Fault dynamics analysis method, device, equipment and storage medium

Abstract

The application provides a fault dynamics analysis method, device, equipment and storage medium, and relates to the technical field of mechanical dynamics analysis. The method comprises the following steps: constructing a crack model based on the crack fault characteristics of a double-disc rotor system; the double-disc rotor system comprises a double-disc rotor and a rolling bearing, the rolling bearing comprises rolling elements, and the double-disc rotor system has a crack; constructing a bearing force model of the rolling bearing; constructing a rolling bearing-crack rotor dynamics model of the double-disc rotor system based on the crack model and the bearing force model; and performing fault dynamics analysis on the double-disc rotor system based on the rolling bearing-crack rotor dynamics model. In the foregoing manner, an effective and feasible fault dynamics analysis method is provided for the double-disc rotor system with rolling bearings and cracks, which is conducive to revealing the system motion state law of the double-disc rotor system with rolling bearings under crack fault, and guaranteeing the fault early warning and prevention and control requirements of the double-disc rotor system under actual working conditions.

Description

Technical Field

[0001] This invention relates to the field of mechanical dynamics analysis technology, and in particular to a fault dynamics analysis method, apparatus, equipment and storage medium. Background Technology

[0002] Rotor systems refer to all mechanical systems containing rotating components (i.e., rotors), such as motors, compressors, and turbines. Dynamic analysis of rotor systems is a core technology for the safe operation and maintenance of rotating machinery and the development of high-end equipment. It can be used to analyze typical faults such as system imbalance, crack propagation, and bearing failure, enabling fault identification, fault location, and system life prediction, and has significant industrial value.

[0003] A dual-disc rotor system is a specific type of rotor system, comprising two bearings and a dual-disc rotor. The dual-disc rotor consists of two discs and a shaft, with both bearings and discs fixed to the shaft and rotating as the shaft rotates. If a component in the dual-disc rotor system has a crack (i.e., a crack fault exists in the dual-disc rotor system), the system's motion will be affected. Accurate fault dynamics analysis of dual-disc rotor systems with cracks is a problem that urgently needs to be solved in the industry.

[0004] In some related technologies, sliding bearings are mostly used in dual-disc rotor systems, and the methods for fault dynamics analysis of dual-disc rotor systems with sliding bearings and cracks are relatively mature. However, sliding bearings rely on sliding friction between components for operation. When the friction coefficient between components is high, sliding bearings generate a lot of heat during operation, requiring a complex oil film lubrication system. The oil film in the oil film lubrication system is easily affected by the rotational speed and load of the dual-disc rotor system, and is prone to instability phenomena such as oil film oscillation. Moreover, sliding bearings have high energy consumption. Based on this, sliding bearings in some dual-disc rotor systems are gradually being replaced by rolling bearings. Compared with sliding bearings, rolling bearings have a higher degree of standardization, lower energy consumption, and better installation convenience and replaceability.

[0005] However, there is currently a lack of effective methods for fault dynamics analysis of dual-disc rotor systems with rolling bearings and cracks. It is difficult to reveal the system motion state law of dual-disc rotor systems with rolling bearings under crack faults, and it is difficult to meet the fault early warning and prevention requirements of dual-disc rotor systems under actual working conditions. Summary of the Invention

[0006] This invention provides a fault dynamics analysis method, apparatus, equipment, and storage medium to address the current lack of an effective method for fault dynamics analysis of double-disc rotor systems using rolling bearings and containing cracks, the difficulty in revealing the system motion state law of double-disc rotor systems using rolling bearings under crack faults, and the difficulty in meeting the fault early warning and prevention requirements of double-disc rotor systems under actual working conditions.

[0007] This invention provides a fault dynamics analysis method, comprising: constructing a crack model based on the crack fault characteristics of a dual-disc rotor system; the dual-disc rotor system includes a dual-disc rotor and rolling bearings, the rolling bearings include rolling elements, and cracks exist on the dual-disc rotor system; the crack model is a mathematical model characterizing the influence of cracks on the dual-disc rotor system; constructing a bearing force model for the rolling bearings; the bearing force model is a mathematical model characterizing the bearing force of the rolling elements; based on the crack model and the bearing force model, constructing a rolling bearing-cracked rotor dynamics model of the dual-disc rotor system; the rolling bearing-cracked rotor dynamics model is a dynamic equation describing the system motion state of the dual-disc rotor system; and performing fault dynamics analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model.

[0008] According to a fault dynamics analysis method provided by the present invention, a dual-disc rotor includes a first disk, a second disk, and a shaft. The first and second disks are fixed on the shaft. Crack fault characteristics include vortex angle, crack depth, and shaft radius. The crack model is constructed based on the following steps: determining the dimensionless crack depth of the dual-disc rotor system based on the crack depth and shaft radius; constructing a cosine model based on the dimensionless crack depth and vortex angle; the cosine model is a mathematical model characterizing the opening and closing of the crack; determining the stiffness variation of the shaft; the stiffness variation is caused by the crack; and constructing the crack model based on the cosine model and the stiffness variation.

[0009] According to a fault dynamics analysis method provided by the present invention, the rolling bearing further includes an outer ring and an inner ring, and a rolling element is disposed between the outer ring and the inner ring; the bearing force model is constructed based on the following steps: determining the deformation of the rolling element based on the angular position and radial clearance of the rolling element; the deformation is caused by the contact between the rolling element and the outer ring and the inner ring; constructing the bearing force model based on the Hertzian contact stiffness and the deformation of the rolling element; wherein, the bearing force model is used to characterize the bearing force of the rolling element in different directions.

[0010] According to a fault dynamics analysis method provided by the present invention, there are two rolling bearings, which are fixed at both ends of a rotating shaft. The rolling bearing-cracked rotor dynamics model is constructed based on the following steps: under the condition of shaft rotation, the first radial displacement information of the two rolling bearings, the second radial displacement information of the first disk, and the third radial displacement information of the second disk are determined; the eccentricity of the first disk and the second disk is determined; based on the first radial displacement information, the second radial displacement information, the third radial displacement information, the eccentricity, the crack model, and the bearing force model, the rolling bearing-cracked rotor dynamics model is constructed.

[0011] According to a fault dynamics analysis method provided by the present invention, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model. The method includes: performing crack fault analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a first fault dynamics analysis result; wherein, the first fault dynamics analysis result includes the influence of cracks on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0012] According to a fault dynamics analysis method provided by the present invention, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model. The method includes: performing eccentricity analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a second fault dynamics analysis result; wherein the second fault dynamics analysis result includes the influence of eccentricity on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0013] According to a fault dynamics analysis method provided by the present invention, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model. The method includes: performing radial clearance analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a third fault dynamics analysis result; wherein, the third fault dynamics analysis result includes the influence of radial clearance on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0014] This invention also provides a fault dynamics analysis device, comprising: a crack model construction module for constructing a crack model based on the crack fault characteristics of a dual-disc rotor system; the dual-disc rotor system includes a dual-disc rotor and rolling bearings, the rolling bearings include rolling elements, and cracks exist on the dual-disc rotor system; the crack model is a mathematical model characterizing the influence of cracks on the dual-disc rotor system; a bearing force model construction module for constructing a bearing force model of the rolling bearings; the bearing force model is a mathematical model characterizing the bearing force of the rolling elements; a dynamics model construction module for constructing a rolling bearing-cracked rotor dynamics model of the dual-disc rotor system based on the crack model and the bearing force model; the rolling bearing-cracked rotor dynamics model is a dynamic equation describing the system motion state of the dual-disc rotor system; and a fault dynamics analysis module for performing fault dynamics analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model.

[0015] The present invention also provides an electronic device, including a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor executes the computer program to implement any of the fault dynamics analysis methods described above.

[0016] The present invention also provides a non-transitory computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements any of the fault dynamics analysis methods described above.

[0017] The fault dynamics analysis method, apparatus, equipment, and storage medium provided by this invention utilize rolling bearings in a dual-disc rotor system. The rolling bearings include rolling elements, and cracks exist in the dual-disc rotor system. In the fault dynamics analysis of this cracked dual-disc rotor system, a crack model is first constructed based on the crack fault characteristics of the dual-disc rotor system. This crack model characterizes the impact of cracks on the dual-disc rotor system. Then, a bearing force model for the rolling bearings is constructed to characterize the bearing force of the rolling elements in the rolling bearings under crack fault conditions. Finally, based on the crack model and the bearing force model, the dual-disc rotor... The rolling bearing-cracked rotor dynamic model of the system provides the dynamic equations describing the system motion state of the dual-disc rotor system. Finally, the rolling bearing-cracked rotor dynamic model is used to conduct fault dynamics analysis on the dual-disc rotor system. This provides an effective and feasible fault dynamics analysis method for dual-disc rotor systems using rolling bearings and with cracks. It is beneficial to reveal the system motion state law of dual-disc rotor systems using rolling bearings under crack faults, and thus, based on the revealed system motion state law, to ensure the fault early warning and prevention requirements of dual-disc rotor systems under actual working conditions. Attached Figure Description

[0018] To more clearly illustrate the technical solutions in this 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 some embodiments of this invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0019] Figure 1 This is one of the flowcharts of the fault dynamics analysis method provided by the present invention.

[0020] Figure 2 This is the second flowchart of the fault dynamics analysis method provided by the present invention.

[0021] Figure 3 This is a schematic diagram of the structure of a dual-disc rotor system with rolling bearings and cracks provided by the present invention.

[0022] Figure 4 This is a cross-sectional schematic diagram of the crack provided by the present invention.

[0023] Figure 5 This is a cross-sectional schematic diagram of the rolling bearing provided by the present invention.

[0024] Figure 6 This is a bifurcation diagram of the crack-free dual-disc rotor system provided by the present invention.

[0025] Figure 7 This is the maximum Lyapunov index diagram for crack-free faults provided by the present invention.

[0026] Figure 8 This is a bifurcation diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0027] Figure 9 This is the maximum Lyapunov exponent diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0028] Figure 10 This is a bifurcation diagram of a dual-disc rotor system with a dimensionless crack depth of 0.2, provided by the present invention, which has a crack fault.

[0029] Figure 11 This is a bifurcation diagram of a dual-disc rotor system with a dimensionless crack depth of 0.8, provided by the present invention, which has a crack fault.

[0030] Figure 12 This is one of the bifurcation diagrams of a dual-disc rotor system with crack faults when using eccentricity as the bifurcation parameter, provided by the present invention.

[0031] Figure 13 This is the second bifurcation diagram of a dual-disc rotor system with crack faults when using eccentricity as the bifurcation parameter, provided by the present invention.

[0032] Figure 14 This is the third bifurcation diagram of a dual-disc rotor system with crack faults when using eccentricity as the bifurcation parameter, provided by the present invention.

[0033] Figure 15 This is one of the time-domain waveform diagrams of a dual-disc rotor system with crack faults provided by the present invention.

[0034] Figure 16 This is one of the shaft center trajectory diagrams of a dual-disc rotor system with crack faults provided by the present invention.

[0035] Figure 17 This is one of the spectrum diagrams of a dual-disc rotor system with crack faults provided by the present invention.

[0036] Figure 18 This is one of the Poincaré cross-sectional views of a dual-disc rotor system with crack faults provided by the present invention.

[0037] Figure 19 This is the second time-domain waveform diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0038] Figure 20 This is the second shaft center trajectory diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0039] Figure 21 This is the second spectrum diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0040] Figure 22 This is the second Poincaré cross-sectional view of a dual-disc rotor system with crack faults provided by the present invention.

[0041] Figure 23 This is one of the bifurcation diagrams of a dual-disc rotor system with crack faults when radial clearance is used as the bifurcation parameter, as provided by the present invention.

[0042] Figure 24 This is the second bifurcation diagram of a dual-disc rotor system with crack faults when radial clearance is used as the bifurcation parameter, provided by the present invention.

[0043] Figure 25 This is the third time-domain waveform diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0044] Figure 26 This is the third of the shaft center trajectory diagrams provided by the present invention for a dual-disc rotor system with crack faults.

[0045] Figure 27 This is the third spectrum diagram of a dual-disc rotor system with crack faults provided by the present invention.

[0046] Figure 28 This is the third Poincaré cross-sectional view of a dual-disc rotor system with crack faults provided by the present invention.

[0047] Figure 29 This is a schematic diagram of the fault dynamics analysis device provided by the present invention.

[0048] Figure 30 This is a schematic diagram of the structure of the electronic device provided by the present invention. Detailed Implementation

[0049] To make the objectives, technical solutions, and advantages of this invention clearer, the technical solutions of this invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some, not all, of the embodiments of this invention. All other embodiments obtained by those skilled in the art based on the embodiments of this invention without creative effort are within the scope of protection of this invention.

[0050] Please see Figure 1 and Figure 2 , Figure 1 This is one of the flowcharts of the fault dynamics analysis method provided by the present invention. Figure 2 This is the second flowchart of the fault dynamics analysis method provided by the present invention.

[0051] like Figure 1 As shown, in this embodiment, the fault dynamics analysis method includes steps S110 to S120, and the specific steps are as follows: S110: Based on the crack fault characteristics of the dual-disc rotor system, a crack model is constructed.

[0052] The dual-disc rotor system includes dual-disc rotors and rolling bearings. The rolling bearings include rolling elements. Cracks exist in the dual-disc rotor system. The crack model is a mathematical model that characterizes the influence of cracks on the dual-disc rotor system.

[0053] Please see Figure 3 , Figure 3 This is a schematic diagram of the structure of a dual-disc rotor system with rolling bearings and cracks provided by the present invention.

[0054] like Figure 3 As shown, the dual-disc rotor system of this embodiment includes a dual-disc rotor and two rolling bearings. The dual-disc rotor includes a first disc ( Figure 3 The green rectangle on the left side of the middle), the second disk ( Figure 3 The green rectangle on the right) and the pivot ( Figure 3 The blue rectangle in the diagram represents two rolling bearings, designated as the first rolling bearing (the bearing on the left side of the shaft) and the second rolling bearing (the bearing on the right side of the shaft). Each rolling bearing comprises multiple rolling elements. Figure 3 The yellow circle in the image shows the first rolling bearing, the first disk, the second disk, and the second rolling bearing, which are sequentially fixed on the rotating shaft. When the rotating shaft rotates, the first rolling bearing, the first disk, the second disk, and the second rolling bearing can all rotate with the rotating shaft. In addition, there is a crack in the dual-disc rotor system.

[0055] in, The geometric center of the first rolling bearing is [the location of the bearing]. Let be the geometric center of the first disk. Let be the geometric center of the second disk. This is the geometric center of the second rolling bearing; The concentrated mass of the first rolling bearing, Let be the concentrated mass of the first disk. Let be the concentrated mass of the second disk. This refers to the concentrated mass of the second rolling bearing.

[0056] Specifically, such as Figure 2 As shown, for a dual-disc rotor system with rolling bearings and cracks, a crack model can be constructed based on the crack failure characteristics of the dual-disc rotor system.

[0057] Among them, the crack model is a mathematical model that characterizes the effect of cracks on the dual-disc rotor system. This crack model can be a simulation calculation model.

[0058] S120: Construct the bearing force model for the rolling bearing.

[0059] The bearing force model is a mathematical model that characterizes the bearing force of rolling elements.

[0060] Specifically, for each rolling bearing, the rolling bearing further includes an outer ring and an inner ring, and a plurality of rolling elements of the rolling bearing are disposed between the outer ring and the inner ring.

[0061] According to Hertz's elastic contact theory, the elastic contact between each rolling element in a rolling bearing and the outer and inner rings causes deformation of the rolling element, resulting in a corresponding nonlinear bearing deformation load.

[0062] For each rolling bearing, the bearing force of each rolling element in different directions can be calculated according to Hertz's elastic contact theory, and the bearing force model of the rolling bearing can be constructed based on the bearing force of each rolling element in different directions.

[0063] Among them, the bearing force model is a mathematical model that characterizes the bearing force of the rolling elements in a rolling bearing under crack failure.

[0064] S130: Based on the crack model and bearing force model, a rolling bearing-cracked rotor dynamic model of a dual-disc rotor system is constructed.

[0065] The rolling bearing-cracked rotor dynamic model is a dynamic equation describing the system motion state of a dual-disc rotor system.

[0066] S140: Based on the rolling bearing-cracked rotor dynamics model, a fault dynamics analysis of a dual-disc rotor system is performed.

[0067] The fault dynamics analysis method provided in this embodiment employs rolling bearings in a dual-disc rotor system. The rolling bearings include rolling elements, and cracks exist in the dual-disc rotor system. In the fault dynamics analysis of this system, a crack model is first constructed based on the crack fault characteristics of the dual-disc rotor system. This model characterizes the impact of cracks on the dual-disc rotor system. Next, a bearing force model for the rolling bearings is constructed to characterize the bearing force of the rolling elements under crack fault conditions. Then, based on the crack model and the bearing force model, a rolling bearing-cracked rotor dynamics model is constructed. This model represents the dynamic equations describing the system motion state of the dual-disc rotor system. Finally, the rolling bearing-cracked rotor dynamics model is used to perform fault dynamics analysis on the dual-disc rotor system. This provides an effective and feasible fault dynamics analysis method for dual-disc rotor systems supported by rolling bearings and exhibiting cracks. It helps to reveal the system motion state laws of dual-disc rotor systems supported by rolling bearings under crack fault conditions, thereby facilitating fault early warning and prevention requirements of the dual-disc rotor system under actual operating conditions based on the revealed system motion state laws.

[0068] In some embodiments, the dual-disc rotor includes a first disk, a second disk, and a shaft. The first and second disks are fixed on the shaft. The crack fault characteristics include vortex angle, crack depth, and shaft radius. The crack model is constructed based on the following steps: determining the dimensionless crack depth of the dual-disc rotor system based on the crack depth and shaft radius; constructing a cosine model based on the dimensionless crack depth and vortex angle; the cosine model is a mathematical model characterizing the opening and closing of the crack; determining the stiffness variation of the shaft; the stiffness variation is caused by the crack; and constructing the crack model based on the cosine model and the stiffness variation.

[0069] Please see Figure 4 , Figure 4 This is a cross-sectional schematic diagram of the crack provided by the present invention.

[0070] Specifically, such as Figure 4 As shown, two different coordinate systems are constructed for the dual-disc rotor system, namely the fixed coordinate system (i.e., ... Figure 4 In coordinate system) and rotating coordinate system (i.e.) Figure 4 In (Coordinate system), assuming the crack appears on the axis of rotation, then the origin of the rotating coordinate system is the center of the axis of rotation. Rotating coordinate system The axis is aligned with the crack propagation direction, and the coordinate system is rotated. The axis is perpendicular to the direction of crack propagation. Let be the eccentricity of the first and second disks.

[0071] Among them, the crack failure characteristics include the angle between the crack direction and the eccentricity. vortex difference angle , the whirl angle of the rotating shaft Half of the crack angle Crack depth The radius of the rotating shaft .

[0072] like Figure 4 As shown, eddy angle , indicating the eddy angle It can be obtained from the center of the rotating shaft Coordinates in a fixed coordinate system ( x, y ) Calculated; intermediate variables used in subsequent calculations , This indicates the rotational angular velocity of the shaft. Indicates time, This indicates the initial phase angle of the rotating shaft.

[0073] In this embodiment, it is assumed that the cracks on the dual-disc rotor system are open-closed cracks whose degree of opening and closing varies periodically with the resultant force of unbalanced force and gravity. Considering that different crack depths have different effects on the shaft stiffness of the dual-disc rotor system, this embodiment uses an improved cosine model to characterize the opening and closing of the cracks.

[0074] Specifically, first, based on the crack depth and axis radius Calculate the dimensionless crack depth of the dual-disc rotor system. .

[0075] Among them, dimensionless crack depth The expression is as follows: .

[0076] Furthermore, based on the dimensionless crack depth and vortex difference angle An improved cosine model was constructed.

[0077] Among them, the improved cosine model The expression is as follows: ; in, Indicates the vortex difference angle The cosine of .

[0078] Furthermore, since cracks cause changes in the stiffness of the shaft, a crack model can be constructed based on the stiffness change of the shaft and the cosine model. .

[0079] Among them, crack model The expression is as follows: ; Among them, crack model It is essentially the stiffness matrix expression of the shaft.

[0080] Among them, the crack transformation model Satisfy the following formula: ; in, This indicates that the shaft is in the direction when there are no cracks. The stiffness of the shaft, for example Indicates the shaft is at coordinate system shaft and Shaft stiffness (i.e., shaft stiffness at) coordinate system shaft and (coupling components on the axis) Indicates the shaft is at coordinate system Shaft stiffness, Indicates the shaft is at coordinate system Shaft stiffness; This represents the change in stiffness of the shaft in different directions caused by the crack, for example... This indicates that the shaft caused by the crack is in coordinate system Changes on the axis This indicates that the shaft caused by the crack is in axis The change in the quantity.

[0081] In some embodiments, the rolling bearing further includes an outer ring and an inner ring, with rolling elements disposed between the outer ring and the inner ring; the bearing force model is constructed based on the following steps: determining the deformation of the rolling elements based on the angular position and radial clearance of the rolling elements; the deformation is caused by the contact between the rolling elements and the outer and inner rings; and constructing the bearing force model based on the Hertzian contact stiffness and the deformation of the rolling elements; wherein the bearing force model is used to characterize the bearing force of the rolling elements in different directions.

[0082] Please see Figure 5 , Figure 5 This is a cross-sectional schematic diagram of the rolling bearing provided by the present invention.

[0083] like Figure 5 As shown, rolling bearings are one of the core components of mechanical equipment, and are the key carriers for transmitting motion and bearing loads in rotating machinery. They consist of an outer ring, an inner ring, and multiple rolling elements. Figure 5 (A small circle in the middle), with multiple rolling elements arranged between the outer ring and the inner ring.

[0084] In this embodiment, the deformation of the rolling element can be determined based on its angular position and radial clearance. Specifically, assuming the linear velocity at the contact point between the rolling element and the outer ring is... The linear velocity at the contact point between the rolling element and the inner ring is The rotational angular velocity of the outer ring is The rotational angular velocity of the inner ring is The radius of the outer ring is The radius of the inner ring is Then the following equation is satisfied: Because the inner ring of a rolling bearing is directly connected to the shaft, the rotational angular velocity of the inner ring is... Equal to the rotational angular velocity of the shaft ,Right now Then the rotational angular velocity of the bearing cage can be expressed as: ; in, The radius of the bearing cage.

[0085] For any rolling bearing, suppose the first... The angular position of each rolling element is The number of rolling elements in this rolling bearing is The initial angular position of the bearing cage is Then the first one in the rolling bearing angular position of each rolling element The expression is as follows: .

[0086] According to Hertz's elastic contact theory, the elastic contact between each rolling element and the outer and inner rings in a rolling bearing causes deformation of the rolling element, resulting in a corresponding nonlinear bearing deformation load. The expression is as follows: ; in, Hertz contact stiffness; This refers to the deformation generated when all rolling elements come into contact with the outer and inner rings.

[0087] For any rolling bearing, suppose the first... The deformation caused by the contact between the rolling element and the outer and inner rings is: Radial clearance is Then the first The deformation caused by the contact between the rolling element and the outer and inner rings is: The expression is as follows: ; in,( , (inner ring) Coordinates of the coordinate system; , ) is the outer ring in Coordinates in a coordinate system.

[0088] According to the nonlinear Hertzian contact theory, in actual working conditions, the deformation of the rolling element will not be less than zero. Only when the deformation of the rolling element is greater than zero can there be a force between it and the outer and inner rings. Therefore, the Heaviside function can be introduced.

[0089] The heaviside function, also known as the unit step function, is a special piecewise function. The expression for the heaviside function is as follows: in, This represents the Heaviside function.

[0090] Furthermore, for the first in each rolling bearing Each rolling element can be selected based on Hertzian contact stiffness. and the deformation of the rolling element Calculate the first The bearing forces of the rolling elements in different directions, and according to the first... To construct a bearing force model for a rolling bearing, considering the bearing forces acting on each rolling element in different directions.

[0091] The expression for the bearing force model of a rolling bearing is as follows: Among them, the The bearing forces on a rolling element in different directions mainly include the rolling element's bearing capacity. Bearing force on the shaft and the rolling element in Bearing force on the shaft .

[0092] In some embodiments, there are two rolling bearings, which are fixed at both ends of the shaft. The rolling bearing-crack rotor dynamics model is constructed based on the following steps: when the shaft rotates, determine the first radial displacement information of the two rolling bearings, the second radial displacement information of the first disk, and the third radial displacement information of the second disk; determine the eccentricity of the first disk and the second disk; and construct the rolling bearing-crack rotor dynamics model based on the first radial displacement information, the second radial displacement information, the third radial displacement information, the eccentricity, the crack model, and the bearing force model.

[0093] Specifically, assume that the structural damping of the first rolling bearing is The structural damping of the first disk is The structural damping of the second disk is The structural damping of the second rolling bearing is With the shaft rotating, determine the first radial displacement information of the two rolling bearings, the second radial displacement information of the first disk, and the third radial displacement information of the second disk.

[0094] like Figure 3 As shown, for the first rolling bearing, with the geometric center of the first rolling bearing... Establish with the origin as the starting point. In a coordinate system, with the shaft rotating, the first radial displacement information of the first rolling bearing is ( , ), indicating that the first rolling bearing is in Radial displacement in the coordinate system.

[0095] Similarly, for the first disk, with the geometric center of the first disk... Establish with the origin as the starting point. In a coordinate system, with the axis of rotation rotating, the second radial displacement information of the first disk is ( , ), indicating that the first disk is in Radial displacement in the coordinate system.

[0096] Similarly, for the second disk, with the geometric center of the second disk... Establish with the origin as the starting point. In a coordinate system, with the axis of rotation rotating, the third radial displacement information of the second disk is ( , ), indicating that the second disk is in Radial displacement in the coordinate system.

[0097] Similarly, for the second rolling bearing, with the geometric center of the second rolling bearing... Establish with the origin as the starting point. In a coordinate system, with the shaft rotating, the first radial displacement information of the second rolling bearing is ( , ), indicating that the second rolling bearing is in Radial displacement in the coordinate system.

[0098] Furthermore, assuming Let be the eccentricity between the first and second disks. This indicates the first time when the dual-disc rotor system is crack-free. Based on the rotor stiffness, and neglecting the torsional vibration and gyroscopic torque of the dual-disc rotor system, a rolling bearing-cracked rotor dynamic model can be constructed using the first radial displacement information, the second radial displacement information, the third radial displacement information, the eccentricity, the crack model, and the bearing force model.

[0099] Specifically, the expression for the rolling bearing-cracked rotor dynamics model is as follows: ; ; ; ; ; ; ; .

[0100] Substituting the stiffness matrix into the above equations, we can perform dimensionless transformation on the equations, letting... , , , , , , , , , , , , , The simplified rolling bearing-cracked rotor dynamics model is obtained by using the above parameters. The simplified model is expressed as follows: ; ; ; ; ; ; ; .

[0101] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing a crack fault analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a first fault dynamics analysis result; wherein, the first fault dynamics analysis result includes the influence of cracks on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0102] By introducing crack and bearing force models into the modeling of the dual-disc rotor system, a rolling bearing-cracked rotor dynamic model is obtained. By solving the dynamic equations of the rolling bearing-cracked rotor dynamic model, a systematic analysis of the dynamic response of the dual-disc rotor system can be achieved, providing a theoretical basis for the identification of the dynamic characteristics and fault detection of the dual-disc rotor system.

[0103] Optionally, the dimensionless crack depth can be used. With a step size of 0.5 and 2π / 100, the fourth-order Runge-Kutta method is used to solve the dynamic equations of the rolling bearing-cracked rotor dynamic model to avoid interference from transient response to the analysis. At the same time, the calculation results after 100 cycles are used for simulation to obtain the bifurcation diagram, time-domain waveform diagram, shaft center trajectory diagram, spectrum diagram and Poincaré section diagram of the dual-disc rotor system, which can be used for nonlinear dynamic behavior analysis of the dual-disc rotor system.

[0104] Specifically, based on the rolling bearing-cracked rotor dynamics model, crack fault analysis can be performed on the dual-disc rotor system to explore the role of crack faults in the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system, and generate the first fault dynamics analysis results. The first fault dynamics analysis results include the influence of cracks on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0105] To aid understanding, some analysis results are provided here. Please refer to... Figures 6 to 11 , Figure 6 This is a bifurcation diagram of the crack-free dual-disc rotor system provided by the present invention. Figure 7 This is the maximum Lyapunov index diagram for crack-free failures provided by the present invention. Figure 8 This is a bifurcation diagram of a dual-disc rotor system with crack faults provided by the present invention. Figure 9 This invention provides a maximum Lyapunov exponent diagram for a dual-disc rotor system with cracked defects. Figure 10 This is a bifurcation diagram of a dual-disc rotor system with a dimensionless crack depth of 0.2 mm, as provided by the present invention. Figure 11 This is a bifurcation diagram of a dual-disc rotor system with a dimensionless crack depth of 0.8, provided by the present invention, which has a crack fault.

[0106] Assuming rotational speed is used as the bifurcation parameter, Figure 6 and Figure 7 The bifurcation diagram and the maximum Lyapunov exponent diagram of a crack-free dual-disc rotor system are presented respectively. Figure 8 and Figure 9 The bifurcation diagram and the maximum Lyapunov exponent diagram of a two-disc rotor system with crack faults are presented respectively: (e.g.) Figure 6 As shown, in the low-speed range, the above dynamic equations have only one set of periodic solutions. The dual-disc rotor system performs single-cycle motion across a wide speed range. When the speed increases to 870 rad / s, the motion state of the dual-disc rotor system changes from single-cycle motion to two-cycle motion. As the rotor speed continues to increase, the dual-disc rotor system enters motion P1 through inverted bifurcation; as... Figure 7 As shown, when the speed increases to 1550 rad / s, the maximum Lyapunov exponent curve of the dual-disc rotor system is almost in line with the value of 0, with no significant positive or negative deviation, indicating that the motion state of the dual-disc rotor system is quasi-periodic motion and can maintain stability within a certain speed range. Figure 8 This reflects that when a dual-disc rotor system has a crack, although both systems exhibit single-cycle motion in the low-speed range, the amplitude of the cracked dual-disc rotor system is larger. The bifurcation of the cracked dual-disc rotor system occurs at a speed of 925 rad / s, while the bifurcation of the crack-free dual-disc rotor system occurs at higher speeds. Combined with... Figure 9 Further verification shows that when the rotational speed increases to 1415 rad / s, the dual-disc rotor system with crack faults is already in a quasi-periodic motion state, and the quasi-periodic motion appears earlier. Moreover, when the rotational speed is between 1500 rad / s and 1565 rad / s, the dynamic behavior of the dual-disc rotor system with crack faults is briefly in P3 motion, and the dynamic behavior is more complex.

[0107] It should be noted that crack depth is a core parameter affecting the dynamic characteristics and operational safety of a dual-disc rotor system. Increased crack depth directly weakens the rotor's matrix strength, leading to stiffness asymmetry and nonlinear vibration. Therefore, accurately understanding the impact of crack depth on dual-disc rotor systems can provide theoretical support for early warning of crack initiation and propagation, prediction of remaining service life, and optimization of maintenance strategies, and has significant engineering value for ensuring the safe and reliable operation of rotating machinery. Figure 10 and Figure 11 The dimensionless crack depths are shown separately. Bifurcation diagram of a dual-disc rotor system exhibiting crack faults at values ​​of 0.2 and 0.8: (from...) Figure 10 and Figure 11 It can be seen that when the dimensionless crack depth At a speed of 0.2, the bifurcation phenomenon of the dual-disc rotor system first appears below 895 rad / s. This critical speed is not only earlier than the first bifurcation speed of the dual-disc rotor system without crack faults, but also later than the dimensionless crack depth. The initial bifurcation speed of a dual-disc rotor system with a crack fault at 0.5 rad / s; when the rotor speed increases to 1505 rad / s, the dual-disc rotor system evolves from single-cycle motion to quasi-cycle motion. This critical speed occurs earlier than in a dual-disc rotor system without a crack fault, and compared to the dimensionless crack depth... The dual-disc rotor system exhibits a delay when the crack depth is 0.5; when the dimensionless crack depth... When the speed is increased to 0.8, the nonlinear dynamic behavior of the dual-disc rotor system becomes more complex. When the rotor speed reaches 970 rad / s, the dual-disc rotor system bifurcates for the first time, which is significantly delayed compared to the condition with shallower crack depth. After a brief P2 motion, if the speed is continuously increased, the quasi-periodic motion and single-period motion will alternate.

[0108] Therefore, it can be seen that crack failure will delay the bifurcation start speed of the dual-disc rotor system and advance the speed at which the quasi-periodic motion occurs. Moreover, the greater the dimensionless crack depth, the greater the delay in bifurcation of the dual-disc rotor system, and the further the speed at which the quasi-periodic motion occurs.

[0109] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing an eccentricity analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a second fault dynamics analysis result; wherein the second fault dynamics analysis result includes the influence of eccentricity on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0110] Eccentricity is a core dynamic parameter of a dual-disc rotor system, easily affecting its stability boundary. Excessive eccentricity can lead to resonance impact at the critical speed of the dual-disc rotor system, and may even induce instability, alter bearing load distribution, and accelerate fatigue damage to the shaft and bearings. Therefore, eccentricity is not only a core objective for dynamic balance in system design, but also a precision acceptance indicator for system manufacturing and installation, and is crucial for ensuring the safe and reliable operation of the rotor.

[0111] Specifically, based on the rolling bearing-cracked rotor dynamics model, eccentricity analysis can be performed on the dual-disc rotor system to explore the role of eccentricity in the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system, generating a second fault dynamics analysis result. The second fault dynamics analysis result includes the influence of eccentricity on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0112] To aid understanding, some analysis results are provided here. Please refer to... Figures 12 to 22 , Figure 12 This is one of the bifurcation diagrams provided by the present invention for a dual-disc rotor system with crack faults when eccentricity is used as the bifurcation parameter. Figure 13 This is the second bifurcation diagram of a dual-disc rotor system with cracking faults when using eccentricity as the bifurcation parameter, provided by this invention. Figure 14 This is the third bifurcation diagram of a dual-disc rotor system with crack faults when using eccentricity as the bifurcation parameter, provided by this invention. Figure 15 This is one of the time-domain waveform diagrams of a dual-disc rotor system with crack faults provided by the present invention. Figure 16 This is one of the shaft center trajectory diagrams of a dual-disc rotor system with crack faults provided by the present invention. Figure 17 This is one of the spectrum diagrams of a dual-disc rotor system with crack faults provided by the present invention. Figure 18 This is one of the Poincaré cross-sectional views of a dual-disc rotor system with crack faults provided by the present invention. Figure 19 This is the second time-domain waveform diagram of a dual-disc rotor system with crack faults provided by this invention. Figure 20 This is the second shaft center trajectory diagram of a dual-disc rotor system with crack faults provided by the present invention. Figure 21 This is the second spectrum diagram of a dual-disc rotor system with crack faults provided by the present invention. Figure 22 This is the second Poincaré cross-sectional view of a dual-disc rotor system with crack faults provided by the present invention.

[0113] Assuming eccentricity is used as the bifurcation parameter, Figure 12 , Figure 13 and Figure 14The bifurcation characteristic curves of a dual-disc rotor system with crack faults at speeds of 990 rad / s, 1550 rad / s, and 1800 rad / s are presented respectively.

[0114] Figure 15 , Figure 16 , Figure 17 and Figure 18 The rotational speed was maintained at 990 rad / s, and the eccentricity increased to... The time-domain waveform, shaft center trajectory, spectrum, and Poincaré cross section of a dual-disc rotor system with a crack fault are shown. In this scenario, the above dynamic equations have two independent periodic solutions. Figure 17 A distinct half-harmonic component can be observed in it, and Figure 18 The corresponding Poincaré section also shows two completely independent points, which together confirm that the system is in motion state P2.

[0115] When the eccentricity exceeds At that time, the dual-disc rotor system with the crack fault was in a stable single-cycle motion state. Under the condition of maintaining a rotational speed of 1550 rad / s, Figure 19 , Figure 20 , Figure 21 and Figure 22 The eccentricity E of the dual-disc rotor system with crack faults is presented separately. , , , and The time-domain waveform, axis trajectory, spectrum, and Poincaré section. Figure 21 Spectral analysis shows that the larger the eccentricity, the larger the first octave amplitude of the system. When the eccentricity is at a low level, the dynamic behavior of the system exhibits typical single-cycle motion. As the eccentricity continues to increase, the system exhibits more complex nonlinear characteristics. Figure 20 and Figure 22 As shown, when the eccentricity is arrive interval and arrive When the interval is within the range, the eccentricity is taken as For example, the system's axis trajectory exhibits a typical wreath-like shape, and the corresponding Poincaré cross-section is circular, fully demonstrating that the system is in a quasi-periodic motion state. When the eccentricity is between and Between these points, the system's axis trajectory exhibits a double-loop structure, with three discrete points on the Poincaré section, and the system's nonlinear behavior manifests as P3 motion. When the eccentricity increases to... Afterward, the system enters a stable single-cycle motion range, and this motion state remains unchanged over a wide range as the eccentricity continues to increase.

[0116] like Figure 14 As shown, under the condition that the rotational speed is maintained at 1800 rad / s, the eccentricity is at arrive When the system is within the specified range, its motion state is quasi-periodic; under other operating conditions, the system exhibits stable single-periodic motion.

[0117] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing radial clearance analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a third fault dynamics analysis result; wherein, the third fault dynamics analysis result includes the influence of radial clearance on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0118] Radial clearance is the inherent radial clearance between the inner ring, outer ring, and rolling elements of a rolling bearing. It is a core parameter that directly constrains rotor motion and affects support characteristics. The presence of radial clearance provides the necessary space for the formation of a lubricating oil film. In addition, radial clearance can reduce mechanical wear and heat generation, buffer impact vibrations and nonlinear responses caused by cracks, and is crucial to the operational stability, fault evolution, and diagnostic accuracy of dual-disc rotor systems.

[0119] Specifically, based on the rolling bearing-cracked rotor dynamics model, radial clearance analysis can be performed on the dual-disc rotor system to explore the role of radial clearance in the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system, generating a third fault dynamics analysis result. The third fault dynamics analysis result includes the influence of radial clearance on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0120] To aid understanding, some analysis results are provided here. Please refer to... Figures 23 to 28 , Figure 23 This is one of the bifurcation diagrams provided by the present invention for a dual-disc rotor system with crack faults when radial clearance is used as the bifurcation parameter. Figure 24 This is the second bifurcation diagram of a dual-disc rotor system with crack faults when radial clearance is used as the bifurcation parameter, provided by this invention. Figure 25 This is the third time-domain waveform diagram of a dual-disc rotor system with crack faults provided by this invention. Figure 26 This is the third of the shaft center trajectory diagrams provided by this invention for a dual-disc rotor system with crack faults. Figure 27 This is the third spectrum diagram of a dual-disc rotor system with crack faults provided by this invention. Figure 28This is the third Poincaré cross-sectional view of a dual-disc rotor system with crack faults provided by the present invention.

[0121] Assuming radial clearance is used as the bifurcation parameter, Figure 23 and Figure 24 The bifurcation characteristic curves of a dual-disc rotor system with crack faults at operating speeds of 990 rad / s and 1550 rad / s, respectively, and enlarged views of these bifurcation characteristic curves are shown: Figure 23 As shown, when the rotational speed is maintained at 990 rad / s, within a certain range, the nonlinear behavior of the system becomes more complex with the increase of radial clearance. When the radial clearance is small, the dual-disc rotor system maintains a single-cycle motion state; when the radial clearance increases to a certain value... When the radial clearance exceeds a certain value, the system's motion state evolves into a two-period motion. At this point, the above dynamic equations have three stable periodic solutions, and the system's motion is characterized by P3 motion. When the radial clearance exceeds... At this point, the nonlinear dynamics of the system evolves into quasi-periodic motion; when the radial clearance continues to increase, the dynamics of the system reverts to single-periodic motion. Figure 24 As shown, when the rotational speed reaches 1550 rad / s, the dynamic response characteristics of the system are similar to those at a rotational speed of 990 rad / s.

[0122] Figure 25 , Figure 26 , Figure 27 and Figure 28 The radial clearance is shown separately. , , , and The time-domain waveform, shaft center trajectory, spectrum, and Poincaré cross section of a dual-disc rotor system with crack faults are obtained. Figures 25 to 28 The results show that, at a radial clearance of , , , and Under these conditions, the corresponding motion states of the system are single-period motion, three-period motion, quasi-period motion, four-period motion, and single-period motion, respectively. In summary, with the change of radial clearance, the dynamic behavior of the system progresses from simple to complex and then back to simple.

[0123] The fault dynamics analysis method provided in this embodiment uses rolling bearings instead of sliding bearings as the support for a dual-disc rotor system and constructs a multi-parameter coupled rolling bearing-cracked rotor dynamics model. This breaks the limitation of traditional dynamic models that only consider the single parameter of crack fault. In the construction of the rolling bearing-cracked rotor dynamics model, the combined effects of multiple parameters (such as eccentricity, radial clearance, and deformation of rolling elements) on the system's motion state are referenced, enabling the model to more accurately describe the system's motion state. This provides theoretical support for fault identification and condition monitoring of this type of rotor system and fills the gap in existing models in multi-factor correlation analysis.

[0124] This invention also provides a fault dynamics analysis device. Please refer to [link / reference]. Figure 29 , Figure 29 This is a schematic diagram of the fault dynamics analysis device provided by the present invention. In this embodiment, the fault dynamics analysis device includes a crack model construction module 2910, a bearing force model construction module 2920, a dynamics model construction module 2930, and a fault dynamics analysis module 2940.

[0125] Crack model construction module 2910 is used to construct crack models based on crack fault characteristics of a dual-disc rotor system.

[0126] The dual-disc rotor system includes dual-disc rotors and rolling bearings. The rolling bearings include rolling elements. Cracks exist in the dual-disc rotor system. The crack model is a mathematical model that characterizes the influence of cracks on the dual-disc rotor system.

[0127] The bearing force model building module 2920 is used to build bearing force models for rolling bearings.

[0128] The bearing force model is a mathematical model that characterizes the bearing force of rolling elements.

[0129] The dynamic model building module 2930 is used to construct a rolling bearing-cracked rotor dynamic model of a dual-disc rotor system based on the crack model and the bearing force model.

[0130] The rolling bearing-cracked rotor dynamic model is a dynamic equation describing the system motion state of a dual-disc rotor system.

[0131] The Fault Dynamics Analysis Module 2940 is used to perform fault dynamics analysis on a dual-disc rotor system based on a rolling bearing-cracked rotor dynamics model.

[0132] In some embodiments, the dual-disc rotor includes a first disk, a second disk, and a shaft. The first and second disks are fixed on the shaft. The crack fault characteristics include vortex angle, crack depth, and shaft radius. The crack model is constructed based on the following steps: determining the dimensionless crack depth of the dual-disc rotor system based on the crack depth and shaft radius; constructing a cosine model based on the dimensionless crack depth and vortex angle; the cosine model is a mathematical model characterizing the opening and closing of the crack; determining the stiffness variation of the shaft; the stiffness variation is caused by the crack; and constructing the crack model based on the cosine model and the stiffness variation.

[0133] In some embodiments, the rolling bearing further includes an outer ring and an inner ring, with rolling elements disposed between the outer ring and the inner ring; the bearing force model is constructed based on the following steps: determining the deformation of the rolling elements based on the angular position and radial clearance of the rolling elements; the deformation is caused by the contact between the rolling elements and the outer and inner rings; and constructing the bearing force model based on the Hertzian contact stiffness and the deformation of the rolling elements; wherein the bearing force model is used to characterize the bearing force of the rolling elements in different directions.

[0134] In some embodiments, there are two rolling bearings, which are fixed at both ends of the shaft. The rolling bearing-crack rotor dynamics model is constructed based on the following steps: when the shaft rotates, determine the first radial displacement information of the two rolling bearings, the second radial displacement information of the first disk, and the third radial displacement information of the second disk; determine the eccentricity of the first disk and the second disk; and construct the rolling bearing-crack rotor dynamics model based on the first radial displacement information, the second radial displacement information, the third radial displacement information, the eccentricity, the crack model, and the bearing force model.

[0135] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing a crack fault analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a first fault dynamics analysis result; wherein, the first fault dynamics analysis result includes the influence of cracks on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0136] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing an eccentricity analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a second fault dynamics analysis result; wherein the second fault dynamics analysis result includes the influence of eccentricity on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0137] In some embodiments, a fault dynamics analysis of a dual-disc rotor system is performed based on a rolling bearing-cracked rotor dynamics model, including: performing radial clearance analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model to generate a third fault dynamics analysis result; wherein, the third fault dynamics analysis result includes the influence of radial clearance on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

[0138] The present invention also provides an electronic device. Figure 30 This is a schematic diagram of the structure of the electronic device provided by the present invention, such as... Figure 30 As shown, the electronic device may include a processor 3010, a communications interface 3020, a memory 3030, and a communication bus 3040. The processor 3010, communications interface 3020, and memory 3030 communicate with each other via the communication bus 3040. The processor 3010 can call logical instructions from the memory 3030 to execute fault dynamics analysis methods.

[0139] Furthermore, the logical instructions in the aforementioned memory 3030 can be implemented as software functional units and, when sold or used as independent products, can be stored in a computer-readable storage medium. Based on this understanding, the technical solution of the present invention, essentially, or the part that contributes to the prior art, or a part of the technical solution, can be embodied in the form of a software product. This computer software product is stored in a storage medium and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute all or part of the steps of the methods described in the various embodiments of the present invention. The aforementioned storage medium includes various media capable of storing program code, such as USB flash drives, portable hard drives, read-only memory (ROM), random access memory (RAM), magnetic disks, or optical disks.

[0140] The present invention also provides a non-transitory computer-readable storage medium having a computer program stored thereon, which, when executed by a processor, implements the fault dynamics analysis methods provided by the above methods.

[0141] The present invention also provides a computer program product, which includes a computer program that can be stored on a non-transitory computer-readable storage medium. When the computer program is executed by a processor, the computer can perform the fault dynamics analysis methods provided by the above methods.

[0142] The device embodiments described above are merely illustrative. The units described as separate components may or may not be physically separate, and the components shown as units may or may not be physical units; that is, they may be located in one place or distributed across multiple network units. Some or all of the modules can be selected to achieve the purpose of this embodiment according to actual needs. Those skilled in the art can understand and implement this without any creative effort.

[0143] Through the above description of the embodiments, those skilled in the art can clearly understand that each embodiment can be implemented by means of software plus necessary general-purpose hardware platforms, and of course, it can also be implemented by hardware. Based on this understanding, the above technical solutions, in essence or the part that contributes to the prior art, can be embodied in the form of a software product. This computer software product can be stored in a computer-readable storage medium, such as ROM / RAM, magnetic disk, optical disk, etc., and includes several instructions to cause a computer device (which may be a personal computer, server, or network device, etc.) to execute the methods described in the various embodiments or some parts of the embodiments.

[0144] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, and not to limit them; although the present invention has been described in detail with reference to the foregoing embodiments, those skilled in the art should understand that modifications can still be made to the technical solutions described in the foregoing embodiments, or equivalent substitutions can be made to some of the technical features; and these modifications or substitutions do not cause the essence of the corresponding technical solutions to deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A fault dynamics analysis method, characterized in that, include: Based on the crack failure characteristics of a dual-disc rotor system, a crack model is constructed. The dual-disc rotor system includes a dual-disc rotor and rolling bearings, the rolling bearings include rolling elements, and cracks exist in the dual-disc rotor system. The crack model is a mathematical model characterizing the influence of the cracks on the dual-disc rotor system. Construct a bearing force model for the rolling bearing; the bearing force model is a mathematical model characterizing the bearing force of the rolling elements; Based on the crack model and the bearing force model, a rolling bearing-cracked rotor dynamic model of the dual-disc rotor system is constructed; the rolling bearing-cracked rotor dynamic model is the dynamic equation describing the system motion state of the dual-disc rotor system. Based on the rolling bearing-cracked rotor dynamics model, a fault dynamics analysis is performed on the dual-disc rotor system.

2. The fault dynamics analysis method according to claim 1, characterized in that, The dual-disc rotor includes a first disk, a second disk, and a rotating shaft. The first disk and the second disk are fixed on the rotating shaft. The crack fault characteristics include the vortex angle, the crack depth, and the rotating shaft radius. The crack model was constructed based on the following steps: The dimensionless crack depth of the dual-disc rotor system is determined based on the crack depth and the shaft radius. Based on the dimensionless crack depth and the vortex difference angle, a cosine model is constructed. The cosine model is a mathematical model that characterizes the opening and closing of the crack. Determine the stiffness change of the shaft; the stiffness change is caused by the crack; The crack model is constructed based on the cosine model and the stiffness variation.

3. The fault dynamics analysis method according to claim 1, characterized in that, The rolling bearing further includes an outer ring and an inner ring, and the rolling element is disposed between the outer ring and the inner ring; The bearing force model is constructed based on the following steps: The deformation of the rolling element is determined based on its angular position and radial clearance; the deformation is caused by the contact between the rolling element and the outer ring and the inner ring. The bearing force model is constructed based on the Hertzian contact stiffness and the deformation of the rolling element; The bearing force model is used to characterize the bearing force of the rolling element in different directions.

4. The fault dynamics analysis method according to claim 2, characterized in that, The number of rolling bearings is two, and the two rolling bearings are respectively fixed at both ends of the rotating shaft; The rolling bearing-cracked rotor dynamics model is constructed based on the following steps: While the shaft is rotating, determine the first radial displacement information of the two rolling bearings, the second radial displacement information of the first disk, and the third radial displacement information of the second disk; Determine the eccentricity of the first disk and the second disk; Based on the first radial displacement information, the second radial displacement information, the third radial displacement information, the eccentricity, the crack model, and the bearing force model, the rolling bearing-crack rotor dynamic model is constructed.

5. The fault dynamics analysis method according to claim 4, characterized in that, The fault dynamics analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model includes: Based on the rolling bearing-cracked rotor dynamics model, crack fault analysis is performed on the dual-disc rotor system to generate the first fault dynamics analysis result. The first fault dynamics analysis results include the influence of the crack on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

6. The fault dynamics analysis method according to claim 4, characterized in that, The fault dynamics analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model includes: Based on the rolling bearing-cracked rotor dynamics model, the eccentricity analysis of the dual-disc rotor system is performed to generate a second fault dynamics analysis result. The second fault dynamics analysis results include the influence of the eccentricity on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

7. The fault dynamics analysis method according to claim 4, characterized in that, The fault dynamics analysis of the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model includes: Based on the rolling bearing-cracked rotor dynamics model, radial clearance analysis is performed on the dual-disc rotor system to generate a third fault dynamics analysis result; The third fault dynamics analysis results include the influence of the radial clearance on the bifurcation characteristics, motion state, and dynamic behavior complexity of the dual-disc rotor system.

8. A fault dynamics analysis device, characterized in that, include: A crack model construction module is used to construct a crack model based on the crack failure characteristics of a dual-disc rotor system. The dual-disc rotor system includes a dual-disc rotor and rolling bearings, the rolling bearings include rolling elements, cracks exist in the dual-disc rotor system, and the crack model is a mathematical model characterizing the impact of the cracks on the dual-disc rotor system. The bearing force model construction module is used to construct the bearing force model of the rolling bearing; the bearing force model is a mathematical model characterizing the bearing force of the rolling elements. The dynamic model construction module is used to construct a rolling bearing-cracked rotor dynamic model of the dual-disc rotor system based on the crack model and the bearing force model; the rolling bearing-cracked rotor dynamic model is a dynamic equation describing the system motion state of the dual-disc rotor system; The fault dynamics analysis module is used to perform fault dynamics analysis on the dual-disc rotor system based on the rolling bearing-cracked rotor dynamics model.

9. An electronic device comprising a memory, a processor, and a computer program stored in the memory and running on the processor, characterized in that, When the processor executes the computer program, it implements the fault dynamics analysis method as described in any one of claims 1 to 7.

10. A non-transitory computer-readable storage medium having a computer program stored thereon, characterized in that, When the computer program is executed by the processor, it implements the fault dynamics analysis method as described in any one of claims 1 to 7.

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