CN114370997B - Dynamic shunt testing method for interior of planetary gear train - Google Patents

Abstract

The invention discloses a dynamic shunt test method inside a planetary gear train. The internal dynamic shunt test method of the planetary gear train includes the following steps: S1, setting strain gauge measuring points on the sun gear and the tooth root of the ring gear and pasting the strain gauges at the strain gauge measuring points; Install the speed-measuring reflective tape and the speed-measuring probe at the point; S2, carry out the test, and obtain the strain data and speed data respectively collected by the strain gauge measuring point and the speed measuring point under the record of the external base source clock; S3, the time-domain laser pulse of the output shaft Trigger synchronously with the time-domain laser pulse of the input shaft to establish the correspondence between the strain data and the planetary gear; S4, according to the correspondence between the planetary gear and the strain data, re-divide the strain data from the perspective of the planetary gear; The strain data is used to calculate the dynamic split of the load power of the planetary gear.

Description

A method for testing internal dynamic shunting of a planetary gear train

technical field

The invention relates to the field of mechanical transmission, in particular to a dynamic shunt test method inside a planetary gear train.

Background technique

The planetary gear train is an important form in the field of mechanical transmission, and is widely used in the mechanical industry due to its high power, high efficiency, and compact structure. The internal dynamic shunting of the planetary gear system refers to the shunting of the load power and transmission power of each planetary gear during the operation of the planetary gear system. It is specifically manifested in the dynamic meshing strain of each planetary gear with the sun gear and ring gear, which affects the life of the planetary gear system. Key factor. By means of testing, the internal dynamic shunt during the motion of the planetary gear train can be detected, which can provide sufficient data support for the design, maintenance and overhaul of the planetary gear train.

The traditional shunt test method within the planetary gear train does not take into account the contingency and error of the experimental test, and has the following disadvantages:

1) Due to the complicated and cumbersome testing process, the mapping relationship between the meshing strain of the sun gear and the planetary gear is easy to be lost, resulting in the meshing strain not having the specificity corresponding to the planetary gear, so the test is accidental.

2) Due to the huge test process and the need for multi-faceted cooperation, it is easy to cause the strain data and the rotational speed data to fail to correspond, resulting in certain systematic errors in the data processing after the test.

Contents of the invention

The purpose of the present invention is to overcome the lack of contingency and error in the internal shunt test existing in the prior art, and provide a dynamic shunt test method inside the planetary gear train. The test of the strain gauge and the rotating speed is triggered synchronously, so that data synchronization.

In order to realize the above-mentioned purpose of the invention, the present invention provides the following technical solutions:

A method for testing internal dynamic shunting of a planetary gear train, comprising the following steps:

S1, set strain gauge measuring points on the sun gear and ring gear tooth roots respectively and paste strain gauges at the strain gauge measuring points; set speed measuring points on the output shaft and input shaft and install speed sensors at the speed measuring points;

S2, carry out the test, under the record of the external base source clock, obtain the strain data and rotational speed data respectively collected by the strain gauge measuring point and the rotating speed measuring point; among them, the strain data and the The speed data is recorded as effective data, and the corresponding relationship between strain data and planetary gear is established according to the effective data;

S3, according to the corresponding relationship between the planetary gear and the strain data, re-divide the strain data collected by each strain measuring point, and obtain the strain data from the perspective of the planetary gear;

S4, calculate the dynamic load power split of the planetary gear according to the strain data from the perspective of the planetary gear.

Preferably, the number of strain gauge measuring points in the step S1 is consistent with the number of planetary gears, and each group of strain gauge measuring points has two strain gauges.

Preferably, in the step S1, the speed measuring sensor is a speed measuring reflective tape and a speed measuring probe, the strain gauge includes a sun gear strain gauge and a ring gear strain gauge, and the speed measuring reflective tape includes an output shaft speed measuring reflective tape and an input shaft speed measuring reflective tape, The speed measuring probe includes the output shaft speed measuring probe and the input shaft speed measuring probe; the speed measuring reflective tape is parallel to the axis of the planetary wheel, and the speed measuring probe and the ring gear strain gauge are directly connected to the planet carrier relative to the output shaft; the speed measuring reflective tape of the output shaft is connected to the planet carrier The planetary gear corresponds; the input shaft is directly connected with the sun gear, and the speed-measuring reflective tape of the input shaft corresponds to a strain gauge of the sun gear.

Preferably, in the step S2, the signals detected by the output shaft and the input shaft speed sensor are recorded as the output shaft time-domain laser pulse signal and the input shaft time-domain laser pulse signal, and the laser pulse synchronous trigger method is used to make the output shaft time-domain laser pulse signal The pulse signal and the time-domain laser pulse signal of the input shaft are triggered synchronously, and the corresponding relationship between the strain data and the planetary gear is established according to the synchronously triggered strain data and rotational speed data.

Preferably, in the step S4, the strain data of the planetary gear as a perspective includes strain data of the planetary gear relative to the sun gear and strain data of the planetary gear relative to the ring gear.

Preferably, the step S5 includes the following steps: based on the corresponding relationship between strain and meshing force, according to the strain data of the planetary gear relative to the sun gear and the strain data of the planetary gear relative to the ring gear, the meshing force of the sun gear and the meshing force of the ring gear are obtained ;Based on the force analysis, calculate the planetary carrier force corresponding to the planetary gear according to the sun gear meshing force and the ring gear meshing force, and then calculate the dynamic split of the planetary gear transmission power based on the formula conversion based on the planetary carrier force.

Preferably, the step S1 collects the strain data of the measuring point of the sun gear strain gauge based on the direct cooperation relationship between the slip ring rotor and the slip ring stator; the direct cooperation relationship between the slip ring rotor and the slip ring stator is as follows:

The transition flange is connected to the input end of the input flange, the output end of the input shaft connecting plate is connected to the input shaft of the sun gear, and the output end of the input shaft connecting plate is sleeved outside the input shaft of the sun gear; the input shaft connecting plate outputs The slip ring rotor and the slip ring stator are sleeved in turn outside the end; the slip ring rotor is splined connected with the output end of the input shaft connection plate; when the sun gear rotates, the slip ring stator is fixed; one end of the sensor signal line is connected to the sun gear The strain gauge is connected, and the other end of the sensor signal line is connected to the slip ring rotor; the sensor signal line is routed through the axis of the input shaft connection plate and the line groove of the transition flange.

Preferably, the strain data collected in step S2 needs to be preprocessed according to the transformation matrix;

The calculation of the conversion matrix includes the following steps:

S21, carry out calibration measurement for the fixed strain gauge, the gear with the fixed strain gauge is set as the test gear, and the gear meshed with the test gear for loading is set as the loading gear; in the standard meshing position, the loading gear is loaded with two different gears After loading, the strain of the strain gauge is collected, and the standard value of the strain is calculated according to the strain influence coefficient;

S22, selecting a meshing position other than the tooth top, loading different loads, and collecting the strain of the strain gauge;

^S23 , calculate the first load F _f ^o and the first strain F _no according to the strain measurement standard value; then combine the strain collected during the test and the load during the test to calculate the relative error δ _f , δ _n , and determine whether the relative error meets the requirement, If the relative error does not meet the requirement, execute step S22; if the relative error meets the requirement, execute step S24;

S24, judging whether the number of tests is sufficient, if the number of tests is not enough, execute step S22, if the number of tests is sufficient, execute step S25;

S25. Calculate the transformation matrix.

Preferably, the calculation method of the strain measurement standard value in the step S21 is as follows:

S ₁ ＝a ₁₁ ^o F _n1 +a ₁₂ ^o F _f1

S ₂ ＝a ₂₁ ^o F _n2 +a ₂₂ ^o F _f2

Among them, the load of the first test is F _f1 , and the corresponding collected strain is F _n1 ; the load of the second test is F _f2 , and the corresponding collected strain is F _n2 ; a ₁₁ ^o , a ₁₂ ^o , a ₂₁ ^o and a ₂₂ ^o is the strain influence coefficient; S ₁ is the strain standard value of the first test, and S ₂ is the strain standard value of the second test.

Preferably, the calculation method of F _n ^o , F _f ^o and relative error in step S23 is as follows:

Wherein, the first load F _n ^o and the first strain F _f ^o are calculated by the following method.

{F ^o }={a ^o } ^-1 {S}

Among them, F ^o = [F _n ^o , F _f ^o ], a ^o —— standard matrix of strain influence coefficient, S = [S _f , S _n ], S _f and S _n are respectively F _f ^o and F _n ^o The corresponding metric value.

The relative error calculation method is as follows:

Among them, F _f is the load during the test, and F _n is the collected strain.

Compared with the prior art, the present invention has the beneficial effect: the patent establishes the mapping relationship between the meshing strain and the planetary gear by designing the corresponding relationship between the measuring point arrangement of the sun gear strain gauge and the measuring point arrangement of the ring gear strain gauge and the planetary gear; Design the relative relationship between strain gauges, speed-measuring reflective tapes and speed-measuring probes, realize automatic synchronous triggering, and create conditions for synchronous correspondence between strain data and rotational speed data in the time domain.

Description of drawings:

Fig. 1 is a flow chart of the dynamic shunt test method inside the planetary gear train in exemplary embodiment 1 of the present invention;

Fig. 2 is an arrangement diagram of the strain gauges of the four-planetary gear train in exemplary embodiment 1 of the present invention;

Fig. 3 is a schematic diagram of the corresponding relationship between strain measuring points and rotating speed measuring points in exemplary embodiment 1 of the present invention;

4 is a schematic diagram of a laser pulse synchronous triggering method in exemplary embodiment 1 of the present invention;

Fig. 5 is a schematic diagram of division of strain data from the perspective of planetary gears in Exemplary Embodiment 1 of the present invention;

Fig. 6 is a schematic diagram of force analysis of planetary gears in Exemplary Embodiment 1 of the present invention;

Fig. 7 is a schematic diagram of the strain measurement installation of the sun gear in the exemplary embodiment 1 of the present invention.

Fig. 8 is a schematic diagram of the standard meshing position of exemplary embodiment 1 of the present invention; that is, the tooth top meshing position corresponding to the tooth groove ② is selected as the standard meshing position, and the strain of the strain gauge is collected after the loading gear is loaded with two different loads.

Reference signs: 1-planetary wheel axis, 2-input shaft speed measuring probe, 3-input shaft speed measuring reflective tape, 4-sun gear strain gauge, 5-output shaft speed measuring reflective tape, 6-output shaft speed measuring probe, 7- Ring gear strain gauge, 8-sun gear, 9-slip ring rotor, 10-slip ring stator, 11-input shaft connection plate, 12-sensor signal line, 13-transition flange.

Detailed ways

The present invention will be further described in detail below in conjunction with test examples and specific embodiments. However, it should not be understood that the scope of the above subject matter of the present invention is limited to the following embodiments, and all technologies realized based on the content of the present invention belong to the scope of the present invention.

Example 1

As shown in FIG. 1 , this embodiment provides a method for testing internal dynamic shunting of a planetary gear train, which includes the following steps:

S1, set strain gauge measuring points on the sun gear and ring gear tooth roots respectively and paste strain gauges at the strain gauge measuring points; set speed measuring points on the output shaft and input shaft and install speed sensors at the speed measuring points;

S2, carry out the test, under the record of the external base source clock, obtain the strain data and rotational speed data respectively collected by the strain gauge measuring point and the rotating speed measuring point; among them, the strain data and the The speed data is recorded as effective data, and the corresponding relationship between strain data and planetary gear is established according to the effective data;

S3, according to the corresponding relationship between the planetary gear and the strain data, re-divide the strain data collected by each strain measuring point, and obtain the strain data from the perspective of the planetary gear;

S4, calculate the dynamic load power split of the planetary gear according to the strain data from the perspective of the planetary gear.

In this embodiment, through the relative relationship between the strain gauge measuring points and the rotating speed measuring points, and using synchronous triggering, the obtained sun gear meshing strain and the ring gear meshing strain have a mapping relationship with the planetary gear, realizing the synchronization of the strain data and the rotating speed data in the time domain correspond.

Exemplarily, the number of strain gauge measuring points is consistent with the number n of planetary gears, and each set of measuring points has two strain gauges. Since the number of measuring points of the strain gauge is consistent with the number n of the planetary gear, the mapping relationship between the meshing strain and the planetary gear can be established through the corresponding relationship between the measuring point arrangement of the sun gear strain gauge and the measuring point arrangement of the ring gear strain gauge and the planetary gear. As shown in Figure 2, step S1 takes a four-planetary gear train as an example, and pastes strain gauges on the tooth roots of the sun gear and the ring gear. Figure 2(a) shows the layout of the sun gear strain gauges, and Figure 2(b) shows The arrangement diagram of the ring gear strain gauge. In this embodiment, the corresponding relationship between the measuring point arrangement of the sun gear strain gauge and the measuring point arrangement of the ring gear strain gauge and the planetary gear is designed, and the mapping relationship between the meshing strain and the planetary gear is established.

Exemplarily, in step S1, the speed measuring sensor is a speed measuring reflective tape and a speed measuring probe, and the strain gauge, the speed measuring reflective tape and the speed measuring probe are installed according to the corresponding relationship between strain gauge measuring points and rotational speed measuring points as shown in FIG. 3 . The strain gauge includes a sun gear strain gauge 4 and a ring gear strain gauge 7, the speed measuring reflective tape includes an output shaft speed measuring reflective tape 5 and an input shaft speed measuring reflective tape 3, and the speed measuring probe includes an output shaft speed measuring probe 6 and an input shaft speed measuring probe 2; The speed-measuring reflective tape is parallel to the axis line 1 of the planetary wheel, and the speed-measuring probe and the ring gear strain gauge are directly connected to the planet carrier relative to the output shaft; the speed-measuring reflective tape of the output shaft corresponds to a planetary wheel on the planet carrier (denoted as planetary gear a); The input shaft is directly connected with the sun gear, and the speed measuring reflective tape of the input shaft corresponds to a sun gear strain gauge (referred to as sun gear strain gauge a). The speed measuring probe measures the speed by capturing the signal returned after the emitted laser pulse signal encounters the speed measuring reflective tape, and obtains the speed data. In this embodiment, by designing the relative relationship between the strain gauges, the speed-measuring reflective tape and the speed-measuring probe, automatic synchronous triggering is realized, creating conditions for synchronous correspondence between strain data and speed data in the time domain.

Exemplarily, as shown in Figure 4, the signals detected by the output shaft and the input shaft speed sensor are recorded as the output shaft time domain laser pulse signal and the input shaft time domain laser pulse signal, and the laser pulse synchronous trigger method is used to make the output shaft time domain The laser pulse signal and the time-domain laser pulse signal of the input shaft are triggered synchronously, and the corresponding relationship between the strain data and the planetary gear is established according to the strain data and rotational speed data after synchronous triggering. In this embodiment, a ring gear strain gauge (denoted as ring gear strain gauge a) is arranged directly above the ring gear, when the output shaft time-domain laser pulse and the input shaft time-domain laser pulse are synchronously triggered (the effective data in the figure starts Time), which means that both the planetary gear a and the sun gear strain gauge a are directly above the planetary gear train, combined with the rotation direction of the planetary carrier, the corresponding relationship between the planetary gear and the strain data, and the strain data and the rotational speed data can be established. In this embodiment, the ring gear strain gauge a can also be set at other positions, and the principle of synchronous triggering is the same. When synchronizing, synchronous triggering is realized. At this time, the positions of the ring gear strain gauge a, the planetary gear a and the sun gear strain gauge a have a corresponding relationship. The data at the time after synchronization is valid data, and the strain data can be established according to the valid data Correspondence with the planetary gear.

Exemplarily, as shown in FIG. 5 , according to the corresponding relationship between the planetary gear and the strain data, the strain data collected at each strain measuring point is re-divided to obtain the strain data from the perspective of the planetary gear. If the strain gauge is installed on the planetary gear, the movement of the planetary gear will easily cause the data collection line to wind, so the strain gauge is installed on the sun gear and the tooth root of the ring gear. Because of the rotation and revolution of the planetary carrier and the planetary gear, not all the strain gauges can have data at the same time, and not all the data collected by the strain gauges are the data of the same planetary gear. Therefore, the data collected by the strain gauges need to be The strain data is re-divided to obtain the strain data from the perspective of the planetary gear. In this embodiment, the four-planetary gear train is taken as an example. Since the number of strain gauge measuring points set on the tooth roots of the sun gear and the ring gear is consistent with the number of planetary gears, it can be quickly and conveniently re-divided as shown in Figure 5. The strain data for the viewing angle of the planet gear.

Exemplarily, in step S4, the dynamic distribution of load power of the planetary gear is completed based on the strain data from the perspective of the planetary gear; the strain data from the perspective of the planetary gear include the strain data of the planetary gear relative to the sun gear and the strain data of the planetary gear relative to the ring gear ; Based on the corresponding relationship between strain and meshing force, according to the strain data of the planetary gear relative to the sun gear and the strain data of the planetary gear relative to the ring gear, the meshing force of the sun gear and the meshing force of the ring gear are obtained; as shown in Figure 6, based on the force According to the analysis, the planetary carrier force corresponding to the planetary gear is calculated according to the meshing force of the sun gear and the ring gear, and then the dynamic split of the power transmitted by the planetary gear is calculated based on the formula conversion based on the force of the planetary carrier.

Exemplarily, as shown in FIG. 7, the strain data of the sun gear is collected based on the direct fit relationship between the slip ring rotor and the slip ring stator;

The transition flange 13 is connected to the input end of the input flange 11, the output end of the input shaft connection plate 11 is connected to the input shaft of the sun gear 8, and the output end of the input shaft connection plate 11 is sleeved outside the input shaft of the sun gear 8; A slip ring rotor 9 and a slip ring stator 10 are sleeved outside the output end of the input shaft connection plate 11 in sequence; the slip ring rotor 9 is splined connected with the output end of the input shaft connection plate 11; when the sun gear rotates, the slip ring stator 10 Fixed; one end of the sensor signal line 12 is connected to the sun gear strain gauge, and the other end of the sensor signal line 12 is connected to the slip ring rotor 9; the sensor signal line 12 passes through the line of the input shaft connection plate 11 axis and the transition flange 13 The slot realizes the wiring setting.

Because the measuring point of the sun gear strain gauge moves with the meshing process, it is easy to cause the data collection line to wind. Therefore, this application uses the direct cooperation relationship between the slip ring rotor and the slip ring stator to measure the tooth root meshing strain of the strain gauge measuring point on the active sun gear. ;The sensor signal line as a whole moves with the sun gear, and the strain data reading is realized through the slip ring stator, that is, the sensor signal line and the sun gear remain stationary, and the data acquisition and receiving end of the sensor also remains stationary; When the process is moving, the sensor signal wire is wound.

In this embodiment, the inner diameter of the slip ring rotor 9 is designed according to the outer diameter of the output end of the input shaft connection plate 11; the outer diameter of the slip ring rotor 9 is designed in combination with the installation and positioning relationship; the slip ring is designed in combination with the length and positioning relationship of the input shaft connection plate 11 The length of the rotor 9 is combined with the length and inner and outer diameters of the slip ring rotor 9, and the splines at the output end of the slip ring rotor 9 and the input shaft connection plate 11 are designed using the spline national standard design process. The inner and outer diameters of the slip ring stator 10 are selected based on the outer diameter of the slip ring rotor 9 and the inner diameter of the outer ring of the planetary gear train, the length of the slip ring stator 10 is designed in combination with the installation and positioning relationship, and the surface roughness of the inner ring of the stator is selected in combination with the requirements for signal connection.

Exemplarily, the strain data collected in step S2 needs to be preprocessed according to the transformation matrix;

The calculation of the conversion matrix includes the following steps:

S21, carry out calibration measurement for the fixed strain gauge, the gear with the fixed strain gauge is set as the test gear, and the gear meshed with the test gear for loading is set as the loading gear; in the standard meshing position, the loading gear is loaded with two different gears After loading, the strain of the strain gauge is collected, and the standard value of the strain is calculated according to the strain influence coefficient;

Among them, as shown in Figure 8, the meshing position of the tooth top corresponding to the tooth groove ② is selected as the standard meshing position, and the strain of the strain gauge is collected after the loading gear is loaded with two different loads.

Among them, the calculation method of strain measurement standard value is as follows:

S ₁ ＝a ₁₁ ^o F _n1 +a ₁₂ ^o F _f1

S ₂ ＝a ₂₁ ^o F _n2 +a ₂₂ ^o F _f2

Among them, the load of the first test is F _f1 , and the corresponding collected strain is F _n1 ; the load of the second test is F _f2 , and the corresponding collected strain is F _n2 ; a ₁₁ ^o , a ₁₂ ^o , a ₂₁ ^o and a ₂₂ ^o is the strain influence coefficient, S ₁ is the strain standard value of the first test, and S ₂ is the strain standard value of the second test.

S22, selecting a meshing position other than the tooth top, loading different loads, and collecting the strain of the strain gauge;

^S23 , calculate the first load F _f ^o and the first strain F _no according to the strain measurement standard value; then combine the strain collected during the test and the load during the test to calculate the relative error δ _f , δ _n , and determine whether the relative error meets the requirement, If the relative error does not meet the requirements, execute step S22; if the relative error meets the requirements, execute step S24;

Wherein, the first load F _f ^o and the first strain F _n ^o are calculated by the following method.

{F ^o }={a ^o } ^-1 {S}

Among them, F ^o = [F _n ^o , F _f ^o ], a ^o —— standard matrix of strain influence coefficient, S = [S _f , S _n ], S _f and S _n are respectively F _f ^o and F _n ^o The corresponding metric value.

The relative error calculation method is as follows:

Among them, F _f is the load during the test, and F _n is the collected strain.

S24, judging whether the number of tests is sufficient, if the number of tests is not enough, execute step S22, if the number of tests is sufficient, execute step S25;

S25. Calculate the transformation matrix.

The transformation matrix F ^o =[F _n ^o , F _f ^o ] is calculated according to the above description, and then used to preprocess the collected strains. In this embodiment, the strain influence coefficient is adjusted through the iteration of the relative error control and the test number control, and finally the collected data is preprocessed through the strain influence coefficient.

In this embodiment, through the strain calibration method, the fixed strain gauges are calibrated and measured, the strain transformation matrix is obtained, and the subsequent measured strains are preprocessed according to the transformation matrix, so as to reduce the manufacturing error of the gear teeth and the installation error of the strain gauge. The resulting strain change makes the collection of strain more accurate, and improves the accuracy of analysis and statistics such as subsequent power dynamic shunting.

The above description is only a detailed description of specific embodiments of the present invention, rather than limiting the present invention. Various replacements, modifications and improvements made by those skilled in the relevant technical fields without departing from the principle and scope of the present invention shall be included in the protection scope of the present invention.

Claims (4)

1. The method for testing the dynamic shunt in the planetary gear train is characterized by comprising the following steps of:

s1, respectively setting strain gauge measuring points on the tooth roots of a sun gear and a gear ring, and pasting strain gauges at the strain gauge measuring points; setting a rotating speed measuring point on the output shaft and the input shaft, and installing a speed measuring sensor at the rotating speed measuring point;

step S1, strain data of a solar strain gauge measuring point are collected based on a direct matching relation between a slip ring rotor and a slip ring stator; the slip ring rotor and the slip ring stator are directly matched as follows:

the transition flange is connected with the input end of the input flange, the output end of the input shaft connecting disc is connected with the sun gear input shaft, and the output end of the input shaft connecting disc is sleeved outside the sun gear input shaft; a slip ring rotor and a slip ring stator are sleeved outside the output end of the input shaft connecting disc in sequence; the slip ring rotor is in spline connection with the output end of the input shaft connecting disc; when the sun gear rotates, the slip ring stator is fixed; one end of a sensor signal wire is connected with the sun wheel strain gauge, and the other end of the sensor signal wire is connected with the slip ring rotor; the sensor signal wire is arranged in a wiring way through the axis of the input shaft connecting disc and the wire groove of the transition flange;

s2, performing a test, and recording an external basic source clock to obtain strain data and rotation speed data respectively acquired by a strain gauge measuring point and a rotation speed measuring point; the strain data and the rotating speed data acquired after synchronous triggering of the rotating speed detection of the output shaft and the input shaft speed measuring sensor are recorded as effective data, and a corresponding relation between the strain data and the planet wheel is established according to the effective data;

s2, preprocessing the acquired strain data according to a conversion matrix;

the calculation of the transformation matrix comprises the following steps:

s21, calibrating and measuring the strain gauge which is fixed, wherein a gear fixed with the strain gauge is set as a test gear, and a gear meshed with the test gear and used for loading load is set as a loading gear; when the gear is in a standard meshing position, the loading gear loads two different loads and then collects the strain of the strain gauge, and a strain measurement standard value is calculated according to the strain influence coefficient;

the method for calculating the strain measurement standard value in the step S21 is as follows:

S ₁ ＝a ₁₁ ^o F _n1 +a ₁₂ ^o F _f1

S ₂ ＝a ₂₁ ^o F _n2 +a ₂₂ ^o F _f2

wherein the load of the first test is F _f1 The corresponding acquired strain is F _n1 The method comprises the steps of carrying out a first treatment on the surface of the The load of the second test is F _f2 The corresponding acquired strain is F _n2 ；a ₁₁ ^o 、a ₁₂ ^o 、a ₂₁ ^o And a ₂₂ ^o Is the strain influence coefficient; s is S ₁ For the strain measurement standard value of the first test, S ₂ Strain gauge values for the second test;

s22, selecting meshing positions except tooth tops, loading different loads, and collecting the strain of a strain gauge;

s23, calculating a first load F according to the strain measurement standard value _f ^o And first strain F _n ^o The method comprises the steps of carrying out a first treatment on the surface of the Calculating relative error delta by combining strain acquired during test and load during test _f ，δ _n Judging that the relative error isIf the relative error does not meet the requirement, executing step S22; if the relative error meets the requirement, executing step S24;

f in step S23 _n ^o 、F _f ^o The relative error calculation method is as follows:

wherein the first load F is calculated by the following method _f ^o And first strain F _n ^o ；

{F ^o }＝{a ^o } ^-1 {S}

Wherein F is ^o ＝[F _n ^o ，F _f ^o ]，a ^o -strain influence coefficient standard matrix, s= [ S ] _f ,S _n ]，S _f And S is equal to _n Are respectively F _f ^o And F is equal to _n ^o Corresponding measurement standard values;

the relative error calculation method is as follows:

wherein F is _f F for load at test _n Is the acquired strain;

s24, judging whether the test times are sufficient or not, executing the step S22, and executing the step S25, wherein the test times are insufficient;

s25, calculating a conversion matrix;

s3, according to the corresponding relation between the planet gears and the strain data, the strain data collected by each strain measuring point are divided again to obtain strain data taking the planet gears as visual angles;

s4, calculating dynamic split of the load power of the planet wheel according to strain data taking the planet wheel as a visual angle;

in the step S4, the strain data of the planet gear with a view angle includes strain data of the planet gear relative to the sun gear and strain data of the planet gear relative to the gear ring;

the step S4 includes the steps of: based on the corresponding relation between the strain and the meshing force, the meshing force of the sun gear and the meshing force of the gear ring are obtained according to the strain data of the planet gear relative to the sun gear and the strain data of the planet gear relative to the gear ring; and calculating the planet carrier acting force corresponding to the planet wheel according to the meshing force of the sun wheel and the meshing force of the gear ring based on the stress analysis, and then calculating the dynamic split of the transfer power of the planet wheel according to the planet carrier acting force based on formula conversion.

2. The method for dynamic split-flow testing of the inside of the planetary gear train according to claim 1, wherein the number of the strain gauge measuring points in the step S1 is identical to the number of the planetary gears, and each group of strain gauge measuring points has two strain gauges.

3. The method for testing the dynamic shunting of the interior of the planetary gear train according to claim 1, wherein in the step S1, the speed measuring sensor is a speed measuring reflecting band and a speed measuring probe, the strain gauge comprises a sun gear strain gauge and a gear ring strain gauge, the speed measuring reflecting band comprises an output shaft speed measuring reflecting band and an input shaft speed measuring reflecting band, and the speed measuring probe comprises an output shaft speed measuring probe and an input shaft speed measuring probe; the speed measuring reflecting belt is parallel to the axis of the planet wheel, and the speed measuring probe and the gear ring strain gauge are directly connected with the planet carrier relative to the output shaft; the speed measuring reflective belt of the output shaft corresponds to a planet wheel on the planet carrier; the input shaft is directly connected with the sun gear, and the speed measuring reflective belt of the input shaft corresponds to a strain gauge of the sun gear.

4. The method for testing the internal dynamic shunting of the planetary gear train according to claim 1, wherein in the step S2, signals detected and obtained by the output shaft and input shaft speed measuring sensor are recorded as output shaft time domain laser pulse signals and input shaft time domain laser pulse signals, a laser pulse synchronous triggering method is adopted to enable the output shaft time domain laser pulse signals and the input shaft time domain laser pulse signals to be synchronously triggered, and a corresponding relation between strain data and the planetary gear train is established according to strain data and rotation speed data after synchronous triggering.

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