Method for analyzing dynamic behavior of wind power double-row tapered roller bearing pin-through cage

Abstract

The application discloses a kind of wind power double-row tapered roller bearing through pin retainer dynamics behavior analysis method, for wind power heavy load, variable speed, complex service conditions of impact, face by the retainer main body, positioning through pin, big washer and small washer are composed of through pin retainer, this method establishes multi-coordinate system system, solves the relative motion velocity of roller and raceway, rib and through pin contact area;Based on contact state determination, calculate the radial collision force between roller and through pin, the axial contact force between roller and big and small washer and the circumferential sliding friction torque around through pin axis;Double-row tapered roller-through pin retainer multibody coupling nonlinear dynamics equation set is constructed, and GSTIFF variable step size integration algorithm is used to solve and is iterated with 10-3 as convergence threshold value, finally output through pin retainer dynamics characteristic result.The application can be used for wind power bearing retainer structure optimization, failure prediction and life check by analyzing the specific mechanical behavior and movement law of through pin retainer.

Description

Technical Field

[0001] This invention belongs to the field of bearing dynamics modeling and analysis technology, specifically relating to a method for analyzing the dynamic behavior of a wind turbine double-row tapered roller bearing with a pin cage. Background Technology

[0002] Double-row tapered roller bearings for wind turbines are core load-bearing components of the main shaft and yaw / pitch systems. They can simultaneously withstand combined axial, radial, and overturning moment loads, making them suitable for complex service conditions such as heavy loads, variable speeds, and impacts. The pin-cage design consists of the cage body, locating pins, large washers, and small washers. It features high rigidity, strong stability, and excellent impact and fatigue resistance, making it the mainstream structure for large-size tapered roller bearings in wind turbines.

[0003] Existing bearing dynamics analysis methods are mostly based on traditional cages or full complement bearings, and no dedicated dynamic model has been established for pin-cage bearings. Pin-cage bearings exhibit unique mechanical behaviors such as radial collision between rollers and pins, axial contact between rollers and washers, and circumferential frictional torque. Traditional models cannot accurately describe their motion constraints, force transmission, and dynamic characteristics, making it difficult to achieve failure prediction, life assessment, and structural optimization. To accurately describe the true dynamic characteristics of pin-cage bearings in wind turbine double-row tapered roller bearings, a dynamic behavior analysis method adapted to wind power operating conditions and coupling the interactions of multiple components is urgently needed. Summary of the Invention

[0004] To address the shortcomings of existing technologies, this invention provides a method for analyzing the dynamic behavior of pin-cage in wind turbine double-row tapered roller bearings. A multi-body coupled dynamic model of rollers, pins, and cage is constructed, fully considering unique mechanical behaviors such as radial collision, axial contact, and circumferential frictional torque. This model can accurately characterize the true dynamic characteristics of the pin-cage, providing theoretical support for the reliability design and lifespan improvement of wind turbine bearings. The specific technical solution adopted in this invention is as follows: A method for analyzing the dynamic behavior of a double-row tapered roller bearing cage in wind turbines includes the following steps: S1. Obtain the structural parameters, material properties, wind power operating conditions, and lubrication parameters of the wind turbine double-row tapered roller bearing, and establish a multi-coordinate system including the inertial coordinate system, inner ring coordinate system, cage coordinate system, tapered roller coordinate system, and pin-cage axis coordinate system. S2. Determine the position and motion parameters of the inner ring, outer ring, tapered rollers, and pin cage. Solve for the tapered roller rotation speed, cage revolution speed, relative speed between the rollers and the inner and outer raceways and the inner ring large flange contact area, and relative motion speed between the rollers and the pin contact area based on the motion constraints. S3. Determine the contact state based on the relative motion between the roller and the pin cage, and solve for the radial collision force between the roller and the pin, the axial contact force between the roller and the large and small washers, and the circumferential sliding friction torque around the pin axis. S4. Establish a set of nonlinear dynamic differential equations for the adapted pin cage, including the balance equations for tapered rollers under traditional cages, the balance equations for tapered rollers under pin cages, the balance equations for pin cages, and the balance equations for the inner ring. S5. Based on bearing dynamics theory, the GSTIFF variable step size integral algorithm is used to solve the equation set and output the normal contact load between the tapered roller and the raceway, the rolling friction resistance of the roller surface, the sliding friction resistance of the roller surface, the acceleration and angular velocity of the pin holder, and the force and displacement of the pin.

[0005] S6, with 10 -3 To determine the solution error, a convergence threshold is used. If convergence is achieved, the iteration proceeds to the next time step. After the preset analysis time is reached, the dynamic characteristics of the pin cage are output.

[0006] Furthermore, the pin retainer consists of a retainer body, a positioning pin, a large washer, and a small washer. The inner hole of the roller and the outer circle of the pin form radial contact collision, and the two end faces of the roller form axial limiting contact with the large and small washers respectively.

[0007] Furthermore, in S3, the contact state is determined based on the penetration depth between the inner hole of the roller and the pin, and the total radial collision contact force, the transient sliding friction force along the pin axis, and the circumferential sliding friction torque are calculated.

[0008] Furthermore, S6 includes the following: S6.1 Solve the dynamic equations time-by-time and determine whether the error is within 10. -3 If the condition is met, the relationship between the position and motion at the next moment will be output. S6.2 Determine if the analysis time has been reached. If it has, output the dynamic results of the pin-piercing cage; otherwise, return to S2 for iterative looping. Furthermore, the preset convergence error is 10. -3 .

[0009] The beneficial effects of this invention are: This invention establishes a dedicated multibody coupled dynamic model for pin-cage bearings in wind turbines, accurately describing the three-way contact behavior of the rollers, pins, and washers. It uses the GSTIFF variable-step integral method to iteratively calculate the dynamic differential equations of each bearing component, finally outputting the dynamic behavior results between the pin-cage, pins, and tapered rollers. This model fully considers the characteristics of wind power operating conditions and can accurately predict cage motion, stress, and failure risks, supporting structural optimization and lifespan improvement. Furthermore, the model has strong applicability, covering the dynamic analysis of pin-cage bearings of different sizes and assembly forms. Attached Figure Description

[0010] To more clearly illustrate the technical solutions in the embodiments of the present invention or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only some embodiments of the present invention. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0011] Figure 1 This is a flowchart of the dynamic behavior analysis method described in this invention; Figure 2 This is a schematic diagram of the bearing coordinate system in an embodiment of the present invention; Figure 3 This is a schematic diagram of the bearing assembly speed analysis model in an embodiment of the present invention; Figure 4 Figure a is a schematic diagram of the geometric relationship between the tapered roller and the cage pin in an embodiment of the present invention; wherein Figure a is a schematic diagram of the ideal state, Figure b is a schematic diagram of the contact state, and Figure c is a schematic diagram of the mathematical model. Figure 5 This is a schematic diagram illustrating the geometric relationship between the tapered rollers and the large (small) washer of the cage in an embodiment of the present invention. Figure 6 This is a schematic diagram of the interaction between the tapered roller and the raceway in an embodiment of the present invention; Figure 7 This is a schematic diagram of the interaction between the tapered roller and the pin in an embodiment of the present invention; Figure 8 This is a simulation result of the collision force between the tapered roller and the pin cage in an embodiment of the present invention.

[0012] In the diagram: 1. Inner ring; 2. Outer ring; 3. Pin retainer; 3.1. Pin; 3.2. Large washer; 3.3. Small washer; 4. Roller. Detailed Implementation

[0013] The technical solution of the present invention will be clearly, completely and in detail below with reference to specific embodiments. These embodiments are implemented based on the technical solution of the present invention, but the scope of protection of the present invention is not limited to the following embodiments.

[0014] The wind turbine double-row tapered roller bearing includes an inner ring 1, an outer ring 2, a pin cage 3, and rollers 4. The pin cage 3 consists of a cage body, a pin 3.1, a large washer 3.2, and a small washer 3.3. The inner hole of the roller 4 forms radial contact with the outer circle of the pin 3.1, and the two end faces of the roller 4 form axial limiting contact with the large washer 3.2 and the small washer 3.3, respectively.

[0015] like Figure 1-8As shown, this invention provides a method for analyzing the dynamic behavior of a double-row tapered roller bearing with a pin cage in wind turbine applications, comprising the following steps: S1. Obtain the initial conditions of the wind turbine double-row tapered roller bearing and establish a multi-coordinate system for the bearing.

[0016] The initial conditions include the bearing's structural parameters, material properties, wind power operating conditions, and lubrication parameters. Based on these initial conditions, a coordinate system is constructed that includes an inertial coordinate system, an inner ring coordinate system, a cage coordinate system, a tapered roller coordinate system, and a pin-cage-pin coordinate system.

[0017] Specifically, in this embodiment, the parameters are selected as follows: As shown in Table 1, the structural parameters include: outer diameter, inner diameter, raceway inclination angle, width, rolling element diameter, roller structural parameters, and pin cage structural parameters, etc. As shown in Table 2, the material properties include: the elastic modulus, Poisson's ratio and density of each component of the bearing; Operating conditions include: radial force, axial force, overturning moment, and rotational speed; As shown in Table 3, the lubrication parameters include: lubricant density, dynamic viscosity, viscosity-pressure coefficient, and thermal conductivity.

[0018] Furthermore, to describe the forces and motions between the components during operation, the coordinate systems of each component of the bearing are determined as follows: Inertial coordinate system The origin O of this coordinate system is located at the geometric center of the bearing, and the X-axis is aligned with the bearing's rotation axis; the interactions between all components can be represented in the inertial coordinate system. Inner coordinate system The origin is located at the geometric center of the inner circle. The shaft coincides with the rotation axis of the outer ring, and the positive direction of the initial position is consistent with the X-axis direction of the bearing's inertial coordinate system; cage coordinate system , The axis coincides with the rotation axis of the cage, and the positive direction of the initial position is consistent with the X-axis direction of the inertial coordinate system; Conical Roller Coordinate System The origin of the j-th conical roller coordinate system Located at the mass center of the j-th roller, Along the center line of the roller's rotation and pointing towards the small end of the roller; Pin-cage coordinate system The origin of the coordinate system for the j-th pin retainer pin axis Located at the centroid of the j-th pin, Along the center line of the roller's rotation and in the direction of the small end of the roller.

[0019] S2. Based on the position and motion parameters of each bearing component, and according to the motion constraints of each bearing component, the relative motion speed between each component is obtained. When determining the relative motion speed between the components, the relative motion speed between the rollers of the bearing and the cage is calculated based on the position and motion parameters of each component, as follows: In the formula, and These are the instantaneous relative linear velocities of the j-th roller with the inner and outer raceways in the contact area, respectively. It is the instantaneous relative linear velocity of the contact area between the roller and the inner ring large flange; The relative speed of motion between the roller bore and the contact area of ​​the pin shaft; The inner orbital angular velocity; The outer ring's angular velocity during revolution; To maintain the orbital angular velocity; The angular velocity of the roller's rotation; This represents the average contact angle of the bearing. The bearing pitch circle diameter; This is the distance from the center of the contact area between the roller and the inner ring large flange to the bearing axis; This is the distance from the center of the contact area between the roller and the inner ring large flange to the roller axis.

[0020] S3. Solve and output the forces between bearing components, including the interaction force between the rollers and the cage pins; The interaction is mainly manifested as follows: in the radial dimension, there is continuous contact, collision and sliding between the inner wall of the roller and the outer circle of the pin; in the axial dimension, the two end faces of the roller are subject to axial restraint and thrust friction by the large and small washers respectively. In the formula, The penetration depth during the contact process between the tapered roller and the cage pin; according to The positive or negative sign indicates the stage of the roller and pin. ; The radius of the inner hole of the tapered roller; To maintain the radius of the cage pin; This refers to the total radial impact contact force between the inner bore of the tapered roller and the cage pin. This refers to the transient sliding friction force of the tapered roller along the axis of the through pin. The circumferential sliding friction torque is about the axis of the through pin. This refers to the contact load between the large end face (spherical base surface) of the tapered roller and the large washer of the cage; The contact load between the small end face of the tapered roller and the small washer of the cage; S4. Establish the nonlinear dynamic differential equations for each bearing component, including the dynamic equilibrium equations for tapered rollers under a conventional cage, the dynamic equilibrium equations for tapered rollers under a pin-cage, the dynamic equilibrium equations for a pin-cage, and the dynamic equilibrium equations for the inner ring. Details are as follows: Traditional cage rollers in inertial coordinate system The nonlinear dynamic differential equation in is as follows: The pin retains the rollers between the cages in the inertial coordinate system The nonlinear dynamic differential equation in is as follows: in, , , These are the inner and outer contact angles and the azimuth angle of the roller in the inertial coordinate system, respectively. This represents the average contact angle of the bearing. For large flange inclination angle; , These represent the contact loads between the rollers and the inner and outer raceways, respectively. , The radial impact contact load between the inner bore of the roller and the cage pin; This refers to the contact load between the large end face (spherical base surface) of the tapered roller and the large washer of the cage; The contact load between the small end face of the tapered roller and the small washer of the cage; , These are the frictional forces between the rollers and the inner and outer raceways, respectively. , These represent the frictional force and normal load at the large flange of the roller, respectively. This refers to the transient sliding friction force of the roller along the axis of the through pin; The frictional resistance torque due to the roller's rotation; , Torque for restoring the roller's attitude; , , The circumferential sliding friction torque of the roller about the axis of the through pin; This refers to the torque between the roller and the cage pocket; , , , This refers to the total torque generated between the raceway and the tapered rollers by the contact load and the drag force, respectively. The diameter of the large end of the roller; , , The moment of inertia of the roller; , , This represents the component of the roller's center of mass acceleration in the inertial coordinate system. , , The angular acceleration components of the roller in the inertial coordinate system; The pin-cage in the inertial coordinate system The nonlinear dynamic differential equation in is as follows: Inner circle in inertial coordinate system The nonlinear dynamic differential equation in is as follows: In the formula, This represents the average contact angle of the bearing. Let be the azimuth angle of the roller in the inertial coordinate system; The radius from the center of mass of the roller to the axis of rotation of the bearing; This is the distance from the center of the contact area between the roller and the inner ring large flange to the bearing axis; The axial distance from the center of mass of the roller to the center of the bearing; For large flange inclination angle; , , , , , These represent the external forces and torques acting on the bearing in the inertial coordinate system. For roller quality; , , To maintain the acceleration of the frame's center of mass along the inertial coordinate system; , , To maintain the moment of inertia of the frame around the inertial coordinate system; , , This is the roller angular acceleration.

[0021] S5. Based on bearing dynamics theory, use the GSTIFF variable step size integral algorithm to solve for the values ​​of dynamic parameters, including the normal contact load between the tapered roller and the raceway, the rolling friction resistance of the tapered roller surface, the sliding friction resistance of the tapered roller surface, the acceleration and angular velocity of the pin holder, and the force and displacement of the pin.

[0022] S6. Determine whether the error of the dynamic equation system meets the convergence error requirement, including the following: S6.1 Solve the dynamic equations time-by-time and determine whether the error is within 10. -3 If the condition is met, the relationship between the position and motion at the next moment will be output. S6.2 Determine if the analysis time has been reached. If it has, output the dynamic results of the pin-piercing cage; otherwise, return to S2 for iterative looping. Furthermore, the preset convergence error is 10. -3 .

[0023] The simulation results are as follows: Based on the aforementioned parameter settings in this embodiment, the simulation results are referenced. Figure 8 To solve for the collision force between the output roller and the pin cage in this invention, the following steps are taken: Figure 8 As can be seen, this invention can output the collision force and contact force between the tapered roller and the pin cage at different times under specified operating conditions. Based on the significant time-varying characteristics exhibited by the local dynamic contact state between the roller and the pin, the contact force amplitude reaches its peak when it cuts from the non-load-bearing area into the load-bearing area. This method can be directly used for pin cage structural dimension optimization, material selection, life verification, and fault early warning. By adjusting parameters and iteratively simulating, it reduces the risk of failures such as cage breakage, pin loosening, and abnormal wear, thereby improving the service life and operational reliability of wind turbine bearings.

[0024] In summary, this invention provides a method for analyzing the dynamic behavior of pin-cage in wind power double-row tapered roller bearings. It constructs a multibody dynamic model to accurately analyze the dynamic behavior of each component under wind power operating conditions. By calculating the geometric relationship and motion state of the rollers, cage pins, and large and small raceways, it can achieve failure prediction and performance optimization of the pin-cage, providing core technical support for the research and development of high-end wind power bearings.

[0025] The core features, basic principles, and advantages of this invention have been elucidated above. This invention is not limited to the above-described embodiments and can be applied to the dynamic analysis and calculation of pin-type cages with different structural forms and assembly methods. Those skilled in the art should understand that this invention is not limited to the foregoing embodiments; the foregoing embodiments and the description are only used to illustrate the technical principles of this invention. Without departing from the spirit and scope of this invention, this invention can also be adjusted, modified, and optimized according to actual application scenarios, and such adjustments, modifications, and optimizations should all fall within the scope of protection claimed by this invention. The scope of protection of this invention is defined by the appended claims and their equivalents.

Claims

1. A method for analyzing the dynamic behavior of a double-row tapered roller bearing cage in wind turbines, characterized in that... Includes the following steps: S1. Obtain the structural parameters, material properties, wind power operating conditions, and lubrication parameters of the wind turbine double-row tapered roller bearing, and establish a multi-coordinate system including the inertial coordinate system, inner ring coordinate system, cage coordinate system, tapered roller coordinate system, and pin-cage axis coordinate system. S2. Determine the position and motion parameters of the inner ring, outer ring, tapered rollers, and pin cage. Solve for the tapered roller rotation speed, cage revolution speed, relative speed between the rollers and the inner and outer raceways and the inner ring large flange contact area, and relative motion speed between the rollers and the pin contact area based on the motion constraints. S3. Determine the contact state based on the relative motion between the roller and the pin cage, and solve for the radial collision force between the roller and the pin, the axial contact force between the roller and the large and small washers, and the circumferential sliding friction torque around the pin axis. S4. Establish a set of nonlinear dynamic differential equations to adapt to the pin cage, including the balance equations of the tapered roller under the pin cage, the balance equations of the pin cage, and the balance equations of the inner ring. S5. The GSTIFF variable step size integral algorithm is used to solve the equation system and output the normal contact load between the roller and the ring, the rolling surface of the roller, the sliding friction resistance, the acceleration and angular velocity of the pin cage, and the force and displacement of the pin. S6, with 10 -3 To determine the solution error, a convergence threshold is used. If convergence is achieved, the iteration proceeds to the next time step. After the preset analysis time is reached, the dynamic characteristics of the pin cage are output.

2. The dynamic behavior analysis method according to claim 1, characterized in that: The pin retainer consists of a retainer body, a positioning pin, a large washer, and a small washer. The inner hole of the roller and the outer circle of the pin form radial contact collision, and the two end faces of the roller form axial limiting contact with the large and small washers respectively.

3. The dynamic behavior analysis method according to claim 1, characterized in that: In S3, the contact state is determined based on the penetration depth between the inner hole of the roller and the pin, and the total radial collision contact force, the transient sliding friction force along the pin axis, and the circumferential sliding friction torque are calculated.

4. The dynamic behavior analysis method according to claim 1, characterized in that, S6 include: S6.1 Solve the dynamic equations time-by-time and determine whether the error is within 10. -3 If the condition is met, the relationship between the position and motion at the next moment will be output. S6.2 Determine if the analysis time has been reached. If it has, output the dynamic results of the pin-piercing cage. If not, return to S2 for iterative loop.

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