CN112948978A - Method for calculating knocking force of gearbox free gear pair - Google Patents

Method for calculating knocking force of gearbox free gear pair Download PDF

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CN112948978A
CN112948978A CN202110290572.8A CN202110290572A CN112948978A CN 112948978 A CN112948978 A CN 112948978A CN 202110290572 A CN202110290572 A CN 202110290572A CN 112948978 A CN112948978 A CN 112948978A
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gear
gearbox
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CN112948978B (en
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刘子谦
孙宇
范莎
冯楠
王攀
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Chongqing Tsingshan Industrial Co Ltd
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Abstract

A method for calculating knocking force of an empty gear pair of a gearbox comprises the following steps: 1) enabling each free gear pair to obtain an excitation signal through a vibration exciter, and collecting box body vibration response signals corresponding to each free gear pair; 2) calculating a transfer function of the vibration response of the gearbox body; 3) acquiring a box body vibration steady-state acceleration time domain signal under each gear, and performing Fourier transform to obtain a box body vibration steady-state acceleration frequency domain signal under each gear; 4) obtaining a box body vibration fluctuation acceleration time domain signal under each gear, and performing Fourier transform to obtain a box body vibration fluctuation acceleration frequency domain signal under each gear; 5) calculating to obtain a knocking vibration frequency domain signal of the gearbox body under each gear working condition; 6) calculating by utilizing a transfer function from the knocking force of each free gear pair to the vibration response of the gearbox body and the knocking vibration frequency domain signal of the gearbox body under each gear working condition to obtain the knocking force of each free gear pair; 7) and judging the knocking force of each free gear pair obtained through calculation.

Description

Method for calculating knocking force of gearbox free gear pair
Technical Field
The invention relates to the field of gearboxes, in particular to a method for calculating knocking force of an idler gear pair of a gearbox.
Background
The knocking noise of the automobile gearbox is generated by that an empty gear pair of the gearbox is impacted back and forth due to input torque fluctuation, and then knocking force is generated and transmitted to a box body through a gear-shaft-bearing so that the box body generates vibration and then radiates outwards to generate noise. With the increasing requirements of people on the sound quality of automobiles, the noise problem of the gearbox is increasingly remarkable, and the knocking noise of the gearbox is one of important noise sources, so that the decomposition of the knocking force of each free gear pair is particularly important for researching and optimizing the knocking noise.
At present, a gearbox knocking sensitivity test method disclosed in the publication No. CN109752183A can only judge when the gearbox knocks through transient test working conditions, and cannot judge whether knocking noise is caused by knocking of any empty gear pair.
In the gearbox gear knocking test device and the test and identification method, which are published under the number of CN110044607A, sinusoidal fluctuation torque is used for generating torsional vibration excitation, whether the free gear pair knocks or not is identified through the rotation speed change of each free gear pair, but because the rotation speed sensor adopted in the method is calculated according to the tooth number of the gear, the more the tooth number is, the smaller the error is, the more the required rotation speed sensors are, the more the knocking occurs, the required rotation speed measurement precision is extremely high, and the main reason for quickly and accurately identifying which free gear pair is the gear pair which causes the knocking of the transmission is unrealistic.
Disclosure of Invention
The invention aims to provide a method for calculating the knocking force of the transmission case free gear pair aiming at the corresponding defects of the prior art, which can quickly and accurately identify which free gear pair is the main cause of the transmission knocking by using a small number of sensors and provides a clear direction for optimizing the knocking noise of the transmission case.
The purpose of the invention is realized by adopting the following scheme: a method for calculating knocking force of an empty gear pair of a gearbox comprises the following steps:
1) the vibration exciters arranged on each free gear pair of the gearbox respectively enable each free gear pair to obtain an excitation signal fj(omega), j ═ {1,2,3, …, n }, and a box body vibration response signal y corresponding to each free gear pair of the gearbox is collected through an acceleration sensor arranged on the surface of the gearboxj(ω), j ═ {1,2,3, …, n }, where n is the number of transmission gears and ω is the case vibration frequency;
2) calculating and obtaining a transfer function H from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body according to the following formulaj(ω)：
Figure BDA0002982376400000021
In the formula (f)j(ω) is the excitation signal, yj(omega) is a tank vibration response signal, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, n is the number of gears of the gearbox, and omega is the vibration frequency of the gearbox body;
3) obtaining a box body vibration steady-state acceleration time domain signal V of the gearbox under each gear through a gearbox torque steady-state testi(t), i is {1,2,3, …, n }, i is the gear position of the gearbox, n is the number of the gear positions of the gearbox, t is the duration of the vibration of the box body, and a box body vibration steady-state acceleration time domain signal V of the gearbox under each gear position is obtainedi(t) carrying out Fourier transform to obtain a box body vibration steady-state acceleration frequency domain signal V of the gearbox under each geari(ω) as shown by the following formula:
Vi(ω)＝FFT(Vi(t))，i＝{1,2,3,…,n}
in the formula, Vi(t) is a box body vibration steady-state acceleration time domain signal of the gearbox under each gear, i isThe gear of the gearbox is in gear, n is the number of gears of the gearbox, t is the duration of vibration of the gearbox, and Vi(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
4) obtaining a box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear through a gearbox torque fluctuation testi(t), i is {1,2,3, …, n }, i is the gear position of the gearbox, n is the number of the gear positions of the gearbox, t is the duration time of the vibration of the box body, and the obtained box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear positioni(t) carrying out Fourier transform to obtain a box body vibration fluctuation acceleration frequency domain signal W of the gearbox under each geari(ω) as shown by the following formula:
Wi(ω)＝FFT(Wi(t))，i＝{1,2,3,…,n}
in the formula, Wi(t) is a box body vibration fluctuation acceleration time domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, t is the duration time of box body vibration, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
5) calculating to obtain a gearbox body knocking vibration frequency domain signal Y under each gear working condition according to the following formulai(ω)：
Yi(ω)＝Wi(ω)-Vi(ω)，i＝{1,2,3,…,n}
In the formula, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal V of the gearbox under each geari(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, and omega is the box body vibration frequency;
6) transfer function H from knocking force generated when gear pair corresponding to each gear is free gear pair to vibration response of gearbox bodyj(omega) and gearbox body knocking vibration frequency domain signal Y under each gear working conditioni(omega) are respectively substituted into the following formula to calculate to obtain that the gear pair corresponding to each gear is an empty gear pairThe generated knocking force Fj(ω)：
Figure BDA0002982376400000031
In the formula, Yi(omega) is a gearbox body knocking vibration frequency domain signal under each gear working condition, Fj(omega) is the striking force generated when the gear pair corresponding to each gear is an empty gear pair, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, omega is the vibration frequency of the body, i is the gear of the gearbox at the gear, n is the number of gears of the gearbox, t is the vibration duration of the body, Fi(ω) is a striking force generated when the gear pair corresponding to the i-th gear is an idler gear pair, Hi(omega) is a transfer function from the knocking force generated when the gear pair corresponding to the i gear is an empty gear pair to the vibration response of the gearbox body;
j is the number of a gear pair corresponding to each gear of the gearbox;
7) the calculated knocking force F generated when the gear pair corresponding to each gear is an empty gear pairj(ω) the knocking force F is determinedj(omega) > 0, judging that the gear pair corresponding to the gear participates in knocking, and if the knocking force F is larger than the threshold value, judging that the gear pair corresponding to the gear participates in knockingjAnd (omega) is less than or equal to 0, the gear pair corresponding to the gear can be judged not to participate in knocking.
The acceleration sensor is a piezoelectric acceleration sensor, is low in price, and reduces the cost to the maximum extent under the condition that the test precision and the sensitivity can meet the requirements.
The invention has the following beneficial effects: only a small number of sensors are needed to quickly and accurately identify which empty gear pair is the main cause of the transmission knocking, and then the knocking noise of the gearbox is optimized by optimizing the backlash of the empty gear pair with large knocking contribution.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a schematic diagram of a transfer function from a knocking force generated when a gear pair corresponding to each gear is an empty gear pair to a vibration response of a gearbox casing in the present invention;
FIG. 3 is a frequency domain signal diagram of knocking vibration of a gearbox body under working conditions of various gears in the invention;
fig. 4 is a schematic diagram of the striking force generated when the gear pair corresponding to each gear is an empty gear pair at different box vibration frequencies in the present invention.
Detailed Description
As shown in fig. 1 to 4, a method for calculating a knocking force of an idler gear pair of a transmission comprises the following steps:
1) the vibration exciters arranged on each free gear pair of the gearbox respectively enable each free gear pair to obtain an excitation signal fj(omega), j ═ {1,2,3, …, n }, and a box body vibration response signal y corresponding to each free gear pair of the gearbox is collected through an acceleration sensor arranged on the surface of the gearboxj(ω), j ═ {1,2,3, …, n }, where n is the number of transmission gears and ω is the case vibration frequency;
since the transmission used in this embodiment is a transmission including seven gears, i.e., n-7.
The excitation signal fj(ω) is a random signal, in this embodiment, the excitation signal fj(ω) is the burst random signal, and the resulting excitation signal is as follows:
the excitation signal obtained by the gear pair corresponding to the first gear is f1(omega) corresponding to the case vibration response signal y when the gear pair is empty1(ω)；
The excitation signal obtained by the gear pair corresponding to the second gear is f2(omega) corresponding to the case vibration response signal y when the gear pair is empty2(ω)；
The excitation signal obtained by the gear pair corresponding to the third gear is f3(omega) corresponding to the case vibration response signal y when the gear pair is empty3(ω)；
The excitation signal obtained by the gear pair corresponding to the fourth gear is f4(omega) corresponding to the case vibration response signal y when the gear pair is empty4(ω)；
The fifth gear corresponds toThe gear pair obtains an excitation signal of f5(omega) corresponding to the case vibration response signal y when the gear pair is empty5(ω)；
The excitation signal obtained by the gear pair corresponding to the sixth gear is f6(omega) corresponding to the case vibration response signal y when the gear pair is empty6(ω)；
The excitation signal obtained by the gear pair corresponding to the reverse gear is f7(ω); the box body vibration response signal y corresponding to the gear pair during the empty sleeve7(ω)；
Compared with other random signals, the burst random signal has no leakage and more accurate result; of course, the excitation signal fjThe (ω) may also be a stepped sinusoidal swept frequency signal, which is the least efficient but the most accurate result and is often applied to nonlinear structures.
2) Calculating and obtaining a transfer function H from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body according to the following formulaj(ω)：
Figure BDA0002982376400000051
In the formula (f)j(ω) is the excitation signal, yj(omega) is a tank vibration response signal, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, n is the number of gears of the gearbox, and omega is the vibration frequency of the gearbox body;
the transfer function of the knocking force when the gear pair corresponding to the first gear of the gearbox is empty to the vibration response of the gearbox body is as follows:
Figure BDA0002982376400000052
the transfer function of the knocking force to the vibration response of the gearbox body when the gear pair corresponding to the second gear of the gearbox is empty is as follows:
Figure BDA0002982376400000061
the transfer function of the knocking force to the vibration response of the gearbox body when the gear pair corresponding to the third gear of the gearbox is empty is as follows:
Figure BDA0002982376400000062
the transfer function of the knocking force when the gear pair corresponding to the fourth gear of the gearbox is empty to the vibration response of the gearbox body is as follows:
Figure BDA0002982376400000063
the transfer function of the knocking force when the gear pair corresponding to the fifth gear of the gearbox is empty to the vibration response of the gearbox body is as follows:
Figure BDA0002982376400000064
the transfer function of the knocking force to the vibration response of the gearbox body when the gear pair corresponding to the sixth gear of the gearbox is empty is as follows:
Figure BDA0002982376400000065
the transfer function of the knocking force to the vibration response of the gearbox body when the gear pair corresponding to the reverse gear of the gearbox is empty is as follows:
Figure BDA0002982376400000066
3) obtaining a box body vibration steady-state acceleration time domain signal V of the gearbox under each gear through a gearbox torque steady-state testi(t), i ═ {1,2,3, …, n }, where i is for the transmission caseIn gear shift, n is the gear shift number of the gearbox, t is the duration time of the vibration of the gearbox, and the obtained time domain signal V of the steady-state acceleration of the vibration of the gearbox under each gear is subjected toi(t) carrying out Fourier transform to obtain a box body vibration steady-state acceleration frequency domain signal V of the gearbox under each geari(ω) as shown by the following formula:
Vi(ω)＝FFT(Vi(t))，i＝{1,2,3,…,n}
in the formula, Vi(t) is a box body vibration steady-state acceleration time domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, t is the duration time of box body vibration, and Vi(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
in this embodiment, the steady-state torque test of the transmission is performed by mounting the transmission on a rack, inputting t to an input shaft of the transmission from a first gear, a second gear to a reverse gear by using a driving motor of the rack in sequence to obtain a steady-state torque 50N · m of 60s, and acquiring a box body vibration steady-state acceleration time-domain signal V of the transmission at each gear by using an acceleration sensor arranged on the surface of the transmissioni(t) after Fourier transform, the box body vibration steady-state acceleration frequency domain signals of the gearbox at each gear are as follows:
and a box body vibration steady acceleration frequency domain signal under the first gear:
V1(ω)＝FFT(V1(t))，t＝0～60s；
and (3) a box body vibration steady acceleration frequency domain signal under the second gear:
V2(ω)＝FFT(V2(t))，t＝0～60s；
and (3) box body vibration steady acceleration frequency domain signals under the three gears:
V3(ω)＝FFT(V3(t))，t＝0～60s；
and (3) box body vibration steady acceleration frequency domain signals under the fourth gear:
V4(ω)＝FFT(V4(t))，t＝0～60s；
and a box body vibration steady acceleration frequency domain signal under the fifth gear:
V5(ω)＝FFT(V5(t))，t＝0～60s；
box vibration steady state acceleration frequency domain signals under six gears:
V6(ω)＝FFT(V6(t))，t＝0～60s；
and (3) a box body vibration steady acceleration frequency domain signal under the reverse gear position:
V7(ω)＝FFT(V7(t))，t＝0～60s；
of course, the duration time t of the box body vibration is the duration time of the steady-state torque input to the input shaft of the gearbox by the driving motor of the rack, the duration time can be 20s, 30s and the like, and the longer the duration time is, the higher the accuracy of the obtained box body vibration steady-state acceleration under each gear is.
4) Obtaining a box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear through a gearbox torque fluctuation testi(t), i is {1,2,3, …, n }, i is the gear position of the gearbox, n is the number of the gear positions of the gearbox, t is the duration time of the vibration of the box body, and the obtained box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear positioni(t) carrying out Fourier transform to obtain a box body vibration fluctuation acceleration frequency domain signal W of the gearbox under each geari(ω) as shown by the following formula:
Wi(ω)＝FFT(Wi(t))，i＝{1,2,3,…,n}
in the formula, Wi(t) is a box body vibration fluctuation acceleration time domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, t is the duration time of box body vibration, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
in this embodiment, the torque ripple test of the transmission is also performed by mounting the transmission on a stage, and the transmission is driven while inputting a steady-state torque t of 60s to an input shaft of the transmission 50N · m from a first gear, a second gear, and a reverse gear in sequence by using a driving motor of the stageThe motor also inputs a fixed-frequency fluctuating torque to the input shaft to simulate the ignition frequency of the engine, namely the ignition frequency of the engine is two times in one crank rotation, the ignition frequency is 2 rotating speed/60, in the embodiment, the fluctuating torque input by the driving motor is 20 N.m, the duration is t 60s, the fluctuating frequency is 67Hz, and a box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear is collected by an acceleration sensor arranged on the surface of the gearboxi(t) after Fourier transform, the box body vibration fluctuation acceleration frequency domain signals of the gearbox at each gear are as follows:
a box body vibration fluctuation acceleration frequency domain signal under the first gear:
W1(ω)＝FFT(W1(t))，t＝0～60s；
and (3) a box body vibration fluctuation acceleration frequency domain signal under the second gear:
W2(ω)＝FFT(W2(t))，t＝0～60s；
and (3) box body vibration fluctuation acceleration frequency domain signals under the three gears:
W3(ω)＝FFT(W3(t))，t＝0～60s；
and (3) box body vibration fluctuation acceleration frequency domain signals under the fourth gear:
W4(ω)＝FFT(W4(t))，t＝0～60s；
and a box body vibration fluctuation acceleration frequency domain signal under the fifth gear:
W5(ω)＝FFT(W5(t))，t＝0～60s；
box body vibration fluctuation acceleration frequency domain signals under the six-gear:
W6(ω)＝FFT(W6(t))，t＝0～60s；
box body vibration fluctuation acceleration frequency domain signals under the reverse gear position:
W7(ω)＝FFT(W7(t))，t＝0～60s；
5) calculating to obtain a gearbox body knocking vibration frequency domain signal under each gear working condition according to the following formulaYi(ω)：
Yi(ω)＝Wi(ω)-Vi(ω)，i＝{1,2,3,…,n}
In the formula, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal V of the gearbox under each geari(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, and omega is the box body vibration frequency;
in this embodiment, the knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y1(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y2(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y3(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y4(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y5(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y6(ω)；
The knocking vibration frequency domain signal of the gearbox body of the gearbox under the working condition of the first gear is Y7(ω)；
6) Transfer function H from knocking force generated when gear pair corresponding to each gear is free gear pair to vibration response of gearbox bodyj(omega) and gearbox body knocking vibration frequency domain signal Y under each gear working conditioni(omega) are respectively substituted into the following formulas to calculate and obtain the knocking force F generated when the gear pair corresponding to each gear is an empty gear pairj(ω)：
Figure BDA0002982376400000091
In the formula, Yi(omega) is a variable under each gear working conditionFrequency domain signal of box body knocking vibration of speed box Fj(omega) is the striking force generated when the gear pair corresponding to each gear is an empty gear pair, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, omega is the vibration frequency of the body, i is the gear of the gearbox at the gear, n is the number of gears of the gearbox, t is the vibration duration of the body, Fi(ω) is a striking force generated when the gear pair corresponding to the i-th gear is an idler gear pair, Hi(omega) is a transfer function from the knocking force generated when the gear pair corresponding to the i gear is an empty gear pair to the vibration response of the gearbox body;
j is the number of a gear pair corresponding to each gear of the gearbox;
in this embodiment, when n is 7, the transfer function H of the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the transmission case is set to be 7j(omega) and gearbox body knocking vibration frequency domain signal Y under each gear working conditioni(ω) are respectively substituted into the formula to obtain:
the knocking vibration frequency domain signals of the gearbox body under the working condition of the first gear are as follows:
Figure BDA0002982376400000101
the knocking vibration frequency domain signals of the gearbox body under the working condition of the second gear are as follows:
Figure BDA0002982376400000102
the knocking vibration frequency domain signals of the gearbox body under the working condition of the three gears are as follows:
Figure BDA0002982376400000103
the knocking vibration frequency domain signals of the gearbox body under the working condition of the fourth gear are as follows:
Figure BDA0002982376400000104
the knocking vibration frequency domain signals of the gearbox body under the working condition of the fifth gear are as follows:
Figure BDA0002982376400000105
the knocking vibration frequency domain signals of the gearbox body under the working condition of the six gears are as follows:
Figure BDA0002982376400000111
the knocking vibration frequency domain signals of the gearbox body under the working condition of the reverse gear are as follows:
Figure BDA0002982376400000112
combining the seven formulas into an equation set, the knocking force of the free gear pair corresponding to each gear of the gearbox can be solved, namely:
the knocking force generated when the gear pair corresponding to the first gear is an empty gear pair is F1(ω)；
The knocking force generated when the gear pair corresponding to the second gear is an empty gear pair is F2(ω)；
The knocking force generated when the gear pair corresponding to the third gear is an empty gear pair is F3(ω)；
The knocking force generated when the gear pair corresponding to the fourth gear is an empty gear pair is F4(ω)；
The knocking force generated when the gear pair corresponding to the fifth gear is an empty gear pair is F5(ω)；
The knocking force generated when the gear pair corresponding to the sixth gear is an empty gear pair is F6(ω)；
Corresponding to reverse gearThe knocking force generated when the gear pair is an empty gear pair is F7(ω)；
7) The calculated knocking force F generated when the gear pair corresponding to each gear is an empty gear pairj(ω) the knocking force F is determinedj(omega) > 0, judging that the gear pair corresponding to the gear participates in knocking, and if the knocking force F is larger than the threshold value, judging that the gear pair corresponding to the gear participates in knockingjAnd (omega) is less than or equal to 0, the gear pair corresponding to the gear can be judged not to participate in knocking.
In this embodiment, ω is in the range of 0 to 2000Hz, for example, ω is 26Hz, and calculated as F1(26)＝16.89N，F2(26)＝8.7N，F3(26)＝3.66N，F4(26)＝11.28N，F5(26)＝0N，F6(26)＝1.3N，F7(26) When the gear pair corresponding to the fifth gear of the gearbox and the gear pair corresponding to the reverse gear are free gear pairs, the gear pair does not participate in knocking and is irrelevant to vibration generated by the gearbox; the first-gear idler gear pair has the largest knocking force and thus has the largest contribution to knocking vibration, and then is the fourth-gear idler gear pair, the second-gear idler gear pair, the third-gear idler gear pair and the sixth-gear idler gear pair.
Because the calculation is too complex, in practical application, a computer is used to create a high-tech computing environment capable of performing interactive program design in computer-aided software such as MATLAB and the like, modeling is performed according to the method provided by the invention, corresponding data acquired by a sensor is utilized to perform simulation, the various parameters are obtained, and a corresponding judgment result is obtained after numerical analysis.
In this embodiment, the steady state test of transmission torque on the rig is shown in table 1:
the parameters in the transmission torque ripple test on the bench are shown in table 2:
TABLE 1
Figure BDA0002982376400000121
TABLE 2
Figure BDA0002982376400000122
The above description is only a preferred embodiment of the present invention, and is not intended to limit the present invention, and modifications of the present invention by those skilled in the art are within the scope of the present invention without departing from the spirit of the present invention.

Claims (3)

1. A method for calculating knocking force of an empty gear pair of a gearbox is characterized by comprising the following steps:
1) respectively enabling each free gear pair to obtain excitation signals f through vibration excitersj(omega), j ═ {1,2,3, …, n }, and a box body vibration response signal y corresponding to each free gear pair of the gearbox is acquired through an acceleration sensorj(ω), j ═ {1,2,3, …, n }, where n is the number of transmission gears and ω is the case vibration frequency;
2) calculating and obtaining a transfer function H from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body according to the following formulaj(ω)：
Figure FDA0002982376390000011
In the formula (f)j(ω) is the excitation signal, yj(omega) is a tank vibration response signal, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, n is the number of gears of the gearbox, and omega is the vibration frequency of the gearbox body;
3) for a box body vibration steady-state acceleration time domain signal V of the gearbox under each gear obtained by utilizing a gearbox torque steady-state testi(t) after Fourier transform, obtaining a box body vibration steady acceleration frequency domain signal V of the gearbox under each geari(ω) as shown by the following formula:
Vi(ω)＝FFT(Vi(t))，i＝{1,2,3,…,n}
in the formula, Vi(t) is a box body vibration steady-state acceleration time domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, t is the duration time of box body vibration, and Vi(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
4) a box body vibration fluctuation acceleration time domain signal W of the gearbox under each gear obtained by utilizing a gearbox torque fluctuation testi(t) after Fourier transform, obtaining a box body vibration fluctuation acceleration frequency domain signal W of the gearbox under each geari(ω) as shown by the following formula:
Wi(ω)＝FFT(Wi(t))，i＝{1,2,3,…,n}
in the formula, Wi(t) is a box body vibration fluctuation acceleration time domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, t is the duration time of box body vibration, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal of the gearbox at each gear, and omega is box body vibration frequency;
5) calculating to obtain a gearbox body knocking vibration frequency domain signal Y under each gear working condition according to the following formulai(ω)：
Yi(ω)＝Wi(ω)-Vi(ω)，i＝{1,2,3,…,n}
In the formula, Wi(omega) is a box body vibration fluctuation acceleration frequency domain signal V of the gearbox under each geari(omega) is a box body vibration steady-state acceleration frequency domain signal of the gearbox under each gear, i is the gear of the gearbox, n is the gear number of the gearbox, and omega is the box body vibration frequency;
6) transfer function H from knocking force generated when gear pair corresponding to each gear is free gear pair to vibration response of gearbox bodyj(omega) and gearbox body knocking vibration frequency domain signal Y under each gear working conditioni(omega) are respectively substituted into the following formulas to calculate and obtain the knocking force F generated when the gear pair corresponding to each gear is an empty gear pairj(ω)：
Figure FDA0002982376390000021
In the formula, Yi(omega) is a gearbox body knocking vibration frequency domain signal under each gear working condition, Fj(omega) is the striking force generated when the gear pair corresponding to each gear is an empty gear pair, Hj(omega) is a transfer function from the knocking force generated when the gear pair corresponding to each gear is an empty gear pair to the vibration response of the gearbox body, omega is the vibration frequency of the body, i is the gear of the gearbox at the gear, n is the number of gears of the gearbox, t is the vibration duration of the body, Fi(ω) is a striking force generated when the gear pair corresponding to the i-th gear is an idler gear pair, Hi(omega) is a transfer function from the knocking force generated when the gear pair corresponding to the i gear is an empty gear pair to the vibration response of the gearbox body;
7) the calculated knocking force F generated when the gear pair corresponding to each gear is an empty gear pairj(ω) the knocking force F is determinedj(omega) > 0, judging that the gear pair corresponding to the gear participates in knocking, and if the knocking force F is larger than the threshold value, judging that the gear pair corresponding to the gear participates in knockingjAnd (omega) is less than or equal to 0, the gear pair corresponding to the gear can be judged not to participate in knocking.
2. The method for calculating the knocking force of the gearbox idler gear pair according to claim 1, characterized by comprising the following steps: the excitation signal fjAnd (omega) is a random signal.
3. The method for calculating the knocking force of the gearbox idler gear pair according to claim 1, characterized by comprising the following steps: the acceleration sensor is a piezoelectric acceleration sensor.
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