The on-site dynamic balancing parameter calculation module is an on-site dynamic balancing parameter calculation tool written in C++ language in QT Creator software; The on-site dynamic balancing parameter calculation module includes: a weight information input unit, a vibration information input unit and an on-site dynamic balancing solution calculation unit; The weight information input unit is used to receive the input equivalent weight of weight No. 1, equivalent phase of weight No. 1, equivalent weight of weight No. 2 and equivalent phase of weight No. 2, and input the equivalent weight of weight No. 1, equivalent phase of weight No. 1, equivalent weight of weight No. 2 and equivalent phase of weight No. 2 to the on-site dynamic balancing solution calculation unit; The vibration information input unit is used to receive the input of the initial vibration value α of the rotor. L1 、No. 1 weight vibration value α L2 and No. 2 weight vibration value α L3 , the initial vibration value of the rotor α L1 、No. 1 weight vibration value α L2 and No. 2 weight vibration value α L3 Input to the on-site dynamic balancing solution calculation unit; The on-site dynamic balancing scheme calculation unit is used to calculate the on-site dynamic balancing scheme based on the input rotor initial vibration value, No. 1 indicator weight vibration value, No. 1 indicator weight equivalent weight, No. 1 indicator weight equivalent phase, No. 2 indicator weight vibration value, No. 2 indicator weight equivalent weight and No. 2 indicator weight equivalent phase; the on-site dynamic balancing scheme includes the counterweight plate counterweight hole number and the counterweight mass corresponding to the counterweight hole number.

10. A method for obtaining a phase-free on-site dynamic balancing solution for a rotating machinery rotor according to claim 9, characterized in that: The on-site dynamic balancing solution calculation unit calculates the on-site dynamic balancing solution based on the input rotor initial vibration value, No. 1 weight vibration value, No. 1 weight equivalent weight, No. 1 weight equivalent phase, No. 2 weight vibration value, No. 2 weight equivalent weight and No. 2 weight equivalent phase, including: Let integer a and integer b be: a∈[1,2,3,···,500]; b∈[0,1,2,···,359]; x1=m sj ×5 / a×cos(b×π / 180)+m 1s ×cos(η 1s ×π / 180) x2=m sj ×5 / a×sin(b×π / 180)+m 1s ×sin(η 1s ×π / 180) y1=m sj ×5 / a×cos(b×π / 180)+m 2s ×cos(η 2s ×π / 180) y2=m sj ×5 / a×sin(b×π / 180)+m 2s ×sin(η 2s ×π / 180) z=(x-α L2 ) 2 +(y-α L3 ) 2 , calculate the integer a and integer b corresponding to the minimum value of z, and assign a z = a and b z = b; m zz =m sj ×5 / a z ;or zz =b z Among them, x1 is process parameter No. 1, x2 is process parameter No. 2, y1 is process parameter No. 3, y2 is process parameter No. 4, x is the calculated value of the vibration amplitude of weight 1, y is the calculated value of the vibration amplitude of weight 2; z is the sum of squares of the vibration value differences, m zz is the final weight calculation value, η zz is the final weight phase calculation value; Determine INT(η ZZ ×N / 360+1) is greater than N; If INT(η ZZ ×N / 360+1) is greater than N, then N ZZ1 =INT(η ZZ ×N / 360+1)-N; If INT(η ZZ ×N / 360+1) is less than or equal to N, then N ZZ1 =INT(η ZZ ×N / 360+1); Judge N ZZ1 +1 is greater than N; If N ZZ1 +1 is greater than N then N ZZ2 =N ZZ1 +1-N; if N ZZ1 +1 is less than or equal to N then N ZZ2 =N ZZ1 +1; h=η ZZ -(INT(η ZZ ×N / 360+1)-1)×360 / N)×π / 180; determine whether h is equal to 0, if h=0, then m ZZ2 =0,m ZZ1 =m ZZ ; if h≠0, m ZZ2 =m zz / (sin(g) / tan(h)+cos(g)),m ZZ1 =m zz2 × sin(g) / sin(h); Where, INT is rounded down, h is process parameter No. 5, g is process parameter No. 6, g = 360 / N × π / 180-h; N ZZ1 is the first final counterweight hole number, m ZZ1 is the first final weight corresponding to the first final weight hole number, N ZZ2 The second final weight hole number, m ZZ2 is the second final weight corresponding to the second final balancing weight hole number.

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