66 results about "Meshing stiffness" patented technology

The invention provides a gear peeling time-varying meshing stiffness prediction method and system based on a back propagation neural network, and the method comprises the steps: considering a tooth surface peeling fault based on a gear tooth bearing contact analysis method, and constructing a helical gear pair time-varying meshing stiffness calculation model; a real irregular tooth surface peeling area is fitted by adopting a least square ellipse fitting method to obtain an ellipse appearance representation, any peeling position is completely described through six key geometric parameters, the geometric parameters of the ellipse appearance are systematically traversed and fitted, and diversified peeling appearance samples are generated. Introducing a tooth profile deviation matrix corresponding to the peeling morphology sample into a tooth surface bearing contact analysis model, and constructing a training data set; and constructing a back propagation neural network model of multiple hidden layers, and performing end-to-end training by using the training data set, so that the back propagation neural network model learns a nonlinear mapping relationship from geometric parameters to a time-varying meshing stiffness curve, thereby predicting the time-varying meshing stiffness under any peeling morphology.

The application discloses a gear time-varying meshing stiffness measurement method, which comprises the following steps: S1, a measurement model between current and time-varying meshing stiffness is established based on Hertz contact theory and Ishikawa formula; S2, a closed circuit is formed by connecting a driving gear, a driven gear and a power supply in series, and time-varying current of the circuit is measured; and S3, the time-varying current measured in S2 is substituted into the measurement model to obtain time-varying meshing stiffness of the gear. The application improves the measurement precision and efficiency of the gear time-varying meshing stiffness.

The application relates to the technical field of mechanical dynamics, and discloses a gear dynamics modeling method considering the influence of meshing position change. The gear dynamics modeling method realized by the method adopts a gear meshing stiffness model which no longer simplifies the meshing stiffness between a driving wheel and a driven wheel into equivalent meshing stiffness acting on a node with a fixed spatial position and only a change in amplitude, but truly considers the change of the instantaneous meshing position between the driving wheel and the driven wheel, that is, the gear meshing stiffness model considers the change of the stiffness amplitude in the time dimension and the change of the stiffness position in the space dimension, and the gear meshing stiffness model is more in line with the actual meshing state of the gear.

This invention belongs to the field of mechanical dynamics technology, and discloses an improved method, medium, and electronic device for load-bearing contact analysis of spiral bevel gears. Based on the tooth contact analysis method, the geometric parameters of the tooth surfaces of the large and small gears are obtained, a load-bearing contact analysis model of the spiral bevel gear pair is constructed, and the overall compliance matrix, overall contact compliance matrix, and local contact compliance matrix of the tooth surface are calculated. A deformation compatibility iterative equation is established, its ill-conditioned nature is analyzed, and a preprocessing matrix is ​​established to improve the deformation compatibility iterative equation. After improvement, the time-varying meshing stiffness and tooth surface load are solved. Based on the tooth surface load, the principal curvature of the tooth surface of the large and small gears is calculated using the Euler analytical method and the principal direction is determined. The contact stress is then solved using Hertz contact theory. This method improves upon the problems of traditional tooth load-bearing contact analysis methods, which suffer from low accuracy and efficiency due to the ill-conditioned nature of the contact compliance matrix under low load conditions and the reliance on numerical differences for curvature calculation.

The application discloses a constant engagement characteristic pair-constructing external engagement cylindrical gear pair, and relates to the technical field of gear transmission, comprising a pair-constructing cylindrical gear I and a pair-constructing cylindrical gear II based on conjugate curves. The normal tooth profile curves of the pair-constructing cylindrical gear I and the pair-constructing cylindrical gear II are continuous combination curves with the same curve shape, facilitating machining with the same cutter; the common normal line at the inflection point or the tangent point of the continuous combination curve passes through the node of the gear pair, and the inflection point or the tangent point position can be adjusted according to actual requirements to adjust the sliding rate of the gear pair; the coincidence degree is designed as an integer, and the engagement stiffness can be kept constant, thereby greatly improving the dynamic engagement performance of the gear pair. In the application, the normal tooth profile of the pair-constructing cylindrical gear I and the pair-constructing cylindrical gear II is the same, the engagement point curvature radius is constant and tends to infinity, the sliding rate is constant, and the engagement stiffness is constant, and the application has the technical characteristics of low manufacturing cost, high bearing capacity, high transmission efficiency, low vibration and noise and the like.

The invention relates to the technical field of mechanical equipment monitoring, in particular to a rotary machinery gear transmission system kinetic parameter identification method, which comprises the following steps: step 1, based on a gear dynamics theory, considering meshing rigidity and meshing damping of a time-varying gear pair, and establishing a transmission chain torsional vibration kinetic model of rotary machinery; step 2, based on the transmission chain dynamic model established in the step 1, respectively establishing parameter identification objective functions of rotational inertia and meshing rigidity; 3, data of angular displacement, angular acceleration and torque of the transmission chain are continuously collected, and data preprocessing is completed; 4, reconstructing a target function of rotational inertia under the reference of the rotor coordinates, and solving the rotational inertia; step 5, based on the rotational inertia identified in the step 4, solving a meshing stiffness objective function; according to the method, the problem that the stability and the reliability of the gear transmission system cannot be accurately predicted by an existing identification method is solved.

A method for calculating the time-varying meshing stiffness of a cracked gear pair considering friction includes: obtaining gear parameters and crack parameters, establishing a gear meshing model, calculating the meshing angle range, and establishing a first cantilever beam model of a healthy gear without considering friction; establishing a second cantilever beam model of a cracked gear without considering friction; calculating the time-varying friction coefficient based on elastohydrodynamic lubrication theory; establishing a third cantilever beam model of a cracked gear considering friction; and deriving, using the potential energy method, a first calculation method for the time-varying meshing stiffness of a healthy gear pair without considering friction, a second calculation method for the time-varying meshing stiffness of a cracked gear pair without considering friction, and a third calculation method for the time-varying meshing stiffness of a cracked gear pair considering friction, based on the three gear cantilever beam models. This invention provides a more accurate time-varying meshing stiffness calculation for the gear pair using a more precise model. The results obtained using this method can effectively diagnose crack faults in gear transmission systems under actual operating conditions.

This invention discloses a nonlinear dynamic modeling method for crack evolution in a helical gear transmission system for vehicles, which includes the following steps: (1) establishing a calculation formula for meshing stiffness of the helical gear pair under cracked conditions using the slice integration method and the potential energy method; (2) establishing an equivalent circuit model of the motor by combining the principles of circuit theory and magnetic circuit theory with coordinate transformation relationship; (3) building an electromechanical coupling model of the motor-gear system based on the mechanical relationship between the motor and the gear transmission system; (4) establishing a model of the electromechanical coupling helical gear transmission system for vehicles and solving the influence mechanism of crack evolution of helical gears on the dynamic characteristics of the electromechanical coupling helical gear transmission system for vehicles; the beneficial effect is that this invention establishes a nonlinear fault dynamic model of the electromechanical coupling transmission system for new energy vehicles, which is of great significance for the design, optimization and life prediction of the helical gear transmission system for new energy vehicles.

This invention discloses a method for solving the dynamic coupling transmission error of a helical gear combined transmission system. The method first obtains the basic parameters of the helical gear combined transmission system and establishes a three-dimensional model of the system. Second, it calculates the static transmission error and time-varying meshing stiffness during gear meshing based on finite element analysis. Next, it establishes an 18-DOF dynamic model of the helical gear combined transmission system, considering time-varying meshing stiffness, installation and machining errors, tooth flank clearance, and meshing damping. Then, it inputs gear parameters and operating conditions, including input torque, output torque, and input speed, and uses the fourth-order variable-step Runge-Kutta method to obtain the dynamic response of the helical gear combined transmission system. Finally, it obtains the dynamic coupling transmission error of the helical gear transmission system based on the dynamic solution results.

The present application relates to the field of new energy vehicle electric drive technology, and particularly relates to a method and device for optimizing NVH performance of a gear transmission of an electric drive system, a terminal and a medium, the method comprising: performing tooth tip modification on a gear pair of the electric drive system, and using a tooth bearing contact analysis method to calculate time-varying mesh stiffness of the modified gear pair; taking the time-varying mesh stiffness as an excitation source, substituting it into a dynamic equation of the transmission system, and solving to obtain a dynamic response of the transmission system; taking bearing dynamic load in the dynamic response of the transmission system as a boundary condition, establishing a finite element-boundary element coupling model of the gear box, and simulating and predicting noise radiation of the gear box; evaluating improvement effects of different modification schemes on the NVH performance through the simulation and prediction results, and determining optimal gear modification parameters. The present application realizes forward design of simulation driving, shortens development cycle, reduces cost, and effectively improves system NVH quality.

The invention discloses a gear pair meshing stiffness calculation method considering a thermoelastic coupling effect, which relates to the field of gear transmission, and comprises the following steps: establishing a gear temperature field model and a contact model by utilizing a finite element method, obtaining a gear heat conduction matrix and a structural stiffness matrix, and calculating to obtain gear meshing stiffness and tooth surface load distribution based on an actual tooth surface equation. Calculating tooth surface heat flux density based on tooth surface load distribution, tooth surface friction coefficient and relative sliding speed of each meshing position to obtain a gear thermal load matrix, calculating to obtain an equivalent node load matrix according to a gear heat conduction matrix and the thermal load matrix, and calculating to obtain tooth surface thermal deformation by combining the equivalent node load matrix with a gear structure stiffness matrix. And repeating the steps to obtain the meshing rigidity of the gear pair under the thermoelastic coupling effect. According to the method, the gear contact state iterative solution model based on the potential energy method, the matrix polycondensation method and the slicing thought is established, the requirement for computing equipment is lowered, and the solution efficiency is improved.

The application provides a gear fatigue crack propagation life calculation method and system considering random dynamic load, and the method is as follows: a local plane coordinate system is established at a crack tip, and a crack propagation equation is constructed; time-varying mesh stiffness containing a tooth root crack feature is calculated; a vibration differential equation of a gear mesh pair is constructed and solved, and dynamic meshing forces of the gear pair under different crack states are obtained; the dynamic meshing forces of the gear pair under different crack states are processed, and a load spectrum is prepared, and variable amplitude load data with multi-periodicity are obtained; the variable amplitude load data are taken as boundary conditions, crack propagation is simulated, gear fatigue crack propagation data are read from a finite element data file; stress intensity factors are calculated based on the gear fatigue crack propagation data; and fatigue crack propagation life is estimated based on the Paris formula and the stress intensity factors. The method can improve the reliability and fatigue crack propagation life of the gear, improve the safety of equipment, and reduce maintenance costs.

The invention discloses a noise prediction method, system and device of a gear transmission system and a medium, and relates to the technical field of vehicle NVH. The method aims at solving the problems that in the prior art, a gear noise prediction model is tedious in calculation, and it is difficult to quantitatively evaluate the influence of microscopic modification and dislocation amount. The method comprises the following steps: determining helical gear pair meshing stiffness by utilizing straight gear stiffness model integration based on a slicing method; determining the vibration displacement by using a vibration displacement model considering the tooth direction crowning quantity, the tooth shape crowning quantity, the tooth top edge trimming quantity and the dislocation quantity; and finally, calculating a total noise value based on a noise prediction model comprising three parts of macroscopic parameters, power and vibration displacement. According to the method, theoretical derivation is combined with test correction, rapid and accurate prediction of the noise of the helical gear of the electric drive assembly is achieved, and gear modification design can be effectively guided.

The invention provides a digital twin tooth surface wear degradation morphology prediction method, which is applied to the field of gear transmission systems, and comprises the following steps: constructing a physical information neural network wear depth prediction model constrained by a gear transient wear model, obtaining a model for predicting a new tooth profile after the gear is worn and a rough morphology model for predicting tooth surface evolution after the gear is worn; a gear wear time-varying meshing stiffness calculation model is constructed, and the corrected wear gear time-varying meshing stiffness is obtained; in combination with a lumped parameter method, a gear system dynamic model is constructed, and a gear wear degradation transmission system simulation dynamic response is obtained; according to the method, the gear bearing supporting rigidity and damping are calibrated, the tooth surface dynamic meshing force is corrected, and finally the corrected tooth surface abrasion depth and the corrected tooth profile and tooth surface morphology are obtained. And interaction of actually measured vibration signals and tooth surface morphology virtual detection in gear box wear degradation is realized.

The application relates to the technical field of mechanical dynamics, in particular to a fault gear time-varying meshing stiffness calculation method considering crack positions, which comprises the following steps: establishing a gear fault calculation model; determining corresponding crack category information, and pre-storing crack gear section division rules corresponding to the crack category information; detecting a crack position on the gear that has occurred a fault, adopting the crack gear section division rule to divide the crack position into sections to obtain a plurality of crack sub-sections; obtaining the bending stiffness and the shear stiffness of each crack sub-section for each crack sub-section; and summing the bending stiffness and the shear stiffness of each crack sub-section to obtain the bending stiffness and the shear stiffness of the fault gear. The bending stiffness and the shear stiffness of the fault gear can be obtained by inputting the parameters of the crack, and the calculation efficiency is higher.

The invention relates to the technical field of new energy automobile electric driving, in particular to an optimization method and device for gear transmission NVH performance of an electric driving system, a terminal and a medium, and the method comprises the steps that tooth crest modification is conducted on a gear pair of the electric driving system, and the time-varying meshing rigidity of the gear pair subjected to modification is calculated through a gear tooth bearing contact analysis method; taking the time-varying meshing stiffness as an excitation source, substituting the time-varying meshing stiffness into a kinetic equation of the transmission system, and solving to obtain a kinetic response of the transmission system; the method comprises the following steps: establishing a finite element-boundary element coupling model of a gearbox by taking a bearing dynamic load in dynamic response of a transmission system as a boundary condition, and performing simulation prediction on noise radiation of the gearbox; and the improvement effect of different modification schemes on the NVH performance is evaluated through the simulation prediction result, and the optimal gear modification parameters are determined. The forward design of simulation driving is realized, the development period is shortened, the cost is reduced, and the NVH quality of the system is effectively improved.

The application discloses a bevel gear engagement stiffness calculation method, system, device and storage medium. The bevel gear engagement stiffness calculation method comprises the following steps: determining a target contact area of an engagement interface of a bevel gear pair in the case of gear tooth bearing contact analysis on the engagement process of the bevel gear pair; determining the entrainment velocity and the first bevel gear engagement stiffness of the bevel gear pair based on the target contact area, and constructing a bevel gear mixed thermal elastohydrodynamic lubrication control equation based on the entrainment velocity; in the case of setting a first pressure distribution value, a first oil film thickness distribution value and a first temperature field distribution value, determining the second bevel gear engagement stiffness through the bevel gear mixed thermal elastohydrodynamic lubrication control equation based on the first pressure distribution value, the first oil film thickness distribution value and the first temperature field distribution value, and determining the target engagement stiffness of the bevel gear pair based on the first bevel gear engagement stiffness and the second bevel gear engagement stiffness, thereby improving the accuracy of the bevel gear engagement stiffness calculation.

The application discloses a kind of based on the meshing stiffness calculation method of modification planetary gear based on tooth surface contact analysis, comprising the following steps: S100. Based on the engagement of the cutter and the modification gear when the cutter processes modification gear, the full tooth surface equation of the modification gear is established;S200. Based on the engagement of two modification gears, the contact equation of two modification gears is established, and the contact trajectory when two modification gears engage is calculated according to the contact equation;S300. According to the full tooth surface equation and the contact trajectory, the tooth surface point information on the contact trajectory is obtained, and the meshing stiffness is calculated using potential energy method according to the tooth surface point information.The meshing stiffness calculation method of modification planetary gear based on tooth surface contact analysis of the application can quickly and accurately calculate the time-varying meshing stiffness of planetary gear after modification, which is beneficial to the subsequent analysis of planetary gear system and suitable for popularization and use.

This invention relates to a method for obtaining the comprehensive meshing stiffness of a spiral bevel gear. The method specifically comprises: S1: Based on multi-tooth pair and meshing state analysis, and combining the given gear displacement angle and the rotation angle of the target tooth pair at the theoretical meshing position, obtaining the single tooth pairs that generate contact; S2: Based on the penetration amount between single tooth pairs and the meshing stiffness between single tooth pairs, obtaining the distributed load of all tooth pairs that generate contact; S3: Based on the deformation amount between single tooth pairs and the distributed load, obtaining the comprehensive meshing stiffness under multi-tooth meshing conditions. This invention incorporates the penetration amount between tooth pairs, more closely approximating the actual situation, thus reducing the error compared to reality.

The invention discloses a propulsion shafting vibration prediction method considering a bidirectional coupling effect of a gear backlash, and the method comprises the following steps: S1, obtaining a first time-varying meshing stiffness and an effective transmission error after gear backlash correction through gear backlash function correction based on an initial gear backlash at a moment t; s2, related parameters of a gear meshing unit are corrected through the first time-varying meshing stiffness and the effective transmission error, so that a propulsion shafting motion differential equation corrected through the gear backlash is established, the propulsion shafting motion differential equation is solved, and vibration displacement of all nodes of the propulsion shafting at the t moment is obtained; and S3, correcting the gear backlash through the vibration displacement of the propulsion shafting at the moment t to obtain an initial gear backlash at the moment t + 1, and repeating the steps S1 to S3 to obtain the vibration characteristics of gear backlash-shafting vibration bidirectional coupling of the propulsion shafting at any moment. The dynamic gear backlash is introduced into propulsion shafting calculation, and support is provided for shafting vibration prediction.

The application discloses a phase-adjustable combined staggered herringbone gear planetary gear train transmission, which comprises a primary sun gear assembly, a secondary sun gear assembly, a primary long planetary gear assembly, a secondary short planetary gear assembly, a primary inner gear ring assembly, a secondary inner gear ring assembly and a planet carrier assembly; all the gears are staggered herringbone gears; one primary planetary gear is engaged with the primary sun gear and the primary inner gear ring, and the other primary planetary gear is engaged with the secondary planetary gear and the secondary inner gear ring; the secondary planetary gear is engaged with the secondary sun gear; the primary sun gear assembly, the secondary sun gear assembly and the primary inner gear ring assembly are different gear input ends, and the planet carrier assembly is an output end. The application reduces the amplitude of the engagement stiffness fluctuation and the engagement impact in the engagement process by adjusting the phase of the herringbone gear, reduces vibration and noise, improves the load sharing characteristics of the planetary gear train through the floating installation of the elastic pin shaft and the planetary gear, and is suitable for high-speed heavy-load working conditions.

The planetary gearbox of the planet carrier double-wall type structure comprises a planet carrier assembly, a connecting sleeve arranged on one side of the planet carrier assembly, a bearing seat assembly arranged on the other side of the planet carrier assembly and a gear ring arranged on the outer side of the planet carrier assembly in a sleeving mode, one end of the gear ring is connected with the connecting sleeve, and the other end of the gear ring is connected with the bearing seat assembly. According to the method provided by the embodiment of the invention, the gear ring is connected with the connecting sleeve and the bearing seat assembly, so that the overall stability of the gear ring is improved, and the overall meshing rigidity of the epicyclic gear train is effectively improved. Meanwhile, the mounting holes are correspondingly formed in the first planet carrier and the second planet carrier respectively, and the two ends of the pin shaft penetrate into the mounting holes of the first planet carrier and the second planet carrier respectively, so that the perpendicularity of the pin shaft relative to the first planet carrier and the second planet carrier is effectively improved, and the stability of the pin shaft is improved; therefore, the reject ratio of the planet carrier assembly is effectively reduced, and the stability requirement under long-term work is met.

The invention discloses a voxel evolution model-based gear peeling time-varying meshing stiffness calculation method. The method comprises the following steps of: constructing a three-dimensional voxel evolution model for describing tooth surface peeling damage initiation and expansion; constructing a voxel growth probability model, calculating a growth probability of a healthy voxel adjacent to the seed voxel being converted into a peeling state, and updating a three-dimensional voxel mask matrix representing a voxel unit state based on a Monte Carlo method; establishing a mathematical mapping relation between a three-dimensional voxel damage field and a two-dimensional slice section geometric attribute, and calculating a residual effective cross section area and a residual effective cross section inertia moment after being influenced by stripping; establishing a stiffness component analysis model considering peeling damage, substituting the residual effective cross-sectional area and the residual effective cross-sectional inertia moment into the component analysis model, and calculating each stiffness component; according to the actual meshing process of the gear, the final time-varying meshing stiffness is synthesized. According to the method, the precision and reliability of rigidity calculation can be improved.

The application discloses a kind of micro gear dynamics modeling methods containing rotation pair gap, belong to gear transmission system dynamics simulation technical field.The method is established by considering the calculation model of meshing stiffness of rotation pair gap based on the meshing principle of involute gear and potential energy method, deduces the calculation formula of important parameters such as gear meshing angle, side clearance, coincidence degree, and establishes the time-varying meshing stiffness calculation model of gear containing rotation pair gap;The application comprehensively considers the change of gear pair center distance caused by the existence of rotation pair gap, influences the meshing stiffness of gear, load distribution coefficient, meshing angle and side clearance etc., the change of these parameters will cause gear to present different nonlinear dynamic behavior, provide theoretical support for noise reduction and life extension of gear transmission system.

The invention discloses a bevel gear pair time-varying meshing stiffness calculation method considering tooth surface pitting corrosion and gluing damage, and aims to solve the problems that a straight bevel gear pair time-varying meshing stiffness calculation method does not consider the real section shape of a gear and neglects the influence of tooth surface pitting corrosion and gluing damage on the contact state of a gear pair. And the calculation precision of the time-varying meshing stiffness of the straight bevel gear pair is low. According to the method, a cantilever beam model of the straight bevel gear is established, the influence of friction force between tooth surfaces in the gear meshing process is considered, the straight bevel gear is sliced to obtain equivalent straight gears, and the time-varying meshing stiffness of the straight bevel gear pair is defined as the sum of the meshing stiffness of all the equivalent straight gears. The meshing rigidity of the equivalent spur gear is determined by calculating the stress, geometric dimension parameters, rotational inertia and cross sectional area of the equivalent spur gear, the oil film thickness, the oil film pressure, the normal oil film rigidity and the normal contact rigidity of the multi-ellipsoidal micro-convex bodies on the tooth surface of the equivalent spur gear, so that the time-varying meshing rigidity of the straight bevel gear pair is obtained.

The application provides a gear wear uniformity identification method based on gear box vibration response characteristics. The constraint relationship in each element of the gear box in the actual operation process is analyzed, the description mode of the system boundary condition is determined, and a rigid-flexible coupling model containing the gear box body and the gear transmission system is established. The dynamic meshing stiffness of the uniform and non-uniform wear gears is calculated by using a numerical calculation method, a system dynamics calculation model is constructed, the influence degree of different wear modes on the gear meshing stiffness and the wear amount is quantitatively evaluated, the gear meshing force and the box vibration response law under the uniform and non-uniform wear are obtained in combination with the rigid-flexible coupling model, a simulation test bench is built, the gear box vibration signals are collected and the features are extracted, and the wear uniformity identification is realized. The gear box dynamic model is established by using the rigid-flexible coupling method and the numerical calculation comprehensive method, the change of the meshing stiffness and the wear amount and the mutual influence of the shell and the transmission system are considered, and the gear wear uniformity can be accurately calculated.

The invention provides a dynamic response solving method for a tooth profile modification gear pair. The method comprises the steps of geometric model construction, time-varying meshing stiffness model construction, dynamic differential equation construction, contact judgment, dynamic response solving and the like. According to the dynamic response solving method for the tooth profile modification gear pair, the problem of non-involute contact can be solved, and the contact state of the gear pair can be judged in real time. Besides, the model is a general model for solving the dynamic response of the tooth profile modification gear pair, the problems of low precision of an analytical method, low efficiency of a numerical method, high cost of a test method and the like are considered in the method, and the calculation precision is ensured while the calculation efficiency is considered.

This invention discloses a method for constructing a calculation model for the transmission accuracy of an RV reducer that considers component errors. The method includes: constructing an equivalent mechanical model: based on the lumped parameter method, the sun gear, planetary carrier, etc., are considered rigid bodies, and gear meshing and bearing support are equivalent to linear springs; assuming assumptions such as constant sun gear speed, a coordinate system and a follower coordinate system are established, generalized micro-displacement parameters (including translational and rotational degrees of freedom) are defined, and a generalized micro-displacement column vector is constructed to clarify the mechanical characterization of the multi-degree-of-freedom system; establishing a system mechanical equation set: based on the error decomposition principle, combined with errors such as sun gear manufacturing eccentricity and crankshaft cam eccentricity, deformation coordination equations for sun gear support and gear meshing are constructed; the gear meshing stiffness, bearing support stiffness, and elastic force are correlated to construct physical equations; force balance equations are established through force analysis of each component, and a system of mechanical equations for transmission accuracy is formed. Solving these equations allows for the calculation of the transmission accuracy of the RV reducer.

The application discloses a kind of rigid-flexible coupling dynamics modeling methods of transmission system, it includes the following steps: (1) the random wind speed prediction model is established, random wind speed is predicted based on double parameter Weibull model, determines input speed and input torque;(2) the time-varying mesh stiffness calculation model is established;(3) the calculation model of gear face friction force is established;(4) the bearing force calculation model is established;(5) the inner gear ring is discretized;(6) the meshing displacement and meshing force between three-stage gear pairs are calculated;(7) the planetary gear-bearing system dynamics vibration differential equation is established, and the vibration displacement curve of three-stage gear pair is obtained by solving;Beneficial effect is that the present rigid-flexible coupling gear-bearing system dynamics modeling related technical blank is filled by calculating random wind speed, time-varying mesh stiffness, gear face friction, time-varying support stiffness and gear ring flexible coupling dynamics equation.