CN108896303B - Detection method for crack fault characteristics of tooth roots of planetary gear or sun gear - Google Patents
Detection method for crack fault characteristics of tooth roots of planetary gear or sun gear Download PDFInfo
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- CN108896303B CN108896303B CN201810628225.XA CN201810628225A CN108896303B CN 108896303 B CN108896303 B CN 108896303B CN 201810628225 A CN201810628225 A CN 201810628225A CN 108896303 B CN108896303 B CN 108896303B
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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
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/021—Gearings
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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
- G01M13/00—Testing of machine parts
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/028—Acoustic or vibration analysis
Abstract
The invention relates to a method for detecting root crack fault characteristics of a planetary gear or a sun gear, and belongs to the technical field of fault diagnosis and signal processing analysis. According to the invention, by combining windowed vibration separation, synchronous averaging and narrow-band demodulation, whether the planetary gear or the sun gear has root crack fault can be determined according to whether periodic sudden change occurs at the same angle position or not by observing phase demodulation and amplitude demodulation results, and the detection of the root crack fault of the planetary gear and the sun gear of the planetary gear box is realized.
Description
Technical Field
The invention relates to a method for detecting root crack fault characteristics of a planetary gear or a sun gear, and belongs to the technical field of fault diagnosis and signal processing analysis.
Background
Planetary gearboxes are widely used in mechanical transmission systems of various rotary machines and large-scale engineering machines. The planetary gearbox often works in a low-speed heavy-load severe environment, and the gear is easy to peel off, crack and even break the tooth. Once the planetary gearbox fails, the mechanical product stops working and even is replaced integrally, which causes great economic loss.
The internal structure of a planetary gear box is more complex than that of a fixed-axis gear box, and generally comprises a sun gear, a planetary gear, a gear ring and a planet carrier. The planetary gear box is usually fixed with the gear ring in transmission, the sun gear rotates, and the planetary gear rotates and revolves around the sun gear and is meshed with the sun gear and the gear ring simultaneously. The vibration sensor is usually fixedly arranged right above a crescent gear of the planetary gearbox body, and the transmission path of meshing vibration generated by the planetary gear and the sun gear from a meshing point to the vibration sensor is time-varying due to the planetary motion of the planetary gear around the sun gear (as shown in figure 2). Furthermore, there are also a plurality of planet gears in the planetary gearbox, each of which meshes with both the ring gear and the sun gear, which complicates the vibration signals of the planetary gearbox that the vibration sensor picks up. Due to the influence of a time-varying transmission path of a vibration signal and other meshing vibration, complex frequency modulation and amplitude modulation exist in the picked vibration signal, extraction and detection of crack fault characteristics of the planetary gear and the sun gear tooth root are difficult, and the fault diagnosis method of the existing dead axle gear box cannot effectively detect the fault of the planetary gear box.
Disclosure of Invention
The invention provides a method for detecting root crack fault characteristics of a planetary gear or a sun gear, which is used for detecting the root crack fault characteristics of the planetary gear/the sun gear.
The technical scheme of the invention is as follows: a detection method for a root crack fault characteristic of a planetary gear or a sun gear comprises the following steps:
s1, converting the key phase pulse signal of the sun gear input shaft into a key phase pulse signal of a planet carrier output shaft according to the transmission ratio of the planetary gearbox, and performing equal-angle resampling on the original vibration signal of the planetary gear tooth root crack fault or the sun gear tooth root crack fault by using the key phase pulse signal of the planet carrier output shaft as a reference signal to obtain an equal-angle resampling vibration signal;
s2, calculating the peak-to-peak value of the equiangular resampling vibration signal, wherein the maximum peak-to-peak value is the position of the meshing point which is closest to the vibration sensor when the gear is meshed, and defining the meshing point with the maximum peak-to-peak value as the position of the first tooth; calculating the meshing gear sequence of the planetary gear/the sun gear according to a meshing gear sequence calculation formula;
s3, windowing and intercepting the equiangular resampling vibration signal at the first tooth position by adopting a Tukey window with the M tooth width; performing time scale calculation according to the key phase pulse signal of the output shaft of the planet carrier to confirm the time scale position of each circle of rotation of the planet carrier, and then performing windowing interception on the equiangular resampling vibration signal at the corresponding time scale position by using a Tukey window with M tooth widths at the time scale position to obtain a plurality of vibration signals with M tooth widths;
s4, dividing each vibration signal with M tooth widths acquired in the step S3 into vibration signals with M single tooth widths, splicing the separated vibration signals with the single tooth widths at the corresponding windowing positions again according to the meshing tooth sequence, and constructing M groups of artificial vibration signals related to a single planetary gear/sun gear;
s5, selecting a planetary gear rotating shaft/a sun gear rotating shaft as a reference shaft, respectively carrying out angular domain synchronous averaging on the M groups of reconstructed artificial vibration signals, calculating the peak-to-peak value of each group of averaged signals, and selecting a group of artificial vibration signals with the maximum peak-to-peak value to carry out narrow-band demodulation analysis so as to extract the crack fault characteristics of the tooth roots of the planetary gear and the sun gear; and detecting the crack faults of the tooth roots of the planet gears and the sun gears through the periodical abrupt change of the amplitude demodulation diagram and the phase demodulation diagram.
The meshing gear sequence pnfCalculating the formula:
pnf＝mod(nNa,Nf)+1
where mod represents the remainder, N is the number of revolutions of the planet carrier, NaAnd NfAnd respectively representing the tooth number of the gear ring and the tooth number of the fault gear, wherein the fault gear is a planetary gear or a sun gear.
The invention has the beneficial effects that: according to the invention, by combining windowed vibration separation, synchronous averaging and narrow-band demodulation, whether the planetary gear or the sun gear has root crack fault can be determined according to whether periodic sudden change occurs at the same angle position or not by observing phase demodulation and amplitude demodulation results, and the detection of the root crack fault of the planetary gear and the sun gear of the planetary gear box is realized.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a schematic view of a time varying transmission path of the gear mesh vibration of the planetary gearbox in accordance with the present invention;
FIG. 3 is a graph showing the vibration signal of five tooth widths isolated in the present invention;
FIG. 4 is a schematic diagram of the reconstruction of an artificial vibration signal in accordance with the present invention;
FIG. 5 is a planet gear failure raw vibration signal in the present invention;
FIG. 6 is a key phase pulse signal corresponding to a planetary gear fault in the present invention;
FIG. 7 is a speed curve corresponding to a planetary gear failure in accordance with the present invention;
FIG. 8 is a vibration isolation reconstruction artificial vibration signal corresponding to a planetary gear fault in the present invention;
FIG. 9 is a synchronous average artificial vibration signal corresponding to a planetary gear failure in the present invention;
FIG. 10 is a graph of band pass filtering for a planetary gear fault in accordance with the present invention;
FIG. 11 is an amplitude demodulation diagram corresponding to a planetary gear fault in the present invention;
FIG. 12 is a phase demodulation diagram corresponding to a planetary gear failure in the present invention;
FIG. 13 is a graph of the original vibration signature for a sun gear failure in accordance with the present invention;
FIG. 14 is a key phase pulse signal corresponding to a sun gear failure in accordance with the present invention;
FIG. 15 is a speed curve corresponding to a sun gear failure in accordance with the present invention;
FIG. 16 is a vibration isolation reconstruction artificial vibration signal corresponding to a sun gear failure in accordance with the present invention;
FIG. 17 is a synchronous average artificial vibration signal corresponding to a sun gear failure in accordance with the present invention;
FIG. 18 is a band pass filter diagram corresponding to a sun gear failure in accordance with the present invention;
FIG. 19 is an amplitude demodulation diagram corresponding to a sun gear fault in accordance with the present invention;
fig. 20 is a phase demodulation diagram corresponding to a sun gear failure in the present invention.
Detailed Description
Example 1: 1-20, a method for detecting a root crack fault signature of a planetary gear or a sun gear, the method comprising the steps of:
s1, converting the key phase pulse signal of the sun gear input shaft into a key phase pulse signal of a planet carrier output shaft according to the transmission ratio of the planetary gearbox, and performing equal-angle resampling on the original vibration signal of the planetary gear tooth root crack fault or the sun gear tooth root crack fault by using the key phase pulse signal of the planet carrier output shaft as a reference signal to obtain an equal-angle resampling vibration signal;
s2, calculating the peak-to-peak value of the equiangular resampling vibration signal, wherein the maximum peak-to-peak value is the position of the meshing point which is closest to the vibration sensor when the gear is meshed, and defining the meshing point with the maximum peak-to-peak value as the position of the first tooth; calculating the meshing gear sequence of the planetary gear/the sun gear according to a meshing gear sequence calculation formula;
s3, windowing and intercepting the equiangular resampling vibration signal at the first tooth position by adopting a Tukey window with the M tooth width; performing time scale calculation according to the key phase pulse signal of the output shaft of the planet carrier to confirm the time scale position of each circle of rotation of the planet carrier, and then performing windowing interception on the equiangular resampling vibration signal at the corresponding time scale position by using a Tukey window with M tooth widths at the time scale position to obtain a plurality of vibration signals with M tooth widths;
s4, dividing each vibration signal with M tooth widths acquired in the step S3 into vibration signals with M single tooth widths, splicing the separated vibration signals with the single tooth widths at the corresponding windowing positions again according to the meshing tooth sequence, and constructing M groups of artificial vibration signals related to a single planetary gear/sun gear;
s5, selecting a planetary gear rotating shaft/a sun gear rotating shaft as a reference shaft, respectively carrying out angular domain synchronous averaging on the M groups of reconstructed artificial vibration signals, calculating the peak-to-peak value of each group of averaged signals, and selecting a group of artificial vibration signals with the maximum peak-to-peak value to carry out narrow-band demodulation analysis so as to extract the crack fault characteristics of the tooth roots of the planetary gear and the sun gear; and detecting the crack faults of the tooth roots of the planet gears and the sun gears through the periodical abrupt change of the amplitude demodulation diagram and the phase demodulation diagram.
Further, the meshing gear order p may be setnfCalculating the formula:
pnf＝mod(nNa,Nf)+1
where mod represents the remainder, N is the number of revolutions of the planet carrier, NaAnd NfAnd respectively representing the tooth number of the gear ring and the tooth number of the fault gear, wherein the fault gear is a planetary gear or a sun gear.
Example 2: as shown in fig. 1-12, the specific parameters are as follows: 1) sun gear tooth number 28; 2) the number of planetary gear teeth is 20; 3) ring gear tooth number 71; 4) the number of the planet gears is 3; 5) when the signal is subjected to high-frequency sampling, the rotating speed of the input shaft is 900 r/min; the fault types are: a root crack was machined in one of the gear teeth of the planet gear (which was spark machined to a root crack failure depth of 5 mm); the eddy current sensor is arranged at the input shaft of the sun gear and adopts a key phase pulse signal; the original vibration signal of the crack fault of the tooth root of the planetary gear is picked up by a piezoelectric acceleration transducer and is arranged right above a box body and a gear ring of the planetary gear box.
Fig. 1 is a flow chart of the invention, wherein the transmission path of gear meshing vibration from a meshing point to a vibration sensor caused by the planetary motion of a planetary gear around a sun gear is time-varying, the principle of which is shown in fig. 2, fig. 3-4 show the process of separating single gear meshing vibration and reconstructing an artificial vibration signal, and the steps of applying the method of the invention to carry out fault characteristic extraction and detection on the planetary gear root crack fault of the planetary gearbox in the embodiment are as follows:
step1, fixing the piezoelectric acceleration sensor right above the planetary gearbox body and the gear ring in the embodiment, installing the eddy current sensor at the position of the input shaft of the sun gear, and obtaining the sampling frequency of the signal at 51.2 kHz. In the process of high-frequency sampling, the piezoelectric acceleration sensor is guaranteed to be interfered by external environment and noise as little as possible, and the sampling accuracy is guaranteed. The collected primary vibration signal of the planetary gear tooth root crack fault (shown in figure 5) and the key phase pulse signal of the sun gear input shaft (shown in figure 6) have the rotating speed of 900r/min and the rotating speed curve (shown in figure 7).
TABLE 1 planetary gearbox parameters
| Gear wheel | Tooth number (one) |
| Sun gear Ns | 28 |
| |
20 |
| Gear ring Na | 71 |
The transmission ratio of the sun gear and the planet carrier is calculated by the transmission ratio of the planetary gear box:
isc＝(Na+Ns)/Ns
in which s and c represent the sun gear and the planet carrier, respectively, and NaNumber of teeth of ring gear, NsThe number of teeth of the sun gear.
Step2, the key phase signal of the input shaft of the sun gear is converted into a key phase signal of the output shaft of the planet carrier according to the transmission ratio of the planetary gear box. And selecting a key phase pulse signal of an output shaft of the planet carrier as a reference signal to perform equal-angle sampling on the original vibration signal of the crack fault of the tooth root of the planetary gear, thereby eliminating the influence of the fluctuation of the rotating speed.
Step3, calculating the peak-to-peak value of the equiangular resampling vibration signal, wherein the maximum peak-to-peak value is the position of the meshing point which is closest to the vibration sensor when the gear is meshed, and defining the meshing point with the maximum peak-to-peak value as the position of the first tooth. And then calculating the meshing tooth sequence of the planetary gear by a meshing tooth sequence calculation formula. The position of the first tooth is determined according to the maximum peak value, and the meshing tooth sequence of the planet gear can be calculated according to a meshing tooth sequence calculation formula every time the planet carrier rotates once (as shown in table 2).
The meshing tooth sequence calculation formula is as follows:
pnf＝mod(nNa,Nf)+1
where mod represents the remainder, N represents the number of revolutions of the planet carrier, and Na、NfThe number of teeth of the ring gear and the number of teeth of the failure gear are respectively.
TABLE 2 planetary gear engagement order
| |
0 | 1 | 2 | 3 | 4 | 5 | 6 | 7 | 8 | 9 |
| |
1 | 12 | 3 | 14 | 5 | 16 | 7 | 18 | 9 | 20 |
| |
10 | 11 | 12 | 13 | 14 | 15 | 16 | 17 | 18 | 19 |
| |
11 | 2 | 13 | 4 | 15 | 6 | 17 | 8 | 19 | 10 |
In Table 2, N represents the number of revolutions of the carrier, NpxIs the meshing gear sequence of the planet gears.
Step4, firstly, windowing and intercepting the equal-angle resampled signal at a first tooth position by adopting a Tukey window with five tooth widths, carrying out time scale calculation according to the output shaft key phase pulse signal of the planet carrier to confirm the time scale position of each circle of rotation of the planet carrier, then windowing and intercepting the equal-angle resampled vibration signal at a corresponding time scale position by using the Tukey window with five tooth widths every time the planet carrier rotates one circle at the time scale position to obtain a plurality of vibration signals with five tooth widths;
and Step5, dividing each vibration signal with five tooth widths acquired in the Step4 into vibration signals with five single tooth widths, splicing the separated vibration signals with the single tooth widths at the corresponding windowing positions again according to the meshing tooth sequence, and constructing five groups of artificial vibration signals related to a single planetary gear. For the signals illustrated in fig. 3, a set of artificial vibration signals about a single planet gear is constructed as a concatenation of each single tooth width vibration signal at the a position, and so on five sets of artificial vibration signals about a single planet gear are constructed as shown in fig. 4, only a portion of which is shown; fig. 8 shows five sets of artificial vibration signals with respect to a single planetary gear constructed in the present embodiment.
Step6, selecting the rotating shaft of the planetary gear as a reference shaft, and respectively carrying out angular domain synchronous averaging on five groups of artificial vibration signals constructed in the Step5 (as shown in fig. 9). Wherein the average length is 15 sun wheel rotation periods, and the average number of times is 10.
Step7, five groups of synchronous averaged signals are obtained from Step6, the peak-to-peak value of the signals is calculated (as shown in table 3), and a group of synchronous averaged artificial vibration signals with the maximum peak-to-peak value is determined.
TABLE 3 Peak-to-Peak value of Each group of the artificial vibration signals after synchronous averaging
| |
1 | 2 | 3 | 4 | 5 |
| Peak to peak value | 151.4 | 149.7 | 157.5 | 159.2 | 161.9 |
And Step8, performing narrow-band demodulation on the group of synchronous averaged artificial vibration signals with the maximum peak-to-peak value selected at Step 7. As can be seen from table 4, the fifth group of artificial vibration signals is selected to be fourier-transformed to obtain a ratio spectrum, and the meshing frequency with the maximum first-order sideband amplitude is selected as the center frequency to be bandpass-filtered. The signal containing the planetary gear fault is band-pass filtered with a bandwidth of 27 (should be less than the mesh frequency 71) by selecting the 7 th mesh frequency as the center frequency (as shown in fig. 10). The filtered signal is subjected to frequency shift processing, then to inverse fourier transform, and finally to amplitude-phase demodulation to obtain an amplitude demodulation diagram and a phase demodulation diagram (as shown in fig. 11 and 12). It is clear from fig. 11 and 12 that the amplitude-phase demodulation diagrams of the planetary gear fault signals are periodically and suddenly changed at the same angular position respectively, so that the planetary gear fault can be determined. The effectiveness of the invention in extracting and detecting the fault of the planet gear of the planetary gearbox is proved through the analysis of the fault experiment of the planet gear.
Example 3: as shown in fig. 1-4 and 13-20, the specific parameters are as follows: 1) sun gear tooth number 28; 2) the number of planetary gear teeth is 20; 3) ring gear tooth number 71; 4) the number of the planet gears is 3; 5) when the signal is subjected to high-frequency sampling, the rotating speed of the input shaft is 900 r/min; the fault types are: a root crack was machined in one of the sun gear teeth (which was spark machined to a root crack failure depth of 5 mm); the eddy current sensor is arranged at the input shaft of the sun gear and adopts a key phase pulse signal; the original vibration signal of the crack fault of the tooth root of the sun wheel is picked up by a piezoelectric acceleration transducer and is arranged right above a planetary gear box body and a gear ring.
Fig. 1 is a flow chart of the invention, wherein the transmission path of gear meshing vibration from a meshing point to a vibration sensor caused by the planetary motion of a planetary gear around a sun gear is time-varying, the principle of which is shown in fig. 2, fig. 3-4 show the process of separating single gear meshing vibration and reconstructing an artificial vibration signal, and the steps of applying the method of the invention to carry out fault characteristic extraction and detection on the planetary gear root crack fault of the planetary gearbox in the embodiment are as follows:
step1, fixing the piezoelectric acceleration sensor right above the planetary gearbox body and the gear ring in the embodiment, installing the eddy current sensor at the position of the input shaft of the sun gear, and obtaining the sampling frequency of the signal at 51.2 kHz. In the process of high-frequency sampling, the piezoelectric acceleration sensor is guaranteed to be interfered by external environment and noise as little as possible, and the sampling accuracy is guaranteed. The collected primary vibration signal of the crack fault of the root of the sun gear (shown in figure 13) and the key phase pulse signal of the input shaft of the sun gear (shown in figure 14) have the rotating speed of 900r/min and the rotating speed curve (shown in figure 15).
TABLE 4 planetary gearbox parameters
| Gear wheel | Tooth number (one) |
| Sun gear Ns | 28 |
| |
20 |
| Gear ring Na | 71 |
The transmission ratio of the sun gear and the planet carrier is calculated by the transmission ratio of the planetary gear box:
isc＝(Na+Ns)/Ns
in which s and c represent the sun gear and the planet carrier, respectively, and NaNumber of teeth of ring gear, NsThe number of teeth of the sun gear.
Step2, the key phase signal of the input shaft of the sun gear is converted into a key phase signal of the output shaft of the planet carrier according to the transmission ratio of the planetary gear box. And (3) selecting a key phase pulse signal of an output shaft of the planet carrier as a reference signal to carry out equal-angle sampling on the original vibration signal of the crack fault of the root of the sun gear, and eliminating the influence of rotation speed fluctuation.
Step3, calculating the peak-to-peak value of the equiangular resampling vibration signal, wherein the maximum peak-to-peak value is the position of the meshing point which is closest to the vibration sensor when the gear is meshed, and defining the meshing point with the maximum peak-to-peak value as the position of the first tooth. And then the meshing gear sequence of the sun gear is calculated by a meshing gear sequence calculation formula. The position of the first tooth is determined according to the maximum peak value, and the meshing gear sequence of the sun gear can be calculated according to a meshing gear sequence calculation formula every time the planet carrier rotates once (as shown in table 5).
The meshing tooth sequence calculation formula is as follows:
pnf＝mod(nNa,Nf)+1
where mod represents the remainder, N is the number of revolutions of the planet carrier, NaAnd NfAnd respectively representing the tooth number of the gear ring and the tooth number of the fault gear, wherein the fault gear is a planetary gear or a sun gear.
TABLE 5 Sun gear engagement order
| |
0 | 1 | 2 | 3 | 4 | 5 | 6 | 7 | 8 | 9 | 10 | 11 | 12 | 13 |
| |
1 | 16 | 3 | 18 | 5 | 20 | 7 | 22 | 9 | 24 | 11 | 26 | 13 | 28 |
| |
14 | 15 | 16 | 17 | 18 | 19 | 20 | 21 | 22 | 23 | 24 | 25 | 26 | 27 |
| |
15 | 2 | 17 | 4 | 19 | 6 | 21 | 8 | 23 | 10 | 25 | 12 | 27 | 14 |
In Table 5, N represents the number of revolutions of the carrier, NsxIs the meshing gear sequence of the sun gear.
Step4, firstly, windowing and intercepting the equal-angle resampled signal at a first tooth position by adopting a Tukey window with five tooth widths, carrying out time scale calculation according to the output shaft key phase pulse signal of the planet carrier to confirm the time scale position of each circle of rotation of the planet carrier, then windowing and intercepting the equal-angle resampled vibration signal at a corresponding time scale position by using the Tukey window with five tooth widths every time the planet carrier rotates one circle at the time scale position to obtain a plurality of vibration signals with five tooth widths;
step5, dividing each vibration signal with five tooth widths acquired in Step4 into vibration signals with five single tooth widths, and splicing the separated vibration signals with the single tooth widths at the corresponding windowing positions again according to the meshing tooth sequence to construct five groups of artificial vibration signals related to a single sun gear (as shown in fig. 16).
Step6, selecting the sun gear rotating shaft as a reference shaft, and respectively carrying out angular domain synchronous averaging on five groups of artificial vibration signals constructed by Step5 (as shown in fig. 17). Wherein the average length is 15 sun wheel rotation periods, and the average number of times is 10.
And Step7, acquiring five groups of synchronous averaged signals for Step6, calculating the peak-to-peak value of the signals, and determining a group of synchronous averaged artificial vibration signals with the maximum peak-to-peak value.
TABLE 6 Peak-to-Peak value of each group of the synchronized averaged artificial vibration signals
| |
1 | 2 | 3 | 4 | 5 |
| Peak to peak value | 113.8 | 95.1 | 122.5 | 113.7 | 102.4 |
And Step8, performing narrow-band demodulation on the group of synchronous averaged artificial vibration signals with the maximum peak-to-peak value selected at Step 7. As can be seen from table 6, the third group of artificial vibration signals is selected to perform fourier transform to obtain a ratio spectrum, and the meshing frequency with the maximum first-order sideband amplitude is selected as the center frequency to perform bandpass filtering. Where the 2 nd order mesh frequency is chosen to be the center frequency and the bandwidth is 35 (should be less than the mesh frequency 71) for bandpass filtering (as shown in figure 18). The filtered signal is subjected to frequency shift processing, then to inverse fourier transform, and finally to amplitude-phase demodulation to obtain an amplitude demodulation diagram and a phase demodulation diagram (as shown in fig. 19 and 20). As is clear from fig. 19 and 20, the amplitude-phase demodulation diagrams of the sun gear fault signals are periodically and suddenly changed at the same angular position, so that it can be determined that the sun gear is in fault. The effectiveness of the invention in extracting and detecting the sun gear fault of the planetary gearbox is proved through the analysis of the sun gear fault experiment.
While the present invention has been described in detail with reference to the embodiments shown in the drawings, the present invention is not limited to the embodiments, and various changes can be made without departing from the spirit of the present invention within the knowledge of those skilled in the art.
Claims (1)
1. A detection method for the root crack fault characteristics of a planetary gear or a sun gear is characterized by comprising the following steps: the method comprises the following steps:
s1, converting the key phase pulse signal of the sun gear input shaft into a key phase pulse signal of a planet carrier output shaft according to the transmission ratio of the planetary gearbox, and performing equal-angle resampling on the original vibration signal of the planetary gear tooth root crack fault or the sun gear tooth root crack fault by using the key phase pulse signal of the planet carrier output shaft as a reference signal to obtain an equal-angle resampling vibration signal;
s2, calculating the peak-to-peak value of the equiangular resampling vibration signal, wherein the maximum peak-to-peak value is the position of the meshing point which is closest to the vibration sensor when the gear is meshed, and defining the meshing point with the maximum peak-to-peak value as the position of the first tooth; calculating the meshing gear sequence of the planetary gear/the sun gear according to a meshing gear sequence calculation formula;
s3, windowing and intercepting the equiangular resampling vibration signal at the first tooth position by adopting a Tukey window with the M tooth width; performing time scale calculation according to the key phase pulse signal of the output shaft of the planet carrier to confirm the time scale position of each circle of rotation of the planet carrier, and then performing windowing interception on the equiangular resampling vibration signal at the corresponding time scale position by using a Tukey window with M tooth widths at the time scale position to obtain a plurality of vibration signals with M tooth widths;
s4, dividing each vibration signal with M tooth widths acquired in the step S3 into vibration signals with M single tooth widths, splicing the separated vibration signals with the single tooth widths at the corresponding windowing positions again according to the meshing tooth sequence, and constructing M groups of artificial vibration signals related to a single planetary gear/sun gear;
s5, selecting a planetary gear rotating shaft/a sun gear rotating shaft as a reference shaft, respectively carrying out angular domain synchronous averaging on the M groups of reconstructed artificial vibration signals, calculating the peak-to-peak value of each group of averaged signals, and selecting a group of artificial vibration signals with the maximum peak-to-peak value to carry out narrow-band demodulation analysis so as to extract the crack fault characteristics of the tooth roots of the planetary gear and the sun gear; detecting the crack faults of the tooth roots of the planet gears and the sun gears through the periodical sudden change of the amplitude demodulation diagram and the phase demodulation diagram;
the meshing gear sequence pnfCalculating the formula:
pnf＝mod(nNa,Nf)+1
where mod represents the remainder, N is the number of revolutions of the planet carrier, NaAnd NfAnd respectively representing the tooth number of the gear ring and the tooth number of the fault gear, wherein the fault gear is a planetary gear or a sun gear.
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| CN112113767B (en) * | 2020-09-29 | 2021-06-08 | 昆明理工大学 | Bearing fault diagnosis method based on proportional band selection criterion |
| CN112231859B (en) * | 2020-10-11 | 2022-05-17 | 昆明理工大学 | Method for simulating local fault vibration of planet wheel of planetary gear box |
| CN113865860A (en) * | 2021-08-25 | 2021-12-31 | 浙江运达风电股份有限公司 | Gear tooth breakage fault diagnosis method based on frequency conversion sideband RMS trend analysis |
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