CN110579312A - dynamic balance fault detection method for multi-wheel-disc shafting of non-trial-weight rotating machinery - Google Patents
dynamic balance fault detection method for multi-wheel-disc shafting of non-trial-weight rotating machinery 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
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/22—Determining imbalance by oscillating or rotating the body to be tested and converting vibrations due to imbalance into electric variables
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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
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/26—Determining imbalance by oscillating or rotating the body to be tested with special adaptations for marking, e.g. by drilling
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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 discloses a dynamic balance fault detection method for a multi-wheel-disc shafting of a non-trial-weight rotating machine. The method can realize a dynamic balance test without test weight, and the magnitude and the angle of unbalanced force are directly detected by vibration test data; meanwhile, the vibration in the vertical direction and the horizontal direction and the coupling influence between the vibration and the vibration are comprehensively considered, and the influence coefficient is not obtained by a method for establishing a rotor dynamics model, so that the accuracy of a dynamic balance test is high; in addition, the method can effectively reduce the number of dynamic balance tests, improve the dynamic balance test efficiency of the rotary machine, reduce the risk of the dynamic balance tests, and is particularly suitable for shafting dynamic balance fault detection of the rotary machine in the real state of the whole machine.
Description
Technical Field
The invention relates to a dynamic balance test method for a multi-wheel-disc shafting of a rotating machine, in particular to a dynamic balance fault detection method for a multi-wheel-disc shafting of a non-trial-weight rotating machine.
background
the unbalanced problem of ubiquitous rotating part in all kinds of rotating machinery production and processing processes such as steam turbine, generator, pump, fan, compressor, motor, rim plate place cross-section focus and geometric centre do not coincide promptly, produce centrifugal force among the rotatory process, this will lead to the vibration to influence equipment safe operation. After the rotary machine is manufactured, a dynamic balance test must be performed.
the currently adopted dynamic balance fault detection methods mainly include 4 types: (1) coefficient of influence method. The influence of the weighting on the vibration of the bearing and other parts is tested through the trial weighting on the plurality of wheel discs, the position, the weight and the angle of the unbalance are calculated through methods such as a least square method, a modal balancing method, a harmonic component and the like aiming at pursuing the minimum vibration. The method needs to obtain the influence coefficient matrix of the aggravation on the vibration through a plurality of dynamic balance tests, and the required dynamic balance tests are more. Because the unbalance angle cannot be accurately grasped whether the unbalance angle is correct or not due to the test weighting, the possibility of further increase of vibration exists in the dynamic balance test process, and the influence is brought to the equipment safety; (2) dynamic balance test method without test weight. The method needs to establish a rotor system dynamics analysis model firstly, calculate and calculate the influence coefficient of the unbalance on the vibration, and further calculate the unbalance weight and angle at one time according to the actually measured vibration and the calculated influence coefficient. The method also needs influence coefficients, but the influence coefficients are calculated by the established dynamic analysis model, the error of the calculated influence coefficients is large, and the dynamic characteristics, the boundary conditions and the like of the bearing have large influence on the calculation result. The calculation result can only be used for qualitative analysis and is difficult to quantify. Therefore, the method has larger error and is basically not adopted in engineering. (3) Balancing on a balancing machine: and assembling the machined wheel disc and placing the wheel disc on a special balancing machine. Balance is achieved by testing stress and vibration of swing frames on two sides of the balancing machine. This method requires special balancing equipment and is costly. The unbalanced force can be directly obtained by the stress of the swing frame at low speed, the trial weighting is not needed, but the balance is still needed by an influence coefficient method at high speed, or the influence coefficient of the weighting on the vibration is needed to be measured firstly. (4) One-time calibration method. According to the knowledge and experience of technicians on the vibration problem, the dynamic balance weighting scheme is calculated at one time by actually measured vibration data. This method does not require trial and error, but its reliability depends on how accurately the technician is cognizant of the vibration problem and the dynamic characteristics of the machine, and is difficult. This method is essentially also an influence coefficient method, except that the influence coefficient is given by the skilled person according to his own experience and the test data of the same type of unit.
With the development of the unit in the large-scale direction, the requirement on the reliability of equipment is higher and higher. After the vibration problem occurs, the vibration problem is hoped to be solved at one time, and repeated tests are not hoped to be carried out. Dynamic balance is an effective means for solving the vibration problem of various rotating machines. Therefore, it is important to research a new non-trial-and-error dynamic balance fault detection method.
disclosure of Invention
the purpose of the invention is as follows: in order to overcome the defects of the prior art, the invention provides a dynamic balance fault detection method for a multi-wheel-disc shafting of a non-trial-weight rotating machine, which can reduce the number of dynamic balance tests, improve the dynamic balance test efficiency of the rotating machine and reduce the risk of the dynamic balance tests. The shafting dynamic balance fault detection method is particularly suitable for shafting dynamic balance fault detection of the rotating machinery in the complete machine real state.
The technical scheme is as follows: the invention relates to a dynamic balance fault detection method for a multi-wheel disc shafting of a non-trial-weight rotating machine, which comprises the following steps of:
(1) after the rotating machine is assembled, vibration sensors are respectively arranged in the vertical direction and the horizontal direction of bearing blocks on two sides of the rotor;
(2) setting a key phase mark on the rotating shaft, using the key phase mark as a 0-degree mark on the rotating shaft, defining the angle of the reverse rotation direction as positive, and testing a key phase signal;
(3) Transmitting the signals of the vibration sensor and the key phase signals to a vibration analyzer to measure four vibration vectors of the two bearing seats;
(4) under the static state of the machine, respectively applying impact excitation forces in the vertical and horizontal directions to the exposed shaft necks near the two bearing seats, testing the vibration of the two bearing seats after the impact excitation, and obtaining frequency response functions of the excitation force of the shaft necks to the vibration of the bearing seats under different frequencies;
(5) Testing the vibration of the bearing seat when the unit is accelerated to the test rotating speed;
(6) Calculating and solving the excitation force vectors received on the bearing seats on the two sides of the rotor at the test rotating speed according to the vibration frequency response function vector matrix of the excitation force at different frequencies and the vibration vector at the test rotating speed, which are measured in the test;
(7) and wheel discs on two sides of the rotor are selected as counterweight surfaces, and the excitation force acting on the bearing is eliminated by balancing on the counterweight surfaces, so that dynamic balance fault detection and test are completed.
Wherein, in the step (1), one vibration sensor is respectively arranged in the vertical direction and the horizontal direction of each bearing seat.
In the step (2), the key phase mark is a key phase groove or a reflective sheet.
Further, an eddy current sensor or a photoelectric sensor is adopted to align the key phase mark, and the key phase signal is tested.
In the step (3), the signals of the four vibration sensors and the key phase signals are transmitted to a vibration analyzerAnd measuring four vibration vectors of the two bearing seats, wherein the four vibration vectors comprise amplitudes and phases, and are recorded as:
In the step (4), the frequency response function vector matrix of the journal part excitation force to the bearing seat vibration under different frequencies is as follows:
wherein the content of the first and second substances,Representing the frequency response function of j point y direction excitation force to i point x direction vibration at frequency point omega;
Wherein FFT represents the fast Fourier transform, yj,xithe j point y direction force signal and the i point x direction vibration response signal are respectively.
In the step (5), the vibration vector of the bearing seat at the rotating speed of the dynamic balance test of the unit comprises an amplitude and a phase, and is recorded as:
the vibration vector of the bearing seat under the rotating speed of the dynamic balance test of the unit is shown.
in the step (6), the excitation force generated by the unbalance acts in the horizontal direction and the vertical direction simultaneously, namely acts in the x direction and the y direction, and the unbalance forces in the two directions are respectively:
Wherein U is the magnitude of the unbalanced force,calculating the angle of the unbalanced force in the reverse rotation direction by using a key phase mark as a 0-degree reference;
Written in complex representation, unbalanced forces in both directionsthere are the following relationships between:
considering the vibration response after the unbalanced force excitation in the vertical direction and the horizontal direction acts on the shaft necks at the two sides simultaneously, the following is written:
For brevity, this is:
Wherein the content of the first and second substances,
Further, the excitation force vectors received by the bearing blocks on the two sides of the rotor are calculated according to the measured vibration vectors at the test rotating speed in the following mode:
Wherein the content of the first and second substances,is a matrixThe transposing of (1).
In the step (7), the dynamic balance weights on the weight plates on the two sides of the rotor are calculated in the following manner:
Bearings on two sides are respectively a first bearing and a second bearing, a wheel disc close to the first bearing in wheel discs at two ends of the rotor is a first wheel disc, and a wheel disc close to the second bearing is a second wheel disc; the excitation force on the first bearing isthe excitation force on the second bearing isIn order to eliminate the exciting force on the first bearingBalance weight on wheel discs at two ends of rotorRespectively as follows:
Wherein the content of the first and second substances,Is the amount of weight to be weighed by the first sheave,the weight of the second wheel disc is matched,is directed tomean andsame,. l1Is the distance between the first wheel disc and the first bearing,/2The distance between the first wheel disc and the second wheel disc;
In order to eliminate the exciting force on the second bearingbalance weight on wheel discs at two ends of rotorRespectively as follows:
Wherein the content of the first and second substances,Is the amount of weight to be weighed by the first sheave,The weight of the second wheel disc is matched,is defined by the direction ofSame,. l3The distance between the second wheel disc and the second bearing;
for eliminating unbalanced forces, counterweights on the first and second wheelsRespectively as follows:
bydetermining the dynamic balance weight U on the two discs1,U2；
wherein r is1,r2The weighted radii on the two wheel discs are shown, and omega is the frequency of the rotating circle;
Bythe angle of the counter rotating shaft is opposite to the rotating direction by a corresponding angle at an angle of 0 degrees on the shaft, the dynamic balance weight angles on the two wheel discs are determined, and the dynamic balance test is completed.
has the advantages that: compared with the prior art, the dynamic balance fault detection method for the multi-wheel-disc shafting of the non-trial-weight rotating machine comprises the steps of testing frequency response functions between the vibration of the bearings at the two sides of the rotor and the impact force received by the shaft necks, calculating the excitation force on the shaft necks at the two sides of the rotor according to the two measured vibration of the bearings at the two ends of the rotor, and eliminating unbalanced force through the dynamic balance weights on the discs at the two ends of the rotor. The dynamic balance test without test weight can be realized, and the magnitude and the angle of unbalanced force can be directly detected by vibration test data; meanwhile, vibration in the vertical direction and vibration in the horizontal direction and coupling influence between the vibration and the vibration are comprehensively considered, influence coefficients are not obtained by a method for establishing a rotor dynamics model, and the accuracy of a dynamic balance test is high. In addition, trial weighting is not needed when dynamic balance detection is carried out by the method, the number of dynamic balance tests can be effectively reduced, the dynamic balance test efficiency of the rotary machine is improved, the dynamic balance test risk is reduced, and the method is particularly suitable for shafting dynamic balance fault detection of the rotary machine in the real state of the whole machine.
drawings
FIG. 1 is a flow chart of a dynamic balance fault detection method for a multi-disk shafting of a non-trial-weight rotating machine according to an embodiment of the present invention;
FIG. 2 is a schematic diagram of an apparatus for carrying out the method of the present invention;
wherein: 1-a first bearing vertical vibration sensor; 2-a first bearing horizontal vibration sensor; 3-a first bearing; 4-bond phase slot; 5-an eddy current sensor; 6-a wheel disc; 7-a rotating shaft; 8-second bearing horizontal vibration sensor; 9-a second bearing; 10-a second bearing vertical vibration sensor; 11-a vibration analyzer;
FIG. 3 is a schematic diagram illustrating key phase marks and unbalance force angle definitions during vibration testing in an embodiment;
FIG. 4 is a force signal, a vibration response signal and a frequency response function respectively obtained by the impact test in the example, wherein: 4a is a force impact signal, 4b is a vibration response signal, and 4c is a frequency response function;
FIG. 5 is a graph showing the relationship between the angle determination of the unbalanced force and its horizontal and vertical component forces in the example;
Figure 6 is an excitation force diagram on the two-end wheel disc dynamic balance weight counteracting bearing seat in the embodiment.
Detailed Description
the present invention will be described in further detail with reference to the accompanying drawings and examples.
as shown in fig. 1, in this embodiment, the dynamic balance fault of the rotating machine is detected by the method for detecting a dynamic balance fault of a multi-disk shafting of a non-trial-weight rotating machine according to the present invention, which specifically includes the following steps:
and carrying out dynamic balance test after the complete machine of the rotating machine is assembled or under the actual state of field actual installation.
As shown in fig. 2 and 3, vibration sensors are arranged in the vertical and horizontal directions of bearing seats on both sides of a rotor including multiple disks, for a total of 4 vibration sensors. A key phase groove (or a reflecting sheet is pasted) is formed in the rotating shaft and used as a 0-degree mark on the rotating shaft, and the angle of the reverse rotating direction is defined to be positive according to a pressing balance test method. Alignment of key phase slots (or) by eddy current sensors (or photoelectric sensors)retroreflective sheeting) to test the key phase signal. Send 4 vibration sensor signals and key phase signal to vibration analysis appearance, 4 vibration vectors (containing amplitude and phase place) of 2 bearing frames are obtained in the test, and it is:
as shown in fig. 4, in a static state of the machine, impact excitation forces in vertical and horizontal directions are applied to the exposed shaft necks near the two bearing seats respectively, vibration of the two bearing seats after the impact excitation is tested, and 16 frequency response function vector matrixes of the excitation force of the shaft neck part to the vibration of the bearing seats under different frequencies are obtained:
Wherein:Representing the frequency response function of j point y direction excitation force to i point x direction vibration at frequency point omega;
wherein FFT represents the fast Fourier transform, yj,xirespectively a j-point y-direction excitation force signal and an i-point x-direction vibration response signal.
bearing seat vibration vector under test unit dynamic balance test rotating speedamplitude and phase, recorded as:
as shown in fig. 5, the excitation force generated by the imbalance acts in both the horizontal and vertical directions, i.e., in the x and y directions, and the imbalance forces in the two directions are:
Wherein U is the magnitude of the unbalanced force,calculating the angle of the unbalanced force in the reverse rotation direction by using a key phase mark as a 0-degree reference;
written in complex representation, unbalanced forces in both directionsthere are the following relationships between:
Derived, the vibrational response under excitation considering both vertical and horizontal imbalance forces can be written as:
for brevity, this is:
Wherein the content of the first and second substances,
According to the vector matrix of the force-to-vibration frequency response function and the vibration vector under different frequencies measured by the test, the excitation force vectors received on the two side bearing seats of the rotor under the condition of increasing the speed to the test rotating speed are calculated and obtained:
wherein the content of the first and second substances,Is a matrixThe transposing of (1).
Two wheel discs at two ends of the rotor are selected as counterweight surfaces, and the excitation force acting on the bearing is eliminated through the counterweights on the two wheel discs, so that dynamic balance fault detection and test are completed.
Taking the model shown in the upper diagram of FIG. 6 as an example, to eliminate the excitation force on the first bearingbalance weight on wheel discs at two ends of rotorrespectively as follows:
wherein the content of the first and second substances,is the amount of weight to be weighed by the first sheave,The weight of the second wheel disc is matched,Is defined by the direction ofsame,. l1is the distance between the first wheel disc and the first bearingi, i2The distance between the first wheel disc and the second wheel disc;
taking the model shown in the lower graph of FIG. 6 as an example, to eliminate the second upward exciting forceBalance weight on wheel discs at two ends of rotorrespectively as follows:
Wherein the content of the first and second substances,is the amount of weight to be weighed by the first sheave,the weight of the second wheel disc is matched,Is defined by the direction ofsame,. l3The distance between the second wheel disc and the second bearing;
For eliminating unbalanced forces, counterweights on the first and second wheelsRespectively as follows:
ByDetermining the dynamic balance weight U on the two discs1,U2，
wherein r is1,r2The weighted radii on the two wheel discs are shown, and omega is the frequency of the rotating circle;
bythe angle of the counter rotating shaft is opposite to the rotating direction by a corresponding angle at an angle of 0 degrees on the shaft, the dynamic balance weight angles on the two wheel discs are determined, and the dynamic balance test is completed.
Claims (10)
1. a dynamic balance fault detection method for a non-trial-weight rotating machine multi-wheel-disc shafting is characterized by comprising the following steps:
(1) After the rotating machine is assembled, vibration sensors are respectively arranged in the vertical direction and the horizontal direction of bearing blocks on two sides of the rotor;
(2) Setting a key phase mark on the rotating shaft, using the key phase mark as a 0-degree mark on the rotating shaft, defining the angle of the reverse rotation direction as positive, and testing a key phase signal;
(3) Transmitting the signals of the vibration sensor and the key phase signals to a vibration analyzer to measure four vibration vectors of the two bearing seats;
(4) under the static state of the machine, respectively applying impact excitation forces in the vertical and horizontal directions to the exposed shaft necks near the two bearing seats, testing the vibration of the two bearing seats after the impact excitation, and obtaining frequency response functions of the excitation force of the shaft necks to the vibration of the bearing seats under different frequencies;
(5) testing the vibration of the bearing seat when the unit is accelerated to the test rotating speed;
(6) Calculating and solving the excitation force vectors received on the bearing seats on the two sides of the rotor at the test rotating speed according to the vibration frequency response function vector matrix of the excitation force at different frequencies and the vibration vector at the test rotating speed, which are measured in the test;
(7) And wheel discs on two sides of the rotor are selected as counterweight surfaces, and the excitation force acting on the bearing is eliminated by balancing on the counterweight surfaces, so that dynamic balance fault detection and test are completed.
2. the method for detecting the dynamic balance fault of the multi-disc shafting of the non-trial-weight rotating machine according to claim 1, wherein in the step (1), one vibration sensor is respectively arranged in the vertical direction and the horizontal direction of each bearing seat.
3. the method for detecting the dynamic balance fault of the non-trial-weight rotating mechanical multi-disc shafting according to claim 1, wherein in the step (2), the key phase mark is a key phase slot or a reflector.
4. The method as claimed in claim 3, wherein the key phase signal is tested by aligning the key phase mark with an eddy current sensor or a photoelectric sensor.
5. the method for detecting the dynamic balance fault of the multi-disc shafting of the non-pilot rotating machine according to claim 2, wherein in the step (3), four vibration sensor signals and a key phase signal are transmitted to a vibration analyzer to measure four vibration vectors of two bearing seats, wherein the four vibration vectors include amplitudes and phases, and are recorded as:
6. The method for detecting the dynamic balance fault of the multi-disc shafting of the non-trial-weight rotating machine according to claim 5, wherein in the step (4), the vector matrix of the frequency response functions of the excitation force of the journal portion to the vibration of the bearing seat under different frequencies is as follows:
Wherein the content of the first and second substances,Representing the frequency response function of j point y direction excitation force to i point x direction vibration at frequency point omega;
wherein FFT represents the fast Fourier transform, yj,xithe j point y direction force signal and the i point x direction vibration response signal are respectively.
7. The method for detecting the dynamic balance fault of the multi-disc shafting of the non-trial-weight rotating machine according to claim 6, wherein in the step (5), the vibration vector of the bearing seat at the rotating speed of the dynamic balance test of the unit comprises an amplitude and a phase, and is recorded as:
the vibration vector of the bearing seat under the rotating speed of the dynamic balance test of the unit is shown.
8. the method for detecting the dynamic balance fault of the multi-disc shafting of the non-pilot rotating machine according to claim 7, wherein in the step (6), the excitation force generated by the unbalance acts in the horizontal direction and the vertical direction simultaneously, i.e. acts in the x direction and the y direction, and the unbalance forces in the two directions are respectively:
Wherein U is the magnitude of the unbalanced force,calculating the angle of the unbalanced force in the reverse rotation direction by using a key phase mark as a 0-degree reference;
Written in complex representation, unbalanced forces in both directionsthere are the following relationships between:
considering the vibration response after the unbalanced force excitation in the vertical direction and the horizontal direction acts on the shaft necks at the two sides simultaneously, the following is written:
for brevity, this is:
wherein the content of the first and second substances,
9. The method for detecting the dynamic balance fault of the multi-disk shafting of the non-trial-weight rotating machine according to claim 8, wherein the excitation force vectors applied to the bearing seats on the two sides of the rotor are calculated according to the measured vibration vectors at the test rotating speed in the following manner:
Wherein the content of the first and second substances,Is a matrixThe transposing of (1).
10. the method for detecting the dynamic balance fault of the multi-disc shafting of the non-trial-weight rotating machine according to claim 9, wherein in the step (7), the dynamic balance weights on the balance weight discs on both sides of the rotor are calculated in the following manner:
Bearings on two sides are respectively a first bearing and a second bearing, a wheel disc close to the first bearing in wheel discs at two ends of the rotor is a first wheel disc, and a wheel disc close to the second bearing is a second wheel disc; the excitation force on the first bearing isthe excitation force on the second bearing isin order to eliminate the exciting force on the first bearingBalance weight on wheel discs at two ends of rotorRespectively as follows:
wherein the content of the first and second substances,is the amount of weight to be weighed by the first sheave,The weight of the second wheel disc is matched,is defined by the direction ofSame,. l1is the distance between the first wheel disc and the first bearing,/2the distance between the first wheel disc and the second wheel disc;
in order to eliminate the exciting force on the second bearingbalance weight on wheel discs at two ends of rotorrespectively as follows:
Wherein the content of the first and second substances,is the amount of weight to be weighed by the first sheave,the weight of the second wheel disc is matched,Is defined by the direction ofsame,. l3The distance between the second wheel disc and the second bearing;
for eliminating unbalanced forces, counterweights on the first and second wheelsRespectively as follows:
bydetermining the dynamic balance weight U on the two discs1,U2；
wherein r is1,r2The weighted radii on the two wheel discs are shown, and omega is the frequency of the rotating circle;
byThe angle of the counter rotating shaft is opposite to the rotating direction by a corresponding angle at an angle of 0 degrees on the shaft, the dynamic balance weight angles on the two wheel discs are determined, and the dynamic balance test is completed.
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| CN112327957A (en) * | 2020-09-24 | 2021-02-05 | 哈尔滨雅静振动测试技术有限公司 | Method and device for controlling low-frequency vibration multi-order line spectrum of rotor |
| CN113361030A (en) * | 2021-06-02 | 2021-09-07 | 华能山东石岛湾核电有限公司 | Method for establishing rotary machine dynamic balance calculation application system based on LabVIEW |
| CN114018480A (en) * | 2021-11-24 | 2022-02-08 | 中国科学院重庆绿色智能技术研究院 | Real-time diagnosis method for rotor unbalance fault of large-scale rotating machinery |
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| CN116448319A (en) * | 2023-06-16 | 2023-07-18 | 天津赛象科技股份有限公司 | Tire dynamic balance detection method, device, medium, equipment and terminal |
| RU2818502C1 (en) * | 2023-05-18 | 2024-05-02 | Общество с ограниченной ответственностью "Газпром трансгаз Ухта" | Method of taking readings from phase meter when balancing gas compressor unit and device for its implementation |
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