A bearing mechanical property calculation method and system considering rotor deformation

Abstract

The application discloses a bearing mechanical property calculation method considering rotor deformation, first, according to rotor load and rotor structure data, a rotor force-deformation coordination equation is established, and the external load borne by the bearing is calculated; a bearing load deformation equation considering bearing centrifugal force and gyroscopic force is established; then, the rotor force-deformation coordination equation and the bearing load deformation equation are solved by using a step-by-step approximation method, and the mechanical property of the bearing is obtained. The combined equation is solved step by step, the solving efficiency of the combined equation is improved, the mechanical property calculation precision of the bearing is improved, and a new method is provided for structure design and performance evaluation of a bearing-rotor system. The bearing and the rotor are regarded as a system, the nonlinear coupling relationship between the additional torque generated by the rotor deformation and the internal load distribution of the bearing is considered, and a more accurate method is provided for mechanical property analysis of the bearing.

Description

Technical Field

[0001] This invention belongs to the field of bearing mechanical analysis, specifically relating to a method and system for calculating bearing mechanical properties considering rotor deformation. Background Technology

[0002] Rolling bearings are critical components in rotating machinery. In some modern engineering applications where rolling bearings are widely used, such as high-speed gas turbines, fans, pumps, and gyroscopes, the bearing must be considered as part of the system in order to accurately determine the deflection, dynamic load, and performance of the bearing-rotor system.

[0003] Bearings and rotor systems are two interconnected components. Current research largely focuses on the impact of bearings on rotor dynamics, but rotor vibration and deformation, in turn, alter the forces acting on the bearings, thus affecting their mechanical properties. Therefore, it is necessary to treat the bearings and rotor as a single system and perform calculations and analyses on both simultaneously. However, solving the mechanical equations of bearings is inherently complex, exhibiting strong nonlinearity. Considering rotor deformation further complicates the solution of the simultaneous equations.

[0004] The internal load distribution, stiffness, and wear of a bearing are directly affected by its supporting force, and these performance indicators directly impact bearing life and system stability. To date, the mechanical properties of individual rolling bearings have been studied in considerable detail. However, these methods analyze individual bearings and do not consider rotor deformation and the additional torque loads caused by that deformation.

[0005] Research on bearing-rotor systems mainly focuses on the effects of rotor imbalance, bearing waviness, and clearance on the rotor system response, but does not address how to consider the impact of rotor deformation and the resulting additional torque on bearing performance. Summary of the Invention

[0006] The technical problem to be solved by the present invention is to provide a method and system for calculating the mechanical properties of bearings that takes into account rotor deformation, thereby solving the problems of the complexity of solving bearing performance by solving simultaneous equations in the prior art and the failure to consider the influence of rotor deformation on bearing mechanical properties.

[0007] To solve the above-mentioned technical problems, the present invention adopts the following technical solution:

[0008] The method for calculating the mechanical properties of bearings considering rotor deformation includes the following steps:

[0009] Step S1: Based on the rotor load and rotor structure data, establish the rotor force-deformation coordination equation and calculate the external load borne by the bearing.

[0010] Step S2: Based on the external load borne by the bearing, establish the bearing deformation equation under load, taking into account the centrifugal force and gyroscopic force of the bearing.

[0011] Step S3: Simultaneously establish the rotor force-deformation coordination equation and the bearing load deformation equation, and solve the simultaneous equations using a step-by-step approximation method to obtain the mechanical properties of the bearing.

[0012] The method for establishing the rotor force-deformation compatibility equation in step S1 is as follows:

[0013] Step S11, construct the force balance equations for the rotor:

[0014] F1+F2-P1=0 (1)

[0015] F1l1-M1+T1-P1(l1-a)+M2=0 (2)

[0016] Where P1 is the assumed external radial load on the rotor, T1 is the torque load, the rotor deforms under the action of the external load, F1 and F2 are the axial loads on the bearings, M1 and M2 are the torque loads on the bearings; l1 is the distance between the two supporting bearings, and a is the distance from the point of application of the external load to the left supporting bearing.

[0017] Step S12: Calculate the bending moment equations for each section of the bearing-rotor system.

[0018] When 0≤x≤a

[0019]

[0020] In the formula, E is the elastic modulus and I is the moment of inertia of the axial cross section;

[0021] Step S13: At x = 0, the radial displacement δ of the shaft and bearing can be obtained by integrating equation (3) twice. r1 The rotation angle θ1 is given by the following formula.

[0022]

[0023] Step S14, similarly, for the section where a≤x≤l1,

[0024]

[0025] In step S15, at x = l1, by integrating equation (6) twice consecutively, the radial displacement of the shaft and bearing is δ. r2 The rotation angle is θ2, and the specific formula is as follows.

[0026]

[0027] In step S16, at x = a, there is only one rotation angle and radial displacement. Therefore, when x = a, equations (4) and (5) should be equal to equations (7) and (8) respectively. Solving these two simultaneous equations yields...

[0028]

[0029] Step S17: Substituting equations (9) and (10) into equations (1) and (2) yields F2 and M2.

[0030]

[0031] In step S2, the specific process of establishing the bearing deformation equation considering the bearing centrifugal force and gyroscopic force is as follows:

[0032] Step S21, after the bearing deforms, the distance between the center of curvature of the inner and outer ring grooves and the center of the ball is...

[0033] Δ ij =(f i -0.5)D w +δ ij (13)

[0034] Δ oj =(f o -0.5)D w +δ oj (14)

[0035] In the formula f i f o These represent the curvature coefficients of the inner and outer grooves, respectively; δ ij δ oj D represents the normal contact deformation of the inner and outer grooves, respectively; w It is the diameter of the steel ball;

[0036] Step S22, at any ball position, the distance between the trajectories of the inner and outer groove curvature centers is

[0037] A 1j =BDsinα 0 +δ a +R i θcosψ j (15)

[0038] A 2j =BDcosα 0 +δ r cosψ j (16)

[0039] Where BD is the distance between the centers of curvature of the inner and outer grooves, and α 0 δ is the initial contact angle of the bearing. a R represents the axial displacement of the bearing inner ring. i Let δ be the radius of the circle tracing the center curvature of the inner groove. r ψ represents the radial displacement of the bearing inner ring.j Let be the azimuth angle of the j-th ball in the inertial coordinate system;

[0040] Step S23: Using the Pythagorean theorem, obtain the compatibility equations for the displacement of the bearing ball and the raceway.

[0041] (A 1j -X 1j ) 2 +(A 2j -X 2j ) 2 -[(f i -0.5)D w +δ ij ] 2 =0 (17)

[0042]

[0043] Among them, X 1j ,X 2j The axial and radial distances between the center of the sphere and the center of curvature of the inner / outer groove.

[0044] Step S24 yields the equilibrium equation for the steel ball.

[0045]

[0046] Among them, Q ij Q is the contact load between the rolling element and the inner ring. oj For the contact load between the rolling element and the outer ring, λ ij With λ oj These are the torque distribution coefficients for the inner and outer gyroscopes, M and M, respectively. gj The gyroscopic torque acting on the rolling element.

[0047] Step S25 also requires establishing the equilibrium equations for the inner ring in order to obtain the displacement δ of the inner ring. a δ r and θ, respectively

[0048]

[0049] The method for solving the simultaneous equations using the successive approximation method in step S3 is as follows:

[0050] Step S31: Input the geometric, material, and operating parameters of the bearing and rotor;

[0051] Step S32: Treat the rotor as a rigid body, disregard rotor deformation, and calculate the initial value of the external load on the support bearing.

[0052] Step S33: Calculate the initial value of the bearing inner ring displacement without considering the bearing centrifugal force and gyro torque based on the initial value of the external load on the bearing obtained in step S32.

[0053] Step S34: Simultaneously establish the bearing load deformation equation and the rotor force-deformation coordination equation without considering the bearing centrifugal force and gyro torque, and correct the initial value of the bearing external load and the unique initial value of the inner ring.

[0054] Step S35: Based on the initial values ​​obtained in step S34, solve the displacement compatibility equation and force balance equation for each ball of each bearing, and obtain the position and deformation value of each ball of the bearing.

[0055] Step S36: Based on the positions and deformation values ​​of each ball in the bearing obtained in step S35, solve the force balance equation of the bearing inner ring and the rotor deformation equation. If the solution does not converge, correct the bearing displacement and bearing external load, and return to step S35; otherwise, output the calculation results.

[0056] The mechanical properties of the bearing include the displacement, velocity, acceleration, and load of each component.

[0057] A bearing mechanical performance calculation system considering rotor deformation is characterized by comprising a processor, wherein the processor applies the bearing mechanical performance calculation method considering rotor deformation to obtain bearing mechanical performance parameters.

[0058] A computer-readable storage medium storing computer-readable instructions that, when executed by a processor, invoke all or part of the steps of the method.

[0059] Compared with the prior art, the present invention has the following beneficial effects:

[0060] 1. This invention proposes a stepwise approximation approach to solve the joint equations step by step, thereby improving the efficiency of solving the joint equations and increasing the accuracy of calculating the mechanical properties of bearings. This provides a new method for the structural design and performance evaluation of bearing-rotor systems.

[0061] 2. This invention treats the bearing and rotor as a system, taking into account the nonlinear coupling relationship between rotor deformation and the resulting additional torque and the internal load distribution of the bearing. Compared with traditional methods, it can more accurately calculate the support reaction force and internal load distribution of the bearing, providing a more accurate method for the mechanical performance analysis of the bearing.

[0062] 3. Since the bearing and rotor are analyzed and calculated as a system, the nonlinearity of the system equations is significantly enhanced, and the solution of the equations is prone to divergence. This invention adopts the idea of ​​stepwise approximation, using the calculation result of a single bearing as the initial value for the calculation of the bearing-rotor system without considering the centrifugal effect of the bearing but considering the rotor deformation, and then using the result as the initial value for the calculation of the bearing-rotor system that simultaneously considers the centrifugal effect of the bearing and the rotor deformation, thereby greatly improving the convergence ability when solving the equations. Attached Figure Description

[0063] Figure 1 This is the bearing-rotor stress deformation model of the present invention.

[0064] Figure 2 This is a schematic diagram showing the position of the center of mass of each component of the bearing of the present invention after deformation under stress.

[0065] Figure 3 This is a schematic diagram of the force applied to the bearing steel ball of the present invention.

[0066] Figure 4 This is a flowchart of the solution process for the basic equations of the bearing-rotor system of the present invention.

[0067] Figure 5 This is a schematic diagram illustrating the influence of rotor length and hollowness on bearing support reaction torque according to the present invention.

[0068] Figure 6 This is a schematic diagram illustrating the influence of rotor length and hollowness on the rotation-to-roll ratio of the present invention.

[0069] Figure 7 This is a schematic diagram showing the relationship between the roll ratio and the torque load of the present invention. Detailed Implementation

[0070] The structure and working process of the present invention will be further described below with reference to the accompanying drawings.

[0071] The method for calculating the mechanical properties of bearings considering rotor deformation includes the following steps:

[0072] Step S1: Based on the rotor load and rotor structure data, establish the rotor force-deformation coordination equation and calculate the external load borne by the bearing.

[0073] Step S2: Based on the external load borne by the bearing, establish the bearing deformation equation under load, taking into account the centrifugal force and gyroscopic force of the bearing.

[0074] Step S3: Simultaneously establish the rotor force-deformation coordination equation and the bearing load deformation equation, and solve the simultaneous equations using a step-by-step approximation method to obtain the mechanical properties of the bearing.

[0075] Specific embodiments, such as Figures 1 to 7 As shown,

[0076] A method for calculating the mechanical properties of bearings considering rotor deformation, with the following modeling steps:

[0077] Step S1: Based on the rotor load and rotor structure, establish the rotor force-deformation coordination equation and calculate the external load borne by the bearing.

[0078] Step S2: Based on the external load borne by the bearing, establish the bearing deformation equation under load, taking into account the centrifugal force and gyroscopic force of the bearing.

[0079] Step S3: Simultaneously establish the rotor force-deformation coordination equation and the bearing load deformation equation, and solve the simultaneous equations using the idea of ​​stepwise approximation.

[0080] The above-mentioned method for calculating the mechanical properties of bearings considering rotor deformation, and the method for establishing the rotor force-deformation compatibility equation in step S1 are as follows:

[0081] Step S11: Assuming the rotor is subjected to an external radial load P1 and a moment load T1, the rotor deforms under the action of the external load, which means that the bearing, in addition to bearing axial and radial loads, will also bear a moment load. Therefore, the force balance equation of the rotor can be derived:

[0082] F1+F2-P1=0 (1)

[0083] F1l1-M1+T1-P1(l1-a)+M2=0 (2)

[0084] Where F1 and F2 are the axial loads borne by the bearings, M1 and M2 are the torque loads borne by the bearings, l1 is the distance between the two supporting bearings, and a is the distance from the point of application of the external load to the left supporting bearing.

[0085] Step S12: The bearing-rotor system described above is statically indeterminate, and the bending moment equations for each section need to be derived.

[0086] When 0≤x≤a

[0087]

[0088] In the formula, E is the elastic modulus and I is the moment of inertia of the axial cross section.

[0089] Step S13: At x = 0, the radial displacement δ of the shaft and bearing can be obtained by integrating equation (3) twice. r1 The rotation angle θ1 is given by the following formula.

[0090]

[0091] Step S14, similarly, for the section where a≤x≤l1,

[0092]

[0093] In step S15, at x = l1, by integrating equation (6) twice consecutively, the radial displacement of the shaft and bearing is δ. r2 The rotation angle is θ2, and the specific formula is as follows.

[0094]

[0095] In step S16, at x = a, there is only one rotation angle and radial displacement. Therefore, when x = a, equations (4) and (5) should be equal to equations (7) and (8) respectively. Solving these two simultaneous equations yields...

[0096]

[0097] Step S17: Substituting equations (9) and (10) into equations (1) and (2) yields F2 and M2.

[0098]

[0099] The above-mentioned method for calculating the mechanical properties of bearings considering rotor deformation, specifically the method for establishing the bearing deformation equation under load considering centrifugal force and gyroscopic force in step S2, is as follows:

[0100] Step S21: Assuming the outer ring of the bearing is fixed, when a force is applied to the bearing, the positions of the center of curvature of the inner ring groove and the center of the ball will change. After the bearing deforms, the distance between the center of curvature of the inner and outer ring grooves and the center of the ball is...

[0101] Δ ij =(f i -0.5)D w +δ ij (13)

[0102] Δ oj =(f o -0.5)D w +δ oj (14)

[0103] In the formula f i f o These represent the curvature coefficients of the inner and outer grooves, respectively; δ ij δ oj D represents the normal contact deformation of the inner and outer grooves, respectively; w It is the diameter of the steel ball.

[0104] Step S22, at any ball position, the distance between the trajectories of the inner and outer groove curvature centers is

[0105] A 1j =BDsinα 0 +δ a +R i θcosψ j (15)

[0106] A 2j =BDcosα 0 +δ r cosψ j (16)

[0107] Where BD is the distance between the centers of curvature of the inner and outer grooves, and α 0 δ is the initial contact angle of the bearing. a R represents the axial displacement of the bearing inner ring. i Let δ be the radius of the circle tracing the center curvature of the inner groove. r ψ represents the radial displacement of the bearing inner ring. j Let be the azimuth angle of the j-th ball in the inertial coordinate system;

[0108] Step S23: Using the Pythagorean theorem, obtain the compatibility equations for the displacement of the bearing ball and the raceway.

[0109] (A 1j -X 1j ) 2 +(A 2j -X 2j ) 2 -[(f i -0.5)D w +δ ij ] 2 =0 (17)

[0110]

[0111] Among them, X 1j ,X 2j The axial and radial distances between the center of the sphere and the center of curvature of the inner / outer groove.

[0112] Step S24 yields the equilibrium equation for the steel ball.

[0113]

[0114] Step S25 also requires establishing the equilibrium equations for the inner ring in order to obtain the displacement δ of the inner ring. a δ r and θ, respectively

[0115]

[0116]

[0117] The above method for calculating the mechanical properties of bearings considering rotor deformation, in step S3, employs a step-by-step approximation approach to solve the simultaneous equations as follows:

[0118] Step S31: Input the geometric, material, and operating parameters of the bearing and rotor;

[0119] Step S32: Treat the rotor as a rigid body, disregard rotor deformation, and calculate the initial value of the external load on the support bearing.

[0120] Step S33: Calculate the initial value of the bearing inner ring displacement without considering the bearing centrifugal force and gyro torque based on the initial value of the external load on the bearing obtained in step S32.

[0121] Step S34: Simultaneously establish the bearing load deformation equation and the rotor force-deformation coordination equation without considering the bearing centrifugal force and gyro torque, and correct the initial value of the bearing external load and the unique initial value of the inner ring.

[0122] Step S35: Based on the initial values ​​obtained in step S34, the Newton-Raphson method is used to solve the displacement compatibility equations and force balance equations of each ball in each bearing, and the position and deformation value of each ball in the bearing are obtained.

[0123] Step S36: Based on the positions and deformation values ​​of each ball in the bearing obtained in step S36, use the Newton-Raphson method to solve the force balance equation of the bearing inner ring and the rotor deformation equation. If the solution does not converge, correct the bearing displacement and bearing external load, and return to step S35; otherwise, output the calculation results.

[0124] Examples are given below:

[0125] For the appendix Figure 1 The analysis focuses on the two-end supported bearing-rotor system. The system bears a radial load of 4N, located between the two bearings (a = l1 / 2). Additionally, the bearings bear an axial preload of 7N. The analysis reveals the effects of different rotor lengths and hollowness on bearing reaction forces, bearing stiffness, internal load distribution, and roll ratio. It should be noted that with two-end support, the radial load application point is always between the two bearings; therefore, the reaction forces and internal load distribution of the two bearings are always the same, and the radial load on each bearing is consistently 2N. This invention uses the right bearing as an example for illustration.

[0126] Appendix Figure 5 The torque load borne by the bearing is presented for different rotor lengths and hollownesses. It can be seen that when rotor deformation is considered, the bearing experiences not only axial and radial loads but also a certain torque load. Furthermore, the longer the rotor and the greater the hollowness, the greater the torque load borne by the bearing. It is also noteworthy that when the rotor hollowness is below 80%, the impact of hollowness on the torque load borne by the bearing is very small, while when it exceeds 80%, the torque load increases dramatically.

[0127] Appendix Figure 6The effects of rotor length and hollowness on the bearing roll ratio are presented. It can be seen that when the rotor length is 40mm (with a torque load less than 3.33 N·mm), the roll ratio gradually decreases with increasing hollowness. However, when the rotor length is 100mm (with a torque load greater than 3.48 N·mm), the roll ratio gradually increases with increasing hollowness. At 60mm and 80mm, the roll ratio first decreases and then increases. For easier analysis of the relationship between the roll ratio and the torque load borne by the bearing, see the attached diagram. Figure 7 As shown, it can be clearly seen that when the torque load is less than 3.37 N·mm, the roll ratio decreases as the torque load increases, while when the torque load is greater than 3.37 N·mm, it gradually increases. Therefore, there exists a specific rotor length or hollowness that allows the bearing to bear a certain torque load and minimizes the bearing roll ratio.

[0128] The influence of a rotor with 90% hollowness on the internal load of the bearing is discussed. When the rotor length varies from 40mm to 100mm, the load distribution range inside the bearing gradually increases with the increase of rotor length, and the maximum load borne by the steel balls also increases. Furthermore, when the rotor length reaches 80mm, the load distribution gradually changes from a U-shaped distribution to a W-shaped distribution. In addition, comparing the load distribution without considering rotor deformation, it can be found that when the rotor length is 40mm and 60mm, the internal load range of the bearing is smaller than the load distribution without considering rotor flexibility, while when the rotor length is 80mm and 100mm, the load distribution is larger than the load distribution without considering rotor flexibility. (See attached diagram.) Figure 5 It can be seen that when considering the deformation of the rotor, the bearing will bear an additional torque load. The longer the rotor, the greater the additional torque load on the bearing. This indicates that as the torque load on the bearing gradually increases from zero, the internal load of the bearing first gradually decreases and then gradually increases. Therefore, it can be inferred that, similar to the roll ratio, there is a specific rotor length or hollowness that allows the bearing to bear a certain torque load and makes the internal load distribution of the bearing most uniform.

[0129] It should be noted that the terms "comprising" and "having" and any variations thereof in the specification, claims and accompanying drawings of this application are intended to cover non-exclusive inclusion. For example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to such process, method, product or device.

[0130] In this application, the terms "upper," "lower," "left," "right," "front," "rear," "top," "bottom," "inner," "outer," "middle," "vertical," "horizontal," "lateral," and "longitudinal" indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for the purpose of better describing this application and its embodiments, and are not intended to limit the indicated device, element, or component to having a specific orientation, or to be constructed and operated in a specific orientation.

[0131] Furthermore, in addition to indicating location or positional relationship, some of the aforementioned terms may also have other meanings. For example, the term "above" may also be used in some cases to indicate a certain dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0132] Furthermore, the terms "installation," "setup," "equipped with," "connection," "linking," and "socketing" should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral structure; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium, or an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of these terms in this application based on the specific circumstances.

[0133] This solution is not limited to the specific embodiments described above. Devices and structures not described in detail herein should be understood as being implemented in a manner common to the art. Any person skilled in the art can make many possible variations and modifications to this solution, or modify it into equivalent embodiments, without departing from the scope of this solution, using the methods and techniques disclosed above. This does not affect the substantive content of this solution. Therefore, any simple modifications, equivalent changes, and alterations made to the above embodiments based on the technical essence of this solution, without departing from its scope, still fall within the protection scope of this solution.

Claims

1. A method for calculating the mechanical properties of a bearing taking into account the deformation of the rotor, characterized in that: It comprises the following steps: Step S1, establishing a rotor force-deformation coordination equation according to rotor load and rotor structure data, and calculating the external load borne by the bearing; the method for establishing the rotor force-deformation coordination equation is as follows: Step S11, constructing a force balance equation of the rotor: F1+F2-P1=0 (1) F1l1-M1+T1-P1(l1-a)+M2=0 (2) Wherein, P1 is an external radial load assumed to be borne by the rotor, T1 is a torque load, the rotor produces deformation under the action of the external load, F1 and F2 are respectively axial loads borne by the bearings, M1 and M2 are respectively torque loads borne by the bearings; l1 is the distance between the two supporting bearings, and a is the distance from the action point of the external load to the left supporting bearing; Step S12, solving a bending moment equation of each section of the bearing-rotor system, When 0≤x≤a, Wherein, E is the elastic modulus, and I is the inertia moment of the shaft cross section; Step S13, at x = 0, the radial displacement δ of the shaft and bearing can be obtained by integrating formula (3) twice in succession r1 , the rotation angle θ1, and the specific formula is as follows, Step S14, similarly, for the section of a≤x≤l1, Step S15, at x = l1, the radial displacement of the shaft and bearing is δ r2 , the rotation angle is θ2, and the specific formula is as follows, Step S16, at x=a, only a rotation angle and a radial displacement exist, therefore, when x=a, the equation (4) and the equation (5) should be respectively equal to the equation (7) and the equation (8), and the two simultaneous equations can be solved to obtain Step S17, the equation (9) and the equation (10) are brought into the equation (1) and the equation (2) to obtain F2 and M2 Step S2, establishing a bearing load-deformation equation considering the centrifugal force and the gyroscopic force of the bearing according to the external load borne by the bearing; the specific process for establishing the bearing load-deformation equation considering the centrifugal force and the gyroscopic force of the bearing is as follows: Step S21, after the deformation of the bearing, the distance between the curvature center of the inner and outer ring raceways and the center of the ball is Δ ij = (f i -0.5)D w +δ ij (13) Δ oj = (f o -0.5)D w +δ oj (14) where f i , f o represent the curvature coefficients of the inner and outer raceway grooves, respectively; δ ij , δ oj represent the normal contact deformations of the inner and outer raceway grooves, respectively; D w is the diameter of the steel ball. Step S22, at any ball position, the distance between the trajectories of the curvature centers of the inner and outer raceways is A 1j = BD sin α 0 + δ a + R i θ cos ψ j (15) A 2j = BD cos α 0 + δ r cos ψ j (16) where BD is the distance between the curvature centers of the inner and outer ring grooves, a 0 is the initial contact angle of the bearing, δ a is the axial displacement of the inner ring of the bearing, R i is the radius of the trajectory circle of the curvature center of the inner ring groove, δ r is the radial displacement of the inner ring of the bearing, ψ j is the azimuth angle of the jth ball in the inertial coordinate system; Step S23, the displacement coordination equation of the bearing ball and the raceway is obtained by using the Pythagorean theorem (A 1j -X 1j ) 2 +(A 2j -X 2j ) 2 -[(f i -0.5)D w +δ ij ] 2 =0 (17) wherein X 1j is the axial, radial distance of the ball center from the center of curvature of the inner / outer race groove; 2j is the axial, radial distance of the ball center from the center of curvature of the inner / outer race groove; Step S24, obtaining the balance equation of the steel ball wherein Q ij is the contact load of the rolling element with the inner ring, Q oj is the contact load of the rolling element with the outer ring, λ ij and λ oj are the inner and outer ring gyroscopic moment distribution coefficients, M gj is the gyroscopic moment experienced by the rolling element, Step S25, the balance equation of the inner ring also needs to be established, in order to obtain the displacement δ a of the inner ring r and θ, respectively, are Step S3, solving the simultaneous equations by using the step-by-step approximation method to obtain the mechanical properties of the bearing; the mechanical properties of the bearing include the displacement, velocity, acceleration and load of each component.

2. The method of claim 1, wherein: The method for solving the simultaneous equations by using the step-by-step approximation method in step S3 is as follows: Step S31, inputting the geometric, material, working condition parameters of the bearing and the rotor; Step S32, taking the rotor as a rigid body without considering the deformation of the rotor, and calculating the initial value of the external load borne by the supporting bearing; Step S33, calculating the initial value of the inner ring displacement of the bearing without considering the centrifugal force and the gyroscopic moment of the bearing based on the initial value of the external load borne by the bearing obtained in step S32; Step S34, solving the bearing load-deformation equation without considering the centrifugal force and the gyroscopic moment and the rotor force-deformation coordination equation, and correcting the initial value of the external load borne by the bearing and the initial value of the inner ring; Step S35, solving the displacement coordination equation and the force balance equation of each ball of each bearing based on the initial value obtained in step S34, and obtaining the position and deformation value of each ball of the bearing; Step S36, based on the bearing ball positions and deformation values obtained in step S35, solving the force balance equation of the bearing inner ring and the rotor deformation equation, if the solution does not converge, correcting the bearing displacement and the bearing external load, returning to step S35; otherwise, outputting the calculation result.

3. A bearing mechanical property calculation system considering rotor deformation, characterized by: The processor applies the bearing mechanical property calculation method considering rotor deformation according to any one of claims 1-2 to obtain bearing mechanical property parameters.

4. A computer-readable storage medium, characterized in that: The computer readable storage medium stores computer readable instructions, and the computer readable instructions are executed by the processor to call all or part of the steps of the method according to any one of claims 1-2.

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