Phenomenological Modeling Method for the Vibration of a Normal Single-Stage Epicyclic Gear Train Considering Gear Meshing Impact

Abstract

The present invention provides a phenomenological vibration modeling method for a normal single-stage epicyclic gear train considering gear meshing impact, including: 1) calculating the impact forces generated by internal and external meshing within the epicyclic gear train, namely the meshing impact force generated by the meshing of the planet gear and the internal gear ring, and the meshing impact force generated by the meshing of the planet gear and the sun gear; 2) calculating the theoretical meshing forces of internal and external meshing within the epicyclic gear train, namely the theoretical meshing force of the meshing of the planet gear and the internal gear ring, and the theoretical meshing force of the meshing of the planet gear and the sun gear; 3) obtaining the corresponding impact coefficients according to the calculation results of 1) and 2); 4) considering the meshing impact characteristics of the gears and combining them with the impact coefficients in 3) to establish a phenomenological vibration model for a normal single-stage epicyclic gear train considering gear meshing impact and giving an expression for the vibration response. The present invention uses an impact function to simulate the meshing impact caused by gear engagement, breaking through the defect that the cosine function cannot simulate the meshing impact when phenomenologically modeling vibration signals in the past.

Description

Technical Field

[0001] The present invention belongs to the technical field of early fault diagnosis of mechanical equipment, and particularly relates to a vibration phenomenological modeling method for a normal single-stage epicyclic gear train considering gear meshing impact. Background Technique

[0002] An epicyclic gear train usually consists of multiple components such as a sun gear, planet gears, and an internal gear ring. Compared with a fixed-axis gear train, the epicyclic gear train has the advantages of compact structure and high transmission efficiency, and is therefore widely used in mechanical equipment in many fields such as aviation, metallurgy, chemical industry, and wind power. Usually, there are multiple planet gears inside the epicyclic gear train. During the operation of the epicyclic gear train, each planet gear needs to mesh with the sun gear and the internal gear ring simultaneously. Therefore, there are multiple external meshes (sun gear - planet gear) and internal meshes (planet gear - internal gear ring) inside the epicyclic gear train, resulting in more meshing vibration components. In addition, there is a phase difference between multiple meshing components, making the vibration components of the epicyclic gear train very complex and not conducive to the smooth implementation of fault diagnosis of the epicyclic gear train.

[0003] Vibration signal spectrum analysis is one of the most commonly used methods in the fault diagnosis of epicyclic gear trains. By performing phenomenological modeling on the vibration signals of the epicyclic gear train, the model response results obtained from the established model can provide theoretical support for spectrum analysis. Ideally, the gears are evenly stressed, and the system smoothly transmits force and torque. As the gears continuously enter and disengage, the gear transmission system will excite harmonic vibrations with the meshing frequency as the fundamental frequency. However, in actual situations, due to inevitable factors such as manufacturing errors, installation errors, and tooth load deformation in the system, the teeth deviate from the theoretical meshing position, and at the same time, the gear speed may fluctuate accordingly, resulting in meshing impact. All these factors cause the existing vibration phenomenological models of epicyclic gear trains to not accurately reflect the dynamic characteristics of the system, thereby making the fault diagnosis of epicyclic gear trains more difficult. Summary of the Invention

[0004] In order to overcome the above-mentioned shortcomings of the existing technology, the purpose of the present invention is to establish a vibration phenomenological modeling method for a normal single-stage epicyclic gear train considering gear meshing impact. This method uses an impact function to simulate the meshing impact caused when the gear enters meshing, breaking through the defect that the existing method using a cosine function to perform phenomenological modeling on vibration signals cannot simulate the meshing impact. By superimposing multiple impact vibration signals inside the epicyclic gear train, a vibration phenomenological model of the normal single-stage epicyclic gear train is established. This method can fully display the impact vibration characteristics of the gear when entering meshing. According to this phenomenological modeling method, the vibration response signal of the normal single-stage epicyclic gear train is obtained, providing a theoretical basis for realizing the fault diagnosis of the epicyclic gear train.

[0005] In order to achieve the above purpose, the technical solution adopted by the present invention is as follows:

[0006] The first aspect of the present invention provides a phenomenological vibration modeling method for a normal single-stage epicyclic gear train considering gear meshing impact, including the following steps:

[0007] Step 1) Calculate the impact forces generated by internal and external meshes within the epicyclic gear train, namely the meshing impact force generated by the meshing of the planet gear and the internal gear ring, and the meshing impact force generated by the meshing of the planet gear and the sun gear;

[0008] Step 2) Calculate the theoretical meshing forces of internal and external meshes within the epicyclic gear train, namely the theoretical meshing force of the meshing of the planet gear and the internal gear ring, and the theoretical meshing force of the meshing of the planet gear and the sun gear;

[0009] Step 3) Obtain the corresponding impact coefficients according to the calculation results of Steps 1) and 2);

[0010] Step 4) Consider the meshing impact characteristics of the gears and combine them with the impact coefficients in Step 3) to establish a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact, and give the vibration response expression.

[0011] The second aspect of the present invention provides a phenomenological vibration modeling device for a normal single-stage epicyclic gear train considering gear meshing impact, including:

[0012] A first calculation module configured to calculate the impact forces generated by internal and external meshes within the epicyclic gear train, namely the meshing impact force generated by the meshing of the planet gear and the internal gear ring, and the meshing impact force generated by the meshing of the planet gear and the sun gear;

[0013] A second calculation module configured to calculate the theoretical meshing forces of internal and external meshes within the epicyclic gear train, namely the theoretical meshing force of the meshing of the planet gear and the internal gear ring, and the theoretical meshing force of the meshing of the planet gear and the sun gear;

[0014] A third calculation module configured to calculate the corresponding impact coefficients according to the impact forces generated by internal and external meshes within the epicyclic gear train and the theoretical meshing forces of internal and external meshes within the epicyclic gear train;

[0015] A fourth calculation module configured to establish a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact according to the meshing impact characteristics of the gears and the impact coefficients, and give the vibration response expression.

[0016] The third aspect of the present invention provides a phenomenological vibration modeling device for a normal single-stage epicyclic gear train considering gear meshing impact, including:

[0017] A memory; and

[0018] A processor coupled to the memory, the processor being configured to execute the above-mentioned phenomenological vibration modeling method for a normal single-stage epicyclic gear train considering gear meshing impact based on instructions stored in the memory.

[0019] In a fourth aspect of the present invention, a non-transitory computer-readable storage medium is provided, on which a computer program is stored. When the program is executed by a processor, the described phenomenological vibration modeling method of a normal single-stage epicyclic gear train considering gear meshing impact is implemented.

[0020] The core of the present invention is to establish a phenomenological vibration modeling method of a normal single-stage epicyclic gear train considering gear meshing impact, and to give the vibration response expression of the model. Starting from the gear meshing transmission mechanism, this method considers the meshing impact characteristics between pairs of gears inside the epicyclic gear train, calculates the impact force magnitudes when the internal and external gears enter meshing respectively, and obtains the vibration signal impact coefficients considering the influence of meshing impact for the internal and external meshes. Then, considering the vibration transmission path and the influence of the phase difference between the internal and external meshes, a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact is established. The advantage of this model is that it considers the influence of gear meshing impact and is modeled according to the vibration impact characteristics, and can fully reflect the vibration characteristics of the epicyclic gear train. According to this phenomenological model, the vibration response signal of a normal single-stage epicyclic gear train is obtained. BRIEF DESCRIPTION OF THE DRAWINGS

[0021] Figure 1 is a flowchart of the present invention.

[0022] Figure 2 is a schematic diagram of external meshing impact during engagement.

[0023] Figure 3 is a schematic diagram of internal meshing impact during engagement.

[0024] Figure 4 is the simulation signal waveform and order spectrum diagram of a normal single-stage epicyclic gear train.

[0025] Figure 5 is Figure 4 a partial enlarged view of the time-domain waveform of the simulation signal of a normal single-stage epicyclic gear train.

[0026] Figure 6 is the experimental signal waveform and order spectrum diagram of a normal single-stage epicyclic gear train. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0027] The present invention will be further described in detail below with reference to the drawings and embodiments.

[0028] Embodiment 1

[0029] In the epicyclic gear train of the test bench in this embodiment, the internal gear ring is fixed, the sun gear is the input end, and the planet carrier is the output end. The specific parameters are shown in Table 1.

[0030] Table 1 Epicyclic gear train parameters

[0031]

[0032] Refer to Figure 1 , a phenomenological vibration modeling method for a normal single-stage epicyclic gear train considering gear meshing impact, comprising the following steps:

[0033] 1) Calculate the impact forces generated by internal and external meshes within the epicyclic gear train, that is, the meshing impact force generated by the planet gear meshing with the internal gear ring, and the meshing impact force generated by the planet gear meshing with the sun gear;

[0034] The process of calculating the meshing impact force is as follows:

[0035] 1.1) Calculate the impact force F during external meshing (planet gear meshing with sun gear) s_spi ,

[0036] As Figure 2 shown, calculate the geometric position of the meshing point A of the sun gear and the planet gear according to the geometric relationships in the figure;

[0037]

[0038] Among them, is the distance from the center of the sun gear to the meshing point A, r ag is the addendum circle radius of the planet gear, r p and r g are the pitch circle radii of the sun gear and the planet gear respectively, η g is the angle between and the center line;

[0039] According to the obtained geometric position of point A, calculate the relative velocity difference Δv between the two gears n_sp ;

[0040] Δv n_sp = v Ap cosβ p - v Ag cosβ g

[0041]

[0042] v Ag = r ag ·ω g

[0043] Among them, v Ap is the instantaneous velocity of the sun gear, v Ag is the instantaneous velocity of the planet gear, β p is the angle between v Ap and N p ’N g ’s, β g is the angle between v Ag and Np ’N g The included angle between ω p and ω g are the angular velocities of the sun gear and the planet gear respectively, and r ag is the addendum circle radius of the planet gear;

[0044] Calculate the meshing impact force F according to the meshing impact point and the relative velocity difference s_spi ;

[0045]

[0046] where E k_sp is the impact kinetic energy during the meshing of the planet gear and the sun gear; m e_sp is the comprehensive induced mass per unit tooth width on the instantaneous meshing line of the two gears; J p and J g are the moments of inertia of the sun gear and the planet gear respectively; b is the tooth width; r bp is the instantaneous base circle radius of the sun gear; r bg ’ is the instantaneous base circle radius of the planet gear; Δv n_sp is the relative velocity difference between the planet gear and the sun gear; k _sp is the meshing stiffness between the planet gear and the sun gear;

[0047] 1.2) Calculate the meshing impact force F generated by the internal meshing (meshing of the planet gear and the internal gear ring) s_rpi ;

[0048] As Figure 3 shown, calculate the geometric position of the meshing point B of the internal gear ring and the planet gear according to the geometric relationship in the figure;

[0049]

[0050] where is the distance from the center of the planet gear to the meshing point B, r ar is the addendum circle radius of the internal gear ring, r g and r r are the pitch circle radii of the planet gear and the internal gear ring respectively, and η r is the included angle between the center line;

[0051] Calculate the relative velocity difference Δv between the two gears according to the geometric position of point B n_rp ;

[0052] Δv n_rp = v Ag cosβ g - v Ar cosβ r

[0053]

[0054] v Ar = r ar ·ω r

[0055] where v Ag is the instantaneous velocity of the planet gear, v Ar is the instantaneous velocity of the internal gear ring, β g is the angle between v Ag and N r ’N g ’, β r is the angle between v Ar and N r ’N g ’, ω g , ω r are the angular velocities of the planet gear and the internal gear ring respectively, r ar is the addendum circle radius of the internal gear ring;

[0056] Calculate the meshing impact force F s_rpi ;

[0057]

[0058] where E k_rp is the impact kinetic energy during the meshing of the planet gear and the internal gear ring, m e_rp is the comprehensive induced mass per unit tooth width of the two gears on the instantaneous meshing line, J g , J r are the moments of inertia of the planet gear and the internal gear ring respectively, b is the tooth width, r bg is the instantaneous base circle radius of the planet gear, r br ’ is the instantaneous base circle radius of the internal gear ring, Δv n_rp is the relative velocity difference between the planet gear and the internal gear ring, k _rp is the meshing stiffness between the planet gear and the internal gear ring.

[0059] 2) Calculate the theoretical meshing forces of the internal and external meshes within the epicyclic gear train, that is, the theoretical meshing force of the meshing between the planet gear and the internal gear ring, and the theoretical meshing force of the meshing between the planet gear and the sun gear;

[0060] The process of calculating the theoretical meshing force is as follows:

[0061] 2.1) Calculate the theoretical meshing force F spi ;

[0062]

[0063] where T is the torque during gear transmission, dp is the pitch circle diameter of the sun gear;

[0064] 2.2) Calculate the theoretical meshing force F of the internal meshing (ring gear and planet gear meshing) rpi ,

[0065]

[0066] where T is the torque during gear rotation; d g is the pitch circle diameter of the planet gear.

[0067] 3) Combine the results obtained in steps 1) and 2) to determine the impact coefficients V spi and V rpi ,

[0068] 3.1) Determine the impact coefficient V of the external meshing spi ;

[0069]

[0070] 3.2) Determine the impact coefficient V of the internal meshing rpi ;

[0071]

[0072] 4) Fully consider the impact and vibration characteristics of the gears, establish the impact and vibration signals when a single planet gear meshes with the sun gear and the ring gear respectively, and then superimpose these signals to obtain a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact.

[0073] 4.1) Considering the impact characteristics of the gears and combining with the impact coefficients, establish the impact and vibration signals v spi (t) when a single planet gear meshes with the sun gear and v rpi (t) when it meshes with the ring gear. The specific process is as follows:

[0074]

[0075] where V spi , V rpi are the impact coefficients of the external meshing and internal meshing respectively, C r is the attenuation coefficient of the impact vibration, mod() is the remainder function, ψ i is the installation angle of the i-th planet gear, ω s , ω c are the rotational frequencies of the sun gear and the planet carrier respectively, γ i is the phase difference between the external and internal meshing; T m is the meshing period;

[0076] 4.2) Considering the impact characteristics of the gears, a phenomenological vibration model of a normal single-stage epicyclic gear train is established. The specific process is as follows:

[0077] For the impact vibration signals v spi (t) and v rpi (t) when the above single planet gear meshes with the sun gear and the internal gear ring respectively, after adding the transfer path function and superimposing them, the vibration response expression v(t) of the phenomenological vibration model of the normal single-stage epicyclic gear train is obtained;

[0078]

[0079] In the formula, N is the number of planet gears; A si (t) is the transfer path function of the vibration when the i-th planet gear meshes with the sun gear; A ri (t) is the transfer path function of the vibration when the i-th planet gear meshes with the internal gear ring.

[0080] As Figure 4 shown, according to the proposed phenomenological modeling method of the normal single-stage epicyclic gear train considering the meshing impact, the simulation signal waveform and the corresponding order spectrum are obtained. The data length of the time-domain waveform is the revolution period T of the planet gear, and the 100th order in the order spectrum corresponds to the meshing frequency of the epicyclic gear train. Different from the traditional phenomenological vibration model of the normal single-stage epicyclic gear train constructed based on the cosine function, the response of the phenomenological vibration model of the normal single-stage epicyclic gear train considering the gear meshing impact is composed of the superposition of multiple impact signals. Figure 5 Figure is a partial enlarged view of the time-domain waveform within one revolution period. It can be clearly seen from the figure that there are multiple impact components. Therefore, this model can fully exhibit the impact vibration characteristics of the gears during the meshing process. In addition, asymmetric sidebands appear near the meshing frequency in the order spectrum, and they only appear at integer multiples of the number of planet gears, such as the 96th, 99th, 102nd orders, etc. This is caused by the time-varying transfer path effect and the phase difference between the internal and external meshes. To sum up, the established model can fully reflect the impact vibration characteristics of the gears during the meshing process, and the sidebands in the order spectrum show corresponding characteristics, verifying the correctness of the established model.

[0081] After establishing the phenomenological vibration model of the normal single-stage epicyclic gear train considering the gear meshing impact, the method is experimentally verified and the results are analyzed. In the experiment, the rotation frequency of the sun gear is 40Hz, the sampling frequency is 5120Hz, and the corresponding revolution period of the planet carrier is 0.15s. The time-domain waveform and the order spectrum obtained from the experiment are as Figure 6As shown, the time-domain waveform is a revolution period of this epicyclic gear train. Obvious impact components can be seen in the figure, which are consistent with the established phenomenological model. In the order spectrum diagram, the sideband amplitudes at orders such as 95.8, 98.8, and 101.8 are relatively large, verifying the correctness of the established model. Due to factors such as gear installation and manufacturing errors, some sidebands also appear at orders such as 97.8, 99.8, and 102.8. In addition, due to the fluctuation of the gearbox speed during the experiment, there are slight differences between the orders on the measured signal order spectrum and the theory. In summary, through the analysis of this experimental signal, the correctness of the established model is verified.

[0082] This phenomenological modeling method can comprehensively consider the impact characteristics between gear meshes in the epicyclic gear train, the phase relationship between internal and external meshes, and factors such as the time-varying transmission path caused by the revolution of the planet gears. The advantage of this model is that, different from the traditional phenomenological model based on the cosine function as the model construction basis, it considers the meshing impact force when the gears enter meshing, and uses the impact function to clearly simulate the meshing impact characteristics between tooth pairs; in addition, it comprehensively considers the phase relationship between internal and external meshes within the epicyclic gear train and the influence of the time-varying transmission path, and can provide an effective theoretical basis for the fault diagnosis of the epicyclic gear train.

[0083] Example 2

[0084] This example provides a phenomenological modeling device for the vibration of a normal single-stage epicyclic gear train considering gear meshing impact, including:

[0085] The first calculation module is configured to calculate the impact forces generated by internal and external meshes within the epicyclic gear train, that is, the meshing impact force generated by the planet gear meshing with the internal gear ring, and the meshing impact force generated by the planet gear meshing with the sun gear;

[0086] The second calculation module is configured to calculate the theoretical meshing forces of internal and external meshes within the epicyclic gear train, that is, the theoretical meshing force of the planet gear meshing with the internal gear ring, and the theoretical meshing force of the planet gear meshing with the sun gear;

[0087] The third calculation module is configured to calculate the corresponding impact coefficients according to the impact forces generated by internal and external meshes within the epicyclic gear train and the theoretical meshing forces of internal and external meshes within the epicyclic gear train;

[0088] The fourth calculation module is configured to establish a phenomenological model for the vibration of a normal single-stage epicyclic gear train considering gear meshing impact according to the meshing impact characteristics of the gears and the impact coefficients, and give the vibration response expression.

[0089] Example 3

[0090] This embodiment provides another phenomenological vibration modeling device for a normal single-stage epicyclic gear train considering gear meshing impact, including: a memory and a processor coupled to the memory. The processor is configured to execute the phenomenological vibration modeling method for a normal single-stage epicyclic gear train in any of the embodiments of the present disclosure based on instructions stored in the memory.

[0091] Among them, the memory can include, for example, a system memory, a fixed non-volatile storage medium, etc. The system memory stores, for example, an operating system, application programs, a boot loader, and other programs.

[0092] The modeling device can also include an input / output interface, a network interface, a storage interface, etc. These interfaces and the memory and the processor can be connected through a bus, for example. Among them, the input / output interface provides a connection interface for input / output devices such as a display, a mouse, a keyboard, and a touch screen. The network interface provides a connection interface for various networking devices. The storage interface provides a connection interface for external storage devices such as an SD card and a USB flash drive.

[0093] Those skilled in the art should understand that the embodiments of the present disclosure can be provided as a method, a system, or a computer program product. Therefore, the present disclosure can take the form of a complete hardware embodiment, a complete software embodiment, or an embodiment combining software and hardware aspects. Moreover, the present disclosure can take the form of a computer program product implemented on one or more computer non-transitory readable storage media (including but not limited to disk memory, CD-ROM, optical memory, etc.) containing computer program code.

[0094] The present disclosure is described with reference to the flowcharts and / or block diagrams of methods, apparatuses (systems), and computer program products according to the embodiments of the present disclosure. It should be understood that each flow and / or block in the flowchart and / or block diagram, and the combination of flows and / or blocks in the flowchart and / or block diagram, can be implemented by computer program instructions. These computer program instructions can be provided to the processor of a general-purpose computer, a special-purpose computer, an embedded processor, or other programmable data processing devices to generate a machine, such that the instructions executed by the processor of the computer or other programmable data processing devices generate means for implementing the functions specified in Figure 1 one or more flows and / or blocks Figure 1 one or more blocks.

[0095] These computer program instructions can also be stored in a computer-readable memory that can direct a computer or other programmable data processing device to work in a specific manner, such that the instructions stored in the computer-readable memory generate a manufactured article including instruction means, and the instruction means implements the functions specified in Figure 1 one or more flows and / or blocks Figure 1The functions specified in one or more boxes.

[0096] These computer program instructions can also be loaded onto a computer or other programmable data processing device, so that a series of operation steps are executed on the computer or other programmable device to generate a computer-implemented process. Thus, the instructions executed on the computer or other programmable device provide for implementing the steps of the functions specified in Figure 1 one process or more processes and / or boxes Figure 1 the functions specified in one box or more boxes.

[0097] The above content is a further detailed description of the present invention in combination with specific embodiments. It cannot be determined that the specific embodiments of the present invention are limited thereto. For those of ordinary skill in the technical field to which the present invention pertains, without departing from the concept of the present invention, several simple deductions or substitutions can still be made, and all should be regarded as belonging to the scope of patent protection determined by the claims submitted for the present invention.

Claims

1. A phenomenological vibration modeling method for a normal single-stage epicyclic gear train considering gear meshing impact, characterized in that, Including the following steps: Step 1) Calculate the impact forces generated by the internal external and internal meshes in the epicyclic gear train, i.e., the impact force during meshing of the planet gear with the internal gear ring, and the impact force during meshing of the planet gear with the sun gear; The calculation process of Step 1) is: Calculate the meshing impact force F generated by the meshing of the planet gear and the sun gear s_spi ; Among them, Δv n_sp represents the relative speed difference between the planet gear and the sun gear; b represents the tooth width; J p and J g are the moments of inertia of the sun gear and the planet gear respectively; r bg ’ is the instantaneous base circle radius of the planet gear; r bp is the base circle radius of the sun gear; k _sp is the meshing stiffness between the planet gear and the sun gear; Calculate the meshing impact force F generated by the engagement of the planet gear and the internal gear ring s_rpi , Among them, Δv n_rp represents the relative speed difference between the planet gear and the internal gear ring; b represents the tooth width; J g and J r are the moments of inertia of the planet gear and the internal gear ring respectively; r br ’ is the instantaneous base circle radius of the internal gear ring; r bg is the base circle radius of the planet gear; k _rp is the meshing stiffness between the planet gear and the internal gear ring; Step 2) Calculate the theoretical meshing forces of the internal external and internal meshes in the epicyclic gear train, i.e., the theoretical meshing force of the planet gear with the internal gear ring, and the theoretical meshing force of the planet gear with the sun gear; The calculation process of the said Step 2) is: According to the calculation formula of gear meshing force, the theoretical meshing force F when the planet gear meshes with the sun gear is obtained spi ; Among them, T is the torque when the gear rotates; d p is the pitch diameter of the sun gear, According to the calculation formula of gear meshing force, the theoretical meshing force F when the planet gear meshes with the internal gear ring is obtained rpi ; Among them, T is the torque when the gear rotates; d g is the pitch diameter of the planetary gear; Step 3) Obtain the corresponding impact coefficients according to the calculation results of Steps 1) and 2); The calculation process of Step 3) is: Calculate the impact coefficient V of external meshing spi ; Calculate the impact coefficient V of internal meshing rpi ; Step 4) Consider the meshing impact characteristics of the gears and combine them with the impact coefficients in Step 3) to establish a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact, and give the vibration response expression; The specific process of Step 4) is: Calculate the impact vibration signal v spi (t) when a single planet gear meshes with the sun gear, and the impact vibration signal v rpi (t) when a single planet gear meshes with the internal gear ring; Among them, C r is the attenuation coefficient of shock vibration; mod() is the remainder function; ψ i is the installation angle of the i-th planet gear; ω s and ω c are the rotational frequencies of the sun gear and the planet carrier respectively; γ i is the phase difference between internal and external meshes; T m is the meshing period; The impact vibration signal v spi (t) when a single planet gear meshes with the sun gear and the impact vibration signal v rpi (t) when a single planet gear meshes with the internal gear ring are superimposed after the action of the transfer path function to obtain the vibration response expression v(t) of the vibration phenomenological model of a normal single-stage epicyclic gear train; Where N is the number of planet gears; A si A(t) is the transmission path function of the meshing vibration between the ith planet gear and the sun gear; A ri A(t) is the transmission path function of the meshing vibration between the ith planet gear and the internal gear ring.

2. A vibration phenomenological modeling device for a normal single-stage epicyclic gear train considering gear meshing impact, characterized in that, Including: A first calculation module configured to calculate the impact forces generated by the internal external and internal meshes in the epicyclic gear train, i.e., the impact force during meshing of the planet gear with the internal gear ring, and the impact force during meshing of the planet gear with the sun gear; The calculation process of the first calculation module is: Calculate the meshing impact force F generated by the meshing of the planet gear and the sun gear s_spi ; Among them, Δv n_sp represents the relative speed difference between the planet gear and the sun gear; b represents the tooth width; J p and J g are the moments of inertia of the sun gear and the planet gear respectively; r bg ’ is the instantaneous base circle radius of the planet gear; r bp is the base circle radius of the sun gear; k _sp is the meshing stiffness between the planet gear and the sun gear; Calculate the meshing impact force F generated by the engagement of the planetary gear and the internal gear ring s_rpi , Among them, Δv n_rp represents the relative speed difference between the planet gear and the internal gear ring; b represents the tooth width; J g and J r are the moments of inertia of the planet gear and the internal gear ring respectively; r br ’ is the instantaneous base circle radius of the internal gear ring; r bg is the base circle radius of the planet gear; k _rp is the meshing stiffness between the planet gear and the internal gear ring; A second calculation module configured to calculate the theoretical meshing forces of the internal external and internal meshes in the epicyclic gear train, i.e., the theoretical meshing force of the planet gear with the internal gear ring, and the theoretical meshing force of the planet gear with the sun gear; The calculation process of the second calculation module is: According to the gear meshing force calculation formula, the theoretical meshing force F when the planet gear meshes with the sun gear is obtained spi ; Among them, T is the torque when the gear rotates; d p is the pitch diameter of the sun gear, According to the calculation formula of gear meshing force, the theoretical meshing force F when the planet gear meshes with the internal gear ring is obtained rpi ; Among them, T is the torque when the gear rotates; d g is the pitch diameter of the planet gear; A third calculation module configured to calculate the corresponding impact coefficients according to the impact forces generated by the internal external and internal meshes in the epicyclic gear train and the theoretical meshing forces of the internal external and internal meshes in the epicyclic gear train; The calculation process of the third calculation module is: Calculate the impact coefficient V of external meshing spi ; Calculate the impact coefficient V of internal meshing rpi ; A fourth calculation module configured to establish a phenomenological vibration model of a normal single-stage epicyclic gear train considering gear meshing impact according to the meshing impact characteristics of the gears and the impact coefficients, and give the vibration response expression; The specific process of the fourth calculation module is: Calculate the impact vibration signal v spi (t) when a single planetary gear meshes with the sun gear, and the impact vibration signal v rpi (t) when a single planetary gear meshes with the internal gear ring; Among them, C r is the attenuation coefficient of shock vibration; mod() is the remainder function; ψ i is the installation angle of the i-th planet gear; ω s and ω c are the rotational frequencies of the sun gear and the planet carrier respectively; γ i is the phase difference between internal and external meshes; T m is the meshing period; The impact vibration signal v spi (t) when a single planet gear meshes with the sun gear and the impact vibration signal v rpi (t) when a single planet gear meshes with the internal gear ring are superimposed after the action of the transfer path function to obtain the vibration response expression v(t) of the vibration phenomenological model of a normal single-stage epicyclic gear train; Where N is the number of planet gears; A si (t) is the transmission path function of the meshing vibration between the i-th planet gear and the sun gear; A ri (t) is the transmission path function of the meshing vibration between the i-th planet gear and the internal gear ring.

3. A vibration phenomenological modeling device for a normal single-stage epicyclic gear train considering gear meshing impact, characterized in that, Including: A memory; And A processor coupled to the memory, the processor being configured to execute the phenomenological vibration modeling method of a normal single-stage epicyclic gear train considering gear meshing impact as described in claim 1 based on instructions stored in the memory.

4. A non-transitory computer-readable storage medium having stored thereon a computer program, which when executed by a processor implements the phenomenological vibration modeling method of a normal single-stage epicyclic gear train considering gear meshing impact as described in claim 1.

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