CN114370997B - Dynamic shunt testing method for interior of planetary gear train - Google Patents
Dynamic shunt testing method for interior of planetary gear train Download PDFInfo
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- CN114370997B CN114370997B CN202111671925.5A CN202111671925A CN114370997B CN 114370997 B CN114370997 B CN 114370997B CN 202111671925 A CN202111671925 A CN 202111671925A CN 114370997 B CN114370997 B CN 114370997B
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- 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
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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
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Abstract
The invention discloses a dynamic shunt test method for the interior of a planetary gear train. The internal dynamic shunt testing method of the planetary gear train comprises the following steps: s1, setting a strain gauge measuring point on the tooth root of a sun gear and a tooth ring and pasting a strain gauge at the strain gauge measuring point; setting a rotating speed measuring point, and installing a speed measuring reflective belt and a speed measuring probe at the rotating speed measuring point; 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; s3, synchronously triggering the output shaft time domain laser pulse and the input shaft time domain laser pulse, and establishing a corresponding relation between strain data and the planet wheel; s4, according to the corresponding relation between the planet gears and the strain data, the strain data taking the planet gears as the visual angles are divided again; and S5, calculating dynamic split of the load power of the planet wheel according to strain data taking the planet wheel as a visual angle.
Description
Technical Field
The invention relates to the field of mechanical transmission, in particular to a dynamic shunt testing method for the interior of a planetary gear train.
Background
Planetary gear trains are an important form in the field of mechanical transmission, and are widely used in the mechanical industry due to their high power, high efficiency and compact structure. The internal dynamic split of the planetary gear train refers to split of load power and transmission power of each planetary gear in the running process of the planetary gear train, and is specifically expressed as dynamic engagement strain of each planetary gear, a sun gear and a gear ring, and is an important factor influencing the service life of the planetary gear train. Through the means of testing, detect the inside dynamic reposition of redundant personnel in the planetary gear train motion process, can provide abundant data support for the design, maintenance, the maintenance of planetary gear train.
The conventional planetary gear train internal shunt test method does not consider the contingency and the error of the test, and has the following defects:
1) Because the testing process is complex and tedious, the mapping relation and loss of the sun gear meshing strain corresponding to the planet gear are easy, and the meshing strain does not have the specificity corresponding to the planet gear, so that the test has the accident.
2) Because the testing process is huge and needs multiple-aspect cooperation, strain data and rotation speed data cannot be corresponding easily, and certain system errors exist in data processing after the test.
Disclosure of Invention
The invention aims to overcome the defect that the accidental and error of the test is not considered in the internal shunt test in the prior art, and provides a dynamic shunt test method for the planetary gear train, wherein the test of a strain gauge and a rotating speed is synchronously triggered, so that data are synchronous.
In order to achieve the above object, the present invention provides the following technical solutions:
a dynamic shunt test method for the interior of a planetary gear train comprises the following steps:
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;
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;
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;
and S4, calculating dynamic split of the load power of the planet wheel according to strain data taking the planet wheel as a visual angle.
Preferably, in the step S1, the number of strain gauge measuring points is identical to the number of the planetary gears, and each group of strain gauge measuring points has two strain gauges.
Preferably, in the step S1, the tachometer sensor is a tachometer reflective tape and a tachometer probe, the strain gauge comprises a sun gear strain gauge and a gear ring strain gauge, the tachometer reflective tape comprises an output shaft tachometer reflective tape and an input shaft tachometer reflective tape, and the tachometer probe comprises an output shaft tachometer probe and an input shaft tachometer 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.
Preferably, in step S2, signals detected and acquired by the output shaft and input shaft tachometer 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 planet gears is established according to strain data and rotation speed data after synchronous triggering.
Preferably, in the step S4, the strain data of the planet gear with respect to the viewing angle includes strain data of the planet gear relative to the sun gear and strain data of the planet gear relative to the ring gear.
Preferably, the step S5 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.
Preferably, the step S1 is to collect strain data of a solar strain gauge measuring point based on a direct matching relationship 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.
Preferably, the strain data collected in step S2 is preprocessed according to a transformation 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;
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 whether the relative error meets the requirement or not, and executing step S22 if the relative error does not meet the requirement; if the relative error meets the requirement, executing step S24;
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.
Preferably, the method for calculating the strain gauge value in 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 The strain gauge for the second test.
Preferably, 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 n o And first strain F f 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 strain collected.
Compared with the prior art, the invention has the beneficial effects that: the method comprises the steps of establishing a mapping relation between meshing strain and a planet wheel by designing a corresponding relation between the arrangement of the strain gauge measuring points of a sun wheel and the arrangement of the strain gauge measuring points of a gear ring and the same planet wheel; by designing the relative relation of the strain gauge, the speed measuring reflective belt and the speed measuring probe, automatic synchronous triggering is realized, and conditions are created for synchronous correspondence of strain data and rotation speed data in the time domain.
Description of the drawings:
FIG. 1 is a flow chart of a dynamic split test method for the planetary gear train interior of exemplary embodiment 1 of the present invention;
FIG. 2 is a four planetary gear train strain gauge layout of an exemplary embodiment 1 of the present invention;
fig. 3 is a schematic diagram of a corresponding relationship between a strain measurement point and a rotation speed measurement point according to an exemplary embodiment 1 of the present invention;
FIG. 4 is a schematic diagram of a laser pulse synchronous triggering method according to an exemplary embodiment 1 of the present invention;
fig. 5 is a diagram illustrating strain data division using a planet as a perspective according to an exemplary embodiment 1 of the present invention;
FIG. 6 is a diagram illustrating a planetary gear force analysis according to an exemplary embodiment 1 of the present invention;
fig. 7 is a schematic view of a sun gear strain measurement installation of exemplary embodiment 1 of the present invention.
FIG. 8 is a schematic view of a standard engagement position of exemplary embodiment 1 of the present invention; namely, the tooth top meshing position corresponding to the tooth slot (2) is selected as a standard meshing position, and the strain of the strain gauge is acquired after the loading gear loads two different loads.
Reference numerals: the speed measuring device comprises a 1-planet wheel axial lead, a 2-input shaft speed measuring probe, a 3-input shaft speed measuring reflecting belt, a 4-sun gear strain gauge, a 5-output shaft speed measuring reflecting belt, a 6-output shaft speed measuring probe, a 7-gear ring strain gauge, an 8-sun gear, a 9-slip ring rotor, a 10-slip ring stator, an 11-input shaft connecting disc, a 12-sensor signal wire and a 13-transition flange.
Detailed Description
The present invention will be described in further detail with reference to test examples and specific embodiments. It should not be construed that the scope of the above subject matter of the present invention is limited to the following embodiments, and all techniques realized based on the present invention are within the scope of the present invention.
Example 1
As shown in fig. 1, the embodiment provides a method for testing dynamic shunt in a planetary gear train, which includes the following steps:
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;
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;
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;
and S4, calculating dynamic split of the load power of the planet wheel according to strain data taking the planet wheel as a visual angle.
According to the embodiment, through the relative relation between the strain gauge measuring point and the rotating speed measuring point and synchronous triggering, the obtained meshing strain of the sun gear, the meshing strain of the gear ring and the planet gear have a mapping relation, and synchronous correspondence of strain data and rotating speed data in a time domain is realized.
Illustratively, the number of strain gauge measuring points is identical to the number n of planet gears, and each group of measuring points has two strain gauges. Because the number of the strain gauge measuring points is consistent with the number n of the planetary gears, the mapping relation between meshing strain and the planetary gears can be established through the corresponding relation between the arrangement of the strain gauge measuring points of the sun gear and the arrangement of the strain gauge measuring points of the gear ring and the same planetary gears. As shown in fig. 2, step S1 is to paste strain gauges on the sun gear and the tooth root of the ring gear, and fig. 2 (a) is a layout of strain gauges of the sun gear and fig. 2 (b) is a layout of strain gauges of the ring gear. The embodiment designs the corresponding relation between the strain gauge measuring point arrangement of the sun gear and the same planet wheel as the strain gauge measuring point arrangement of the gear ring, and establishes the mapping relation between meshing strain and the planet wheel.
In step S1, the tachometer sensor is exemplified by a tachometer strip and a tachometer probe, and the tachometer strip, the tachometer strip and the tachometer probe are installed according to the corresponding relationship between the strain gauge measuring point and the tachometer measuring point as shown in fig. 3. The strain gauge comprises a sun gear strain gauge 4 and a gear ring strain gauge 7, the speed measuring and reflecting belt comprises an output shaft speed measuring and reflecting belt 5 and an input shaft speed measuring and reflecting belt 3, and the speed measuring probe comprises an output shaft speed measuring probe 6 and an input shaft speed measuring probe 2; the speed measuring reflecting belt is parallel to the axis 1 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 (marked as a planet wheel a) 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 sun gear strain gauge (marked as a sun gear strain gauge a). The speed measuring probe measures the rotating speed by capturing the returned signal after the emitted laser pulse signal encounters the speed measuring reflective belt, and the rotating speed data is obtained. According to the embodiment, the automatic synchronous triggering is realized by designing the relative relation among the strain gauge, the speed measuring reflecting belt and the speed measuring probe, and conditions are created for synchronous correspondence of strain data and rotation speed data in a time domain.
For example, as shown in fig. 4, signals detected and acquired by the output shaft and input shaft tachometer sensors 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 planet gears is established according to strain data and rotation speed data after synchronous triggering. In this embodiment, a ring gear strain gauge (denoted as a ring gear strain gauge a) is disposed directly above the ring gear, and when the output shaft time domain laser pulse and the input shaft time domain laser pulse are triggered synchronously (in the figure, the effective data start time), it represents that the planet wheel a and the sun gear strain gauge a are both directly above the planetary gear train, and by combining with the rotation direction of the planet carrier, the corresponding relationship between the planet wheel and the strain data, and between the strain data and the rotation speed data can be established. In this embodiment, the ring gear strain gauge a may be set at another position, and the synchronous triggering principle is consistent, when the strain signal detected by the ring gear strain gauge a is synchronous with the rising edge time of the output shaft time domain laser pulse signal and the rising edge time of the input shaft time domain laser pulse signal, synchronous triggering is achieved, at this time, the positions of the ring gear strain gauge a, the planet wheel a and the sun gear strain gauge a have a corresponding relationship, the data at the time after synchronization is effective data, and the corresponding relationship between the strain data and the planet wheel can be established according to the effective data.
Exemplary, as shown in fig. 5, strain data collected at each strain measurement point is divided again according to the corresponding relationship between the planet and the strain data, so as to obtain strain data with the planet as a viewing angle. If the strain gauge is arranged on the planet gear, the movement of the planet gear easily causes the winding of the acquisition data wire, so the strain gauge is arranged on the tooth root of the sun gear and the tooth ring. Because the rotation and revolution of the planet carrier and the planet wheel exist, at the same moment, data can not exist in all the strain gauges, and the data collected by all the strain gauges are not all data of the same planet wheel, strain data collected by the strain gauges need to be divided again, and strain data of the planet wheel as a visual angle is obtained. In this embodiment, taking a four-planetary gear train as an example, because the number of strain gauge measuring points respectively arranged on the tooth root of the sun gear and the tooth root of the gear is identical to the number of the planetary gears, strain data taking the planetary gears as view angles can be rapidly and conveniently repartitioned in a mode shown in fig. 5.
Step S4 is implemented by taking the planet as strain data of the view angle to dynamically split the load power of the planet; the strain data taking the planet wheel as the view angle comprises strain data of the planet wheel relative to the sun wheel and strain data of the planet wheel relative to the gear ring; 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; as shown in fig. 6, based on the force analysis, the carrier acting force corresponding to the planet wheel is calculated according to the meshing force of the sun wheel and the meshing force of the ring gear, and then the dynamic split of the transmission power of the planet wheel is calculated according to the carrier acting force based on formula conversion.
Exemplary, as shown in fig. 7, strain data of the sun gear is collected based on the direct matching relationship of the slip ring rotor and the slip ring stator;
the transition flange 13 is connected with the input end of the input flange 11, the output end of the input shaft connecting disc 11 is connected with the input shaft of the sun gear 8, and the output end of the input shaft connecting disc 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 connecting disc 11 in sequence; the slip ring rotor 9 is in spline connection with the output end of the input shaft connecting disc 11; when the sun gear rotates, the slip ring stator 10 is fixed; one end of a sensor signal wire 12 is connected with the sun gear strain gauge, and the other end of the sensor signal wire 12 is connected with the slip ring rotor 9; the sensor signal wire 12 is arranged in a wiring way through the axle center of the input shaft connecting disc 11 and the wire groove of the transition flange 13.
Because the strain gauge measuring point of the sun gear moves along with the meshing process, the winding of the collected data wire is easy to cause, and therefore, the tooth root meshing strain of the strain gauge measuring point on the movable sun gear is measured through the direct matching relation of the slip ring rotor and the slip ring stator; the whole sensor signal wire moves along with the sun gear, and strain data reading is realized through the slip ring stator, namely the sensor signal wire and the sun gear are kept static, and a data acquisition receiving end of the sensor is also kept static; therefore, the problem of winding of the sensor signal wire when the sun gear moves along with the meshing process is solved.
The inner diameter of the slip ring rotor 9 is designed according to the outer diameter of the output end of the input shaft connecting disc 11; the outer diameter of the slip ring rotor 9 is designed in combination with the installation and positioning relation; the length of the slip ring rotor 9 is designed by combining the length of the input shaft connecting disc 11 and the positioning relation, and the spline of the slip ring rotor 9 and the output end of the input shaft connecting disc 11 is designed by utilizing the spline national standard design flow by combining the length of the slip ring rotor 9 and the inner diameter and the outer diameter. The outer diameter of the slip ring rotor 9 and the inner diameter of the outer ring of the planetary gear train are used for selecting the inner diameter and the outer diameter of the slip ring stator 10, the length of the slip ring stator 10 is designed in combination with the installation positioning relation, and the surface roughness of the inner ring of the stator is selected in combination with the requirement of signal connection.
The strain data collected in step S2 is preprocessed according to a transformation 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;
as shown in fig. 8, the tooth top meshing position corresponding to the tooth slot (2) is selected as a standard meshing position, and the loading gear loads two different loads and then acquires the strain of the strain gauge.
The strain measurement standard value calculation method 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 S is the strain influence coefficient 1 For the strain measurement standard value of the first test, S 2 For the second testAnd (5) changing a standard value.
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 whether the relative error meets the requirement or not, and executing step S22 if the relative error does not meet the requirement; if the relative error meets the requirement, executing step S24;
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 strain collected.
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.
Calculating the transformation matrix F according to the above description o ＝[F n o ，F f o ]And then used to pre-process the acquired strain. In this embodiment, the strain influence coefficient is adjusted through iteration of relative error control and test frequency control, and finally the acquired number is obtained through the strain influence coefficientAnd (5) performing pretreatment.
According to the embodiment, through a strain calibration method, calibration measurement is conducted on the fixed strain gauge, a strain conversion matrix is obtained, and the strain measured subsequently is preprocessed according to the conversion matrix, so that strain changes of the gear caused by gear tooth manufacturing errors and strain gauge mounting errors are reduced, the strain is acquired more accurately, and the accuracy of analysis statistics of subsequent power dynamic shunt and the like is improved.
The foregoing is a detailed description of specific embodiments of the invention and is not intended to be limiting of the invention. Various alternatives, modifications and improvements will readily occur to those skilled in the relevant art without departing from the spirit and scope of the 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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