CN113623279A - Method for treating low-frequency vibration of fan - Google Patents
Method for treating low-frequency vibration of fan Download PDFInfo
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- CN113623279A CN113623279A CN202111051523.5A CN202111051523A CN113623279A CN 113623279 A CN113623279 A CN 113623279A CN 202111051523 A CN202111051523 A CN 202111051523A CN 113623279 A CN113623279 A CN 113623279A
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- 238000000034 method Methods 0.000 title claims abstract description 49
- 238000012360 testing method Methods 0.000 claims abstract description 33
- 230000005284 excitation Effects 0.000 claims abstract description 28
- 238000004364 calculation method Methods 0.000 claims abstract description 10
- 238000006243 chemical reaction Methods 0.000 claims abstract description 4
- 238000012216 screening Methods 0.000 claims abstract description 4
- 230000008569 process Effects 0.000 claims description 8
- 238000003466 welding Methods 0.000 claims 1
- 230000001133 acceleration Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 3
- 230000003247 decreasing effect Effects 0.000 description 3
- 238000004088 simulation Methods 0.000 description 3
- 230000003068 static effect Effects 0.000 description 3
- 241000886569 Cyprogenia stegaria Species 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 239000012530 fluid Substances 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000006378 damage Effects 0.000 description 1
- 230000007547 defect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/662—Balancing of rotors
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/001—Testing thereof; Determination or simulation of flow characteristics; Stall or surge detection, e.g. condition monitoring
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D27/00—Control, e.g. regulation, of pumps, pumping installations or pumping systems specially adapted for elastic fluids
- F04D27/02—Surge control
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04D—NON-POSITIVE-DISPLACEMENT PUMPS
- F04D29/00—Details, component parts, or accessories
- F04D29/66—Combating cavitation, whirls, noise, vibration or the like; Balancing
- F04D29/661—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps
- F04D29/668—Combating cavitation, whirls, noise, vibration or the like; Balancing especially adapted for elastic fluid pumps damping or preventing mechanical vibrations
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
- Structures Of Non-Positive Displacement Pumps (AREA)
Abstract
The invention discloses a method for treating low-frequency-band vibration of a fan, wherein the fan comprises a fan body and a rack; the treatment method comprises the following steps: s1 b: measuring a group of initial vibration data by the fan under a rated working condition, and screening out a frequency band corresponding to a vibration peak value; s2 b: judging the source of the frequency band vibration screened in the S1 b; s3 b: calculating the mode of the fan, namely respectively measuring the natural frequency of the fan body and the integral natural frequency of the fan body and the rack; s4 b: installing a frequency knocking test, and measuring a resonance point of the fan under the excitation of the force hammer; s5 b: starting and stopping the fan, and testing a resonance point under the frequency conversion excitation of the fan; s6 b: and judging whether the natural frequency and the resonance point measured in the S3b-S5b are overlapped with the frequency band screened in the S1b or not, and if so, changing the natural frequency of the fan to avoid resonance. The invention adopts a method of combining analog calculation, knocking test and starting and stopping test to ensure that the vibration excitation source avoids the natural frequency of the fan so as to reduce the vibration of the low frequency band.
Description
Technical Field
The invention belongs to the technical field of fluid machinery, and particularly relates to a method for treating low-frequency-band vibration of a fan.
Background
The low frequency band generally refers to the frequency below 315Hz, the vibration excitation of the frequency part usually contributes greatly to the vibration of the motor, and no effective means is formed at present for treating the low frequency band vibration to reduce the vibration of the whole fan.
At present, common methods for testing a resonance point comprise modal calculation, knocking test and start-stop test, but the three methods cannot judge the source of low-frequency vibration in detail; the mode calculation mainly analyzes the modes of various structural parts at the beginning of design, has wide application range, is not only in the fan industry, but also cannot be realized by common manufacturers. The knocking test is mainly used for testing the rigidity of an actual structural part, when equipment is very complex or a three-dimensional model is not available, simulation analysis is convenient to perform, the knocking test is generally adopted, however, knocking generally can only obtain a 1-order mode, and the subsequent 2-6-order result is inaccurate. The start-stop test is mainly the excitation of an actual working condition, is different from the excitation of knocking, is used for measuring a resonance point, but cannot be solved without combining the two working conditions.
Disclosure of Invention
The invention provides a method for treating low-frequency-band vibration of a fan, aiming at overcoming the defects of the prior art.
In order to achieve the purpose, the invention adopts the following technical scheme: a method for treating low-frequency vibration of a fan comprises the following steps that the fan comprises a fan body and a rack for supporting the fan body; the treatment method comprises the following steps:
s1 b: measuring a group of initial vibration data by the fan under a rated working condition, and screening out a frequency band corresponding to a vibration peak value;
s2 b: judging the source of the frequency band vibration screened in the S1 b;
s3 b: calculating the mode of the fan, namely respectively measuring the natural frequency of the fan body and the integral natural frequency of the fan body and the rack;
s4 b: installing a frequency knocking test, and measuring a resonance point of the fan under the excitation of the force hammer;
s5 b: starting and stopping the fan, and testing a resonance point under the frequency conversion excitation of the fan;
s6 b: and judging whether the natural frequency and the resonance point measured in the S3b-S5b are overlapped with the frequency band screened in the S1b, if so, changing the natural frequency of the fan to avoid resonance, and if not, determining that the vibration source is non-resonance factor interference.
Preferably, the specific steps of the fan mode calculation in S3b are as follows:
s31: obtaining a three-dimensional drawing of the fan body and the rack;
s32: simulating and calculating a 1-6 order mode by adopting structural simulation software, and obtaining the natural frequency of the fan body from six resonance points with low frequency to high frequency;
s33: and (5) assembling the fan body and the rack, and measuring the integral resonance point of the fan body and the rack by adopting the method in S32.
Optionally, the structural simulation software is one of Ansys, Abqus and Adams.
Preferably, the specific steps of the tap test in S4b are as follows:
s41b, assembling the fan body and the rack on site;
s42b, installing a vibration sensor on the fan body and/or the rack;
s43b, knocking the fan body or the rack by using a force hammer to give broadband excitation, and measuring a resonance point by using a sensor.
Preferably, the specific steps of the fan shutdown starting test in S5b are as follows:
s51: the fan body is integrally assembled with the rack;
s52: starting the fan, correspondingly changing the axial frequency in the process that the rotating speed of the fan is from 0 to the rated rotating speed, and measuring the resonance point of the fan body and/or the rack under the excitation of the axial frequency;
s53: and (3) shutting down the fan, correspondingly changing the shaft frequency in the process that the rotating speed of the fan is changed from the rated rotating speed to 0, and measuring the resonance point of the fan body and/or the rack under the excitation of the shaft frequency.
Optionally, in S6b, the method for changing the natural frequency of the wind turbine is to add a support or weld a shaft plate on the wind turbine body and/or the rack.
In conclusion, the invention has the following beneficial effects:
1. in the prior art, when the problem of fan vibration is solved, only imbalance of an impeller and a rotor is generally considered, however, the invention finds that vibration of 2-3 times of shaft frequency and shaft frequency is also an important factor causing fan vibration, so that the invention creatively provides a field balancing method so as to reduce the shaft frequency.
2. The invention measures some resonance points/certain frequency by adopting a method of combining simulation calculation, knocking test and startup and shutdown test, judges whether the resonance points/certain frequency is superposed with the frequency band screened out by the initial vibration data, can judge the source of low-frequency vibration in detail, and can provide a solution according to calculation, for example, the natural frequency of the fan is increased/decreased by increasing the structure, so that the vibration excitation source avoids the natural frequency of the fan, thereby reducing the vibration of the low-frequency band. In addition, under extreme conditions (ultra-large equipment and ultra-complex parts), a vibration source can still be found by combining two or one of the methods, so that a solution is provided.
Drawings
Fig. 1 is a flowchart of a dynamic balancing method for a multi-stage fan according to an embodiment of the present invention.
Fig. 2 is a flow chart of a method of field balancing in fig. 1.
FIG. 3 is a flow chart of the equilibrium disruption method of FIG. 2.
Fig. 4 is a schematic diagram of an arrangement of a vibration acceleration sensor on a blower casing according to a first embodiment of the present invention.
FIG. 5 is a flow chart of the treatment of low-frequency vibration of a fan according to the second embodiment of the present invention.
Fig. 6 is a flow chart of the modal computation of fig. 5.
FIG. 7 is a flow chart of the installation frequency tap test of FIG. 5.
Fig. 8 is a flow chart of the fan shutdown test of fig. 5.
Detailed Description
In order to make the technical solutions of the present invention better understood, the technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention.
A systematic fan vibration reduction method comprises the treatment of the dynamic balance of a multistage fan and the low-frequency-band vibration of the fan, and the problem of matching of dynamic balance of an impeller and a motor and the problem of treatment of a fan vibration source are solved in a targeted manner.
Example one
As shown in fig. 1 to 3, a dynamic balancing method for a multi-stage fan includes the following steps:
s1 a: the single impeller static balance weight is used for penetrating the shaft of the impeller and then placing the impeller in a hard support balancing machine to push the impeller to rotate, the impeller automatically stops stably under the condition of unbalanced weight, after the lowest point is marked, the marking is repeated for a plurality of times (the force for pushing the impeller to rotate each time is approximately the same), if the marking points which are repeated for a plurality of times are all at the lowest point, the marking position is the unbalanced point, and a balance weight is added at the determined unbalanced weight position to ensure that the impeller achieves static balance;
s2 a: the double-sided balance weight of a single impeller is also adopted by a hard support balancing machine, and double-sided balance is carried out at two axial positions of the impeller, so that the residual unbalance of each impeller can reach the G1 standard;
s3 a: the motor rotor is provided with a double-sided dynamic balance weight, and a half key is arranged at the key slot part in the period of time, so that the residual unbalance of the motor rotor reaches the G1 standard;
s4 a: the whole fan adopts a field balancing method to reduce the shaft frequency;
the field balancing method comprises the following steps:
s41 a: assembling the impeller and the motor;
s42 a: arranging two vibration acceleration sensors on a fan shell, specifically, as shown in fig. 4, making vertical planes perpendicular to the rotation center line of an impeller at the installation positions of a first-stage impeller and a last-stage impeller respectively, wherein the vibration acceleration sensors are arranged at the intersection positions of the vertical planes and the fan shell;
s43 a: and balancing weights on the first-stage impeller and the last-stage impeller respectively by adopting a balance destruction method, so that the integral unbalance of the impellers and the motor rotor at all stages reaches the G1 standard.
The specific steps of the equilibrium disruption method in S43a are as follows:
s431: after the fan is normally started, respectively measuring original vibration data of a first-stage impeller and a last-stage impeller under a rated working condition;
s432: defining a zero position, measuring the rotating speed of the impeller by using a photoelectric sensor on the fan, and correspondingly attaching a cursor (a light reflecting strip) on the impeller, so that the position where the light on the impeller is attached can be set to be zero degree;
s433: adding a balance weight at any phase position of the first-stage impeller, starting a fan, and measuring a first group of vibration change data of the first-stage impeller and the last-stage impeller;
s434: adding a balance weight at any phase position of the last-stage impeller, starting the fan, and measuring a second group of vibration change data of the first-stage impeller and the last-stage impeller;
s435: and comparing the phase and vibration amplitude changes of the two groups of vibration change data relative to the original vibration data, and analyzing the unbalanced mass and the specific phase position of the first-stage impeller and the last-stage impeller by software.
In the prior art, when the problem of fan vibration is solved, only imbalance of an impeller and a rotor is generally considered, however, the invention finds that mismatching of the balance of the impeller and the rotor is also an important factor causing the fan vibration, so that the invention creatively provides a field balancing method so as to reduce the shaft frequency.
In the embodiment, the problem of matching of the impeller and the motor in the multistage fan is effectively solved by combining the static balance weight of the single impeller, the double-sided dynamic balance weight of the motor rotor and the double-sided dynamic balance of the field complete machine, so that the residual unbalance of the multistage impeller and the motor rotor is perfectly matched, the vibration intensity of 2-3 frequency multiplication of the shaft frequency and the shaft frequency is reduced, and the fan disclosed by the invention can be suitable for high-end application occasions such as a military fan; in addition, the whole fan shaft is stressed uniformly in the rotation process of the fan, and the service life of the fan is prolonged.
Example two
As shown in fig. 5-8, a method for treating low-frequency vibration of a fan, wherein the fan includes a fan body and a rack for supporting the fan body; the treatment method comprises the following steps:
s1 b: measuring a group of initial vibration data by the fan under a rated working condition, and screening out a frequency band corresponding to a vibration peak value;
s2 b: judging the source of the frequency band vibration screened in the S1 b;
s3 b: calculating the mode of the fan, namely respectively measuring the natural frequency of the fan body and the integral natural frequency of the fan body and the rack;
s4 b: installing a frequency knocking test, and measuring a resonance point of the fan under the excitation of the force hammer;
s5 b: starting and stopping the fan, and testing a resonance point under the frequency conversion excitation of the fan;
s6 b: and judging whether the natural frequency and the resonance point measured in S3b-S5b coincide with the frequency band screened in S1b, if so, changing the natural frequency of the fan to avoid resonance, and if not, determining the vibration source to be non-resonance factor interference (such as vibration caused by non-concentric and non-vertical matching of an impeller and a main shaft, vibration caused by imbalance of the impeller, vibration caused by alignment error of the center of a fan coupling, unreasonable pneumatic design and the like).
The specific steps of the fan mode calculation in the S3b are as follows:
s31: obtaining a three-dimensional drawing of the fan body and the rack;
s32: simulating and calculating a 1-6 order mode by adopting structural simulation software, and obtaining the natural frequency of the fan body from six resonance points with low frequency to high frequency; the structure simulation software can be one of Ansys, Abqus and Adams;
s33: and (5) assembling the fan body and the rack, and measuring the integral resonance point of the fan body and the rack by adopting the method in S32.
The specific steps of the knocking test in the S4b are as follows:
s41b, assembling the fan body and the rack on site;
s42b, installing a vibration sensor on the fan body and/or the rack;
s43b, knocking the fan body or the rack by using a force hammer to give broadband excitation, and measuring a resonance point by using a sensor.
The specific steps of the fan startup and shutdown test in the S5b are as follows:
s51: the fan body and the rack are integrally assembled;
s52: starting the fan, correspondingly changing the axial frequency in the process that the rotating speed of the fan is from 0 to the rated rotating speed, testing whether a resonance point exists on the fan body and/or the rack under the excitation of the axial frequency, and if so, detecting a vibration peak through an instrument; specifically, in the process that the rotating speed of the fan is from 0 to 3000rpm, the shaft frequency is from 0 to 50Hz correspondingly, and the excitation of 0-50Hz is provided;
the specific principle of the above-mentioned axial frequency excitation is as follows: after the fan is started, fluid flows or collides in the flow channel to generate excitation of various different frequency bands, and if the excitation is just matched with the natural frequency of the fan body and/or the rack, the fan generates severe vibration due to resonance.
S53: and (3) shutting down the fan, correspondingly changing the axial frequency in the process that the rotating speed of the fan is from the rated rotating speed to 0, testing whether the fan body and/or the rack have resonance points under the excitation of the axial frequency, and if so, detecting a vibration peak through an instrument.
Through starting and stopping the test, can read the vibration data of fan whole position, the testing result is comprehensive accurate.
The method for changing the natural frequency of the fan in the step S6b comprises the following steps: and a shaft plate is additionally supported or welded on the fan body and/or the rack, so that the excitation source avoids the natural frequency.
In the embodiment, by adopting a method combining simulation calculation, a knocking test and a start-stop test, some resonance points/certain frequency are measured, whether the resonance points/certain frequency is overlapped with a frequency band screened out by initial vibration data or not is judged, the source of low-frequency vibration can be judged in detail, and a solution can be provided according to calculation, for example, the natural frequency of a fan is increased/decreased by increasing/decreasing the natural frequency of the fan in a structure mode, so that a vibration excitation source avoids the natural frequency of the fan, and the vibration of the low-frequency band is reduced. In addition, under extreme conditions (ultra-large equipment and ultra-complex parts), a vibration source can still be found by combining two or one of the methods, so that a solution is provided. .
The above-described embodiments do not limit the scope of the present invention. Any modification, equivalent replacement, and improvement made within the spirit and principle of the above-described embodiments should be included in the protection scope of the technical solution.
Claims (6)
1. A method for treating low-frequency vibration of a fan comprises the following steps that the fan comprises a fan body and a rack for supporting the fan body; the method is characterized by comprising the following steps:
s1 b: measuring a group of initial vibration data by the fan under a rated working condition, and screening out a frequency band corresponding to a vibration peak value;
s2 b: judging the source of the frequency band vibration screened in the S1 b;
s3 b: calculating the mode of the fan, namely respectively measuring the natural frequency of the fan body and the integral natural frequency of the fan body and the rack;
s4 b: installing a frequency knocking test, and measuring a resonance point of the fan under the excitation of the force hammer;
s5 b: starting and stopping the fan, and testing a resonance point under the frequency conversion excitation of the fan;
s6 b: and judging whether the natural frequency and the resonance point measured in the S3b-S5b are overlapped with the frequency band screened in the S1b, if so, changing the natural frequency of the fan to avoid resonance, and if not, determining that the vibration source is non-resonance factor interference.
2. The method for governing the low-frequency band vibration of the fan according to claim 1, wherein the specific steps of the fan mode calculation in S3b are as follows:
s31: obtaining a three-dimensional drawing of the fan body and the rack;
s32: simulating and calculating a 1-6 order mode by adopting structural simulation software, and obtaining the natural frequency of the fan body from six resonance points with low frequency to high frequency;
s33: and (5) assembling the fan body and the rack, and measuring the integral resonance point of the fan body and the rack by adopting the method in S32.
3. The method for governing the vibration of the low-frequency band of the wind turbine according to claim 2, wherein the structural simulation software is one of Ansys, Abqus and Adams.
4. The method for treating the low-frequency band vibration of the fan according to claim 1, wherein the knocking test in the S4b comprises the following specific steps:
s41b, assembling the fan body and the rack on site;
s42b, installing a vibration sensor on the fan body and/or the rack;
s43b, knocking the fan body or the rack by using a force hammer to give broadband excitation, and measuring a resonance point by using a sensor.
5. The method for treating the low-frequency band vibration of the fan according to claim 1, wherein the fan startup and shutdown test in S5b comprises the following specific steps:
s51: the fan body is integrally assembled with the rack;
s52: starting the fan, correspondingly changing the axial frequency in the process that the rotating speed of the fan is from 0 to the rated rotating speed, and measuring the resonance point of the fan body and/or the rack under the excitation of the axial frequency;
s53: and (3) shutting down the fan, correspondingly changing the shaft frequency in the process that the rotating speed of the fan is changed from the rated rotating speed to 0, and measuring the resonance point of the fan body and/or the rack under the excitation of the shaft frequency.
6. The method for treating the low-frequency band vibration of the fan as claimed in claim 1, wherein the method for changing the natural frequency of the fan in S6b is to add a supporting or welding shaft plate on the fan body and/or the rack.
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| CN202111051523.5A CN113623279A (en) | 2021-09-08 | 2021-09-08 | Method for treating low-frequency vibration of fan |
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| CN202111051523.5A CN113623279A (en) | 2021-09-08 | 2021-09-08 | Method for treating low-frequency vibration of fan |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN113623278A (en) * | 2021-09-08 | 2021-11-09 | 绍兴智新机电科技有限公司 | Dynamic balance method of multistage fan |
| CN114321023A (en) * | 2021-12-20 | 2022-04-12 | 常州市永安电机厂有限公司 | Method for solidifying noise resonance point of EC fan by adopting conical shaft sleeve fit |
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| CN114321023A (en) * | 2021-12-20 | 2022-04-12 | 常州市永安电机厂有限公司 | Method for solidifying noise resonance point of EC fan by adopting conical shaft sleeve fit |
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