Method and device for determining abnormal rotor balance state and abnormal bearing support stiffness

Abstract

The present invention relates to a method and device for determining abnormal rotor balance and bearing support stiffness. The method comprises: obtaining the mass of the rotor's initial focal point, the rotor's rotor mass, the bearing support stiffness, the distance between the initial focal point and the rotor center, and the angular velocity of the rotor during rotation; determining the rotor's 1st harmonic amplitude based on the rotor mass, the bearing support stiffness, the initial focal point's mass, the distance, and the angular velocity; and determining that the rotor's balance has changed and that the bearing support stiffness has become abnormal if the rotor's 1st harmonic amplitude is greater than a set value. The method of the present invention allows timely detection of rotor imbalance and abnormal changes in composite spring stiffness based on changes in rotor vibration.

Description

Technical Field

[0001] The present invention relates to the technical field of rotor system fault diagnosis, and in particular to a method and device for determining abnormal rotor balance state and abnormal bearing support stiffness. Background Art

[0002] Rotating equipment includes major equipment such as gas generators, power turbines, exciters, motors, gearboxes, and centrifugal compressors. Due to the high speed during operation and the small clearance between the rotor and the bearing, any abnormal changes in the rotor or the stator that supports it may affect the normal operation of the rotor. In previous studies, scholars have proposed analysis, diagnosis, and treatment methods for problems such as rotor imbalance, abnormal bearing support stiffness, and dynamic and static friction. However, for the rotor system, including the rotor itself and its bearing support structure, when both of them are abnormal, a more complex phenomenon will occur, and there is still a lack of reliable methods for diagnosing this phenomenon.

[0003] In the prior art, Chinese patent CN202210200427.0 discloses a method for diagnosing high-speed air compressor gearbox rotor faults. This invention collects vibration signals from centrifugal air compressor high-speed gearbox rotors, performs VMD decomposition, calculates eigenvectors, and performs KPCA dimensionality reduction on the vibration signals. This method then establishes a KELM model for training to develop a fault diagnosis model, preventing sudden failures from causing unit downtime. This invention primarily addresses gearbox rotor faults and is not universally applicable.

[0004] Therefore, there is an urgent need in the prior art for a method that is highly universal and can simultaneously determine the abnormalities of the rotor itself and the bearing support stiffness. Summary of the Invention

[0005] The technical problem to be solved by the present invention is to provide a method and device for determining abnormal rotor balance state and abnormal bearing support stiffness, aiming to solve at least one of the above technical problems.

[0006] The present invention solves the above technical problems with the following technical solution: a method for determining abnormal rotor balance state and abnormal bearing support stiffness, the method comprising:

[0007] Obtaining the mass of an initial focus point of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus point and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus point is the angular position of the residual unbalance amount of the rotor after dynamic balancing;

[0008] Determining a 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0009] If the 1st harmonic amplitude of the rotor is greater than a set value, it is determined that the balance state of the rotor has changed and the bearing support stiffness has become abnormal.

[0010] The beneficial effect of the present invention is that when the rotor rotates, vibration is generated. From the perspective of vibration principle, based on the angular velocity obtained when the rotor rotates, as well as the mass of the initial focus, the rotor mass, the bearing support stiffness, and the distance between the initial focus and the rotor center, the 1-harmonic frequency amplitude of the rotor can be determined. Through the change of the 1-harmonic frequency amplitude, it can be simultaneously determined whether the balance state of the rotor has changed and whether the bearing support stiffness has become abnormal.

[0011] On the basis of the above technical solution, the present invention can also be improved as follows.

[0012] Furthermore, the above method further includes:

[0013] Determining whether a 1st harmonic phase angle changes when the rotor rotates according to the rotor mass and the bearing support stiffness;

[0014] If the 1st harmonic frequency phase angle changes, it is determined that the bearing support stiffness is abnormal.

[0015] The beneficial effect of adopting the above further scheme is that, based on the vibration principle of the rotor, when the 1st harmonic phase angle changes, it can also indicate that the bearing support stiffness is abnormal. Then, whether the bearing support stiffness is abnormal can be determined based on the change of the 1st harmonic phase angle.

[0016] Furthermore, the above-mentioned determination of the 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance and the angular velocity includes:

[0017] The rotor's 1st harmonic amplitude is determined according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity using a first formula, wherein the first formula is:

[0018]

[0019] Where A is the 1-harmonic amplitude, m is the mass of the initial focus, r is the distance between the initial focus and the rotor center, Ω is the angular velocity, K is the bearing support stiffness, and M is the rotor mass.

[0020] The beneficial effect of adopting the above further solution is that the 1st harmonic amplitude can be accurately determined based on the relationship between the 1st harmonic amplitude represented by the first formula and the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance and the angular velocity.

[0021] Furthermore, the above method further includes:

[0022] Obtaining the axis trajectory of the rotor when it rotates;

[0023] If the axis trajectory is elliptical and directional, it is determined that the bearing support stiffness is abnormal.

[0024] The beneficial effect of adopting the above further scheme is that when the axis trajectory of the rotor during rotation is elliptical and directional, it can also indicate that the bearing support stiffness is abnormal. In the scheme of the present application, it is also possible to judge whether the bearing support stiffness is abnormal based on the axis trajectory.

[0025] Furthermore, the above-mentioned determining whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness includes:

[0026] determining a critical speed of the rotor according to the rotor mass and the bearing support stiffness;

[0027] If the angular velocity is less than the critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change;

[0028] If the angular velocity is greater than the critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

[0029] The beneficial effect of adopting the above further scheme is that when the angular velocity is greater than the critical speed, it indicates that the rotation of the rotor may exceed the critical range corresponding to the critical speed, and the rotation is abnormal, then it can be determined that the 1-harmonic frequency phase angle during the rotation of the rotor has changed; if the angular velocity is less than the critical speed, then it indicates that the rotation of the rotor is in a normal state, then it can be determined that the 1-harmonic frequency phase angle during the rotation of the rotor has not changed.

[0030] Furthermore, the bearing support stiffness includes a first stiffness and a second stiffness, wherein the first stiffness is the stiffness in the horizontal direction and the second stiffness is the stiffness in the vertical direction;

[0031] The above-mentioned determination of the 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity includes:

[0032] determining a 1st harmonic amplitude of the rotor in a horizontal direction according to the rotor mass, the first stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0033] The 1-fold frequency amplitude of the rotor in the vertical direction is determined according to the rotor mass, the second stiffness, the mass of the initial focus, the distance, and the angular velocity. The 1-fold frequency amplitude of the rotor includes the 1-fold frequency amplitude of the rotor in the horizontal direction and the 1-fold frequency amplitude of the rotor in the vertical direction.

[0034] The beneficial effect of adopting the above further solution is that, by determining the 1st harmonic amplitude from the stiffness in different directions, the change in the 1st harmonic amplitude of the rotor caused by the rotation of the rotor can be more accurately characterized.

[0035] Furthermore, the bearing support stiffness includes a first stiffness and a second stiffness, wherein the first stiffness is the stiffness in the horizontal direction and the second stiffness is the stiffness in the vertical direction;

[0036] The above-mentioned determining whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness includes:

[0037] determining a first critical speed of the rotor in a horizontal direction according to the rotor mass and the first stiffness;

[0038] determining a second critical speed of the rotor in a vertical direction according to the rotor mass and the second stiffness, wherein the critical speed includes the first critical speed and the second critical speed;

[0039] If the angular velocity is less than the first critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change;

[0040] If the angular velocity is greater than the second critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

[0041] The beneficial effect of adopting the above further solution is that the 1st harmonic phase angle is determined from the stiffness in different directions, which can more accurately characterize the changes in the 1st harmonic phase angle of the rotor when the rotor rotates.

[0042] In a second aspect, in order to solve the above technical problems, the present invention further provides a device for determining abnormal rotor balance state and abnormal bearing support stiffness, the device comprising:

[0043] a data acquisition module, configured to acquire the mass of an initial focus of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus is the angular position of the residual unbalance amount of the rotor after dynamic balancing;

[0044] an amplitude determination module, configured to determine a 1-harmonic frequency amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0045] The abnormality judgment module is used to determine that the balance state of the rotor has changed and the bearing support stiffness has become abnormal when the 1st harmonic amplitude of the rotor is greater than a set value.

[0046] In the third aspect, in order to solve the above-mentioned technical problems, the present invention also provides an electronic device, which includes a memory, a processor, and a computer program stored in the memory and runnable on the processor. When the processor executes the computer program, the method for determining the abnormal rotor balance state and the abnormal bearing support stiffness of the present application is implemented.

[0047] In a fourth aspect, in order to solve the above-mentioned technical problems, the present invention also provides a computer-readable storage medium, on which a computer program is stored. When the computer program is executed by a processor, the method for determining the abnormal rotor balance state and the abnormal bearing support stiffness of the present application is implemented.

[0048] Additional aspects and advantages of the present application will be given in part in the following description, which will become apparent from the following description, or will be learned through practice of the present application. BRIEF DESCRIPTION OF THE DRAWINGS

[0049] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for describing the embodiments of the present invention.

[0050] Figure 1 A flow chart of a method for determining abnormal rotor balance state and abnormal bearing support stiffness provided by one embodiment of the present invention;

[0051] Figure 2 A schematic diagram of a rotor vibration model provided by one embodiment of the present invention;

[0052] Figure 3 A schematic diagram of anisotropic stiffness provided by one embodiment of the present invention;

[0053] Figure 4 A schematic diagram of an RB211 rotor test bench provided in accordance with an embodiment of the present invention;

[0054] Figure 5 A schematic diagram of rotor vibration corresponding to a well-aligned rotor, a balancing plate at 0°, and a 1g counterweight provided by one embodiment of the present invention;

[0055] Figure 6 A schematic diagram of rotor vibration corresponding to a well-aligned rotor, a 0° balance plate, and a 2g counterweight provided by an embodiment of the present invention;

[0056] Figure 7 A schematic diagram of rotor vibration corresponding to a well-aligned rotor, a 90° balance plate, and a 1g counterweight provided by an embodiment of the present invention;

[0057] Figure 8 A diagram showing the axis trajectory of a well-aligned rotor at a rotational speed of 2000 r / min provided by one embodiment of the present invention;

[0058] Figure 9 A diagram showing the axis trajectory of a well-aligned rotor at a rotational speed of 4000 r / min provided by one embodiment of the present invention;

[0059] Figure 10 A diagram showing the axis trajectory of a centered eccentric rotor at a rotational speed of 2000 r / min is provided in accordance with one embodiment of the present invention;

[0060] Figure 11 A diagram showing the axis trajectory of a centered eccentric rotor at a speed of 4000 r / min provided by one embodiment of the present invention;

[0061] Figure 12 A schematic structural diagram of a device for determining abnormal rotor balance state and abnormal bearing support stiffness provided by one embodiment of the present invention;

[0062] Figure 13 The present invention provides a schematic structural diagram of an electronic device according to an embodiment of the present invention.

[0063] Figure 2 In the figure, 101, rotor; 102, rotor vibration equilibrium position; 103, rotor rotation direction; 104, high point; 105, rotor amplitude, A; 106, key phase; 107, focus; 108, phase angle of focus, δ; 109, phase angle of high point, α; 110, spring stiffness, K;

[0064] Figure 3 In the figure, 201, weak spring stiffness; 202, strong spring stiffness; 203, housing; 204, pipeline; 205, foundation; 206, bearing; 207, rotor;

[0065] Figure 4 Among them, 301, motor; 302, key phase; 303, 1# bearing; 304, vibration sensor; 305, balance plate; 306, counterweight; 307, 2# bearing. DETAILED DESCRIPTION

[0066] The principles and features of the present invention are described below. The examples given are only used to explain the present invention and are not used to limit the scope of the present invention.

[0067] The following describes in detail the technical solution of the present invention and how the technical solution of the present invention solves the above-mentioned technical problems using specific embodiments. The following specific embodiments can be combined with each other, and the same or similar concepts or processes may not be repeated in some embodiments. The following embodiments of the present invention are described in conjunction with the accompanying drawings.

[0068] The solution provided by the embodiments of the present invention is applicable to any application scenario requiring the determination of abnormal rotor balance and bearing support stiffness. The solution provided by the embodiments of the present invention can be executed by any electronic device, for example, a user's terminal device, including at least one of the following: a smartphone, tablet computer, laptop computer, desktop computer, smart speaker, smart watch, smart TV, or smart in-vehicle device.

[0069] The embodiment of the present invention provides a possible implementation method, such as Figure 1 As shown, a flowchart of a method for determining abnormal rotor balance state and abnormal bearing support stiffness is provided. This solution can be executed by any electronic device, for example, a terminal device, or by a terminal device and a server. For ease of description, the method provided by the embodiment of the present invention will be described below using a terminal device as an example of the execution subject. Figure 1 As shown in the flowchart, the method may include the following steps:

[0070] Step S110, obtaining the mass of an initial focus point of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus point and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus point is the angular position of the residual unbalance amount of the rotor after dynamic balancing;

[0071] Step S120, determining the 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0072] Step S130: If the 1st harmonic amplitude of the rotor is greater than a set value, it is determined that the balance state of the rotor has changed and the bearing support stiffness has become abnormal.

[0073] According to the method of the present invention, when the rotor rotates, vibration is generated. From the perspective of vibration principle, based on the angular velocity obtained when the rotor rotates, as well as the mass of the initial focus, the rotor mass, the bearing support stiffness, and the distance between the initial focus and the rotor center, the 1-harmonic frequency amplitude of the rotor can be determined. Through the change of the 1-harmonic frequency amplitude, it can be simultaneously determined whether the balance state of the rotor has changed and whether the bearing support stiffness has become abnormal.

[0074] The scheme of the present invention is further described below in conjunction with the following specific embodiments. In this embodiment, the principles involved in this application and how to determine the abnormality of the rotor balance state and the abnormality of the bearing support stiffness based on the 1st harmonic amplitude and 1st harmonic phase angle of the rotor based on the vibration principle are first described.

[0075] Abnormal rotor balance refers to changes in the rotor balance state. Figure 2As shown, when the rotor's mass centerline and the shaft centerline do not coincide, imbalance occurs. Rotor imbalance is the amount of center-of-gravity offset, or the amount of weight required to achieve balance at a certain radius. The unit is mass multiplied by radius. The angular location of the rotor imbalance is called the high point. When the rotor vibrates, it deviates from the equilibrium position. The point on the outer surface of the shaft (corresponding to the rotor's equilibrium position) at this point is called the high point. The rotor includes a healthy phase, and the bearing supports can be springs.

[0076] Establish an isotropic composite spring stiffness model, let δ be the phase angle of the focus, and represent the angle between the line 1 between the rotor center and the focus and the line 2 between the rotor center and the key phase. For details, see Figure 2 108 in the figure; A is the displacement of the rotor from the vibration equilibrium position (rotor vibration equilibrium position), that is, the amplitude of the vibration vector; α is the phase angle of the high point, and the phase angle of the high point and the phase angle of the vibration vector are made the same value, that is, α and δ are the same value, which represents the angle between the line 3 between the center of the rotor and the high point and the line 2 between the center of the rotor and the key phase. On this basis, the influence of the change in unbalance on the rotor vibration is analyzed.

[0077] In the present application, the vibration vector can be expressed in exponential form, with the position of the key phase as 0°, the reverse rotation direction of the rotor as the angle increasing direction, the line between the center of the rotor and the key phase as the Y axis, the direction of the key phase as the positive direction of the Y axis, and the axis passing through the center of the rotor and perpendicular to the Y axis as the X axis. The positive direction of the Y axis is rotated 90° in the reverse rotation direction to obtain the positive direction of the X axis, and a coordinate system is established. For details, see Figure 2 .

[0078] The rotor's 1-fold frequency vibration vector can be expressed as:

[0079]

[0080] Where A is the amplitude of the rotor's 1st-harmonic vibration vector (rotor amplitude A), j is the unit of an imaginary number, m is the mass of the initial focus, r is the distance between the initial focus and the center of the rotor, Ω is the angular velocity of the rotor during rotation, K is the spring stiffness, M is the rotor mass, and mr is the rotor imbalance.

[0081] Based on the above formula, the rotor's 1-harmonic frequency amplitude can be expressed by the first formula:

[0082]

[0083] This suggests that changes in rotor imbalance will also cause changes in the rotor's 1st harmonic amplitude. Furthermore, changes in the rotor's 1st harmonic amplitude indicate an abnormal change in the rotor's balance.

[0084] The critical speed of the rotor can be expressed by the second formula:

[0085]

[0086] Among them, Ω res Indicates critical speed.

[0087] When the rotor speed (rotor angular velocity) is below the critical speed (Ω < Ωres), α = δ, indicating that the vibration peak and the focal point are in phase. When the rotor speed is above the critical speed (Ω > Ωres), α = -δ, indicating that the vibration peak and the focal point are out of phase. This indicates that if the focal point phase angle δ changes while the rotor speed is constant, the rotor's single harmonic frequency phase angle will also change. Furthermore, changes in the rotor's single harmonic frequency phase angle indicate an abnormality in the bearing support stiffness.

[0088] In practical applications, for rotating equipment, see Figure 3 As shown, the method of installing the rotor system's casing on the foundation will produce anisotropic stiffness characteristics, and the spring stiffness of the rotor corresponding to the machine in the horizontal direction is much lower than the vertical spring stiffness; the external piping system and accessories usually produce different spring stiffnesses in different directions; in sliding bearings, especially pressure dam bearings, tilting pad bearings and other bearings with oil film disturbance structures, the rotor will run at a higher eccentricity. In this case, due to the action of the fluid wedge, the journal position has anisotropic stiffness. In the present application scheme, the strong and weak spring stiffnesses in all directions can be comprehensively considered and integrated into a strong composite spring stiffness (also called the second stiffness) and a weak composite spring stiffness (also called the first stiffness) that are perpendicular to each other.

[0089] The composite spring stiffness in the anisotropic stiffness system has two values, namely the first stiffness and the second stiffness. The vibration behavior (amplitude and phase angle) of the rotor in the anisotropic stiffness system can be expressed as the third and fourth formulas:

[0090]

[0091]

[0092] Among them, K 弱 Indicates the weak composite spring stiffness, that is, the first stiffness, K 强 Indicates the strong composite spring stiffness, that is, the second stiffness, A 弱 A is the amplitude of the rotor 1-fold frequency vibration vector in the direction of the weak composite spring stiffness (horizontal direction), 强 is the amplitude of the rotor 1-fold frequency vibration vector in the direction of the strong composite spring stiffness (vertical direction); the same principle as described above, based on the above A 弱 and A 强The corresponding two formulas can determine the 1-fold frequency amplitude of the rotor in the horizontal direction and the 1-fold frequency amplitude of the rotor in the vertical direction.

[0093] Based on the same principle of determining the critical speed as the second formula above, the first critical speed Ω corresponding to the rotor in the horizontal direction can be determined according to the rotor mass and the first stiffness: res1 , and determining the second critical speed Ω of the rotor in the vertical direction according to the rotor mass and the second stiffness res2 When Ω<Ω res1 When Ω>Ω, the denominator of the third formula is positive, the vibration high point and the key point are in phase (indicating that the 1st frequency phase angle does not change when the rotor rotates), and the 1st frequency amplitude in the direction of the weak composite spring stiffness is higher than the 1st frequency amplitude in the direction of the strong composite spring stiffness; when Ω>Ω res2 When , the denominator of the fourth formula is a negative value, the vibration high point and the key point are in antiphase (indicating that the 1st frequency phase angle changes when the rotor rotates), and the 1st frequency amplitude in the direction of the weak composite spring stiffness is lower than the 1st frequency amplitude in the direction of the strong composite spring stiffness.

[0094] As the rotor rotates, the position of the rotor axis changes, forming a trajectory. Analysis of this trajectory indicates the presence of strong and weak composite spring stiffnesses in the rotor system. Furthermore, when the speed is stable, the rotor axis trajectory is elliptical and maintains a stable direction. When the composite spring stiffness changes, the direction of the elliptical axis trajectory also changes. In other words, when the axis trajectory is elliptical and directional, an abnormality in the bearing support stiffness is determined. Otherwise, the bearing support stiffness is determined to be normal. An abnormality is likely an indicator of a rotor system failure.

[0095] Based on the above conclusions, the rotor test bench can be used to verify the vibration behavior of the rotor when the rotor balance state changes and the composite spring stiffness (bearing support stiffness) changes. The specific process is as follows:

[0096] The rotor test bench consists of a foundation, motor assembly, rotor assembly and vibration collection assembly. For details, please refer to Figure 4The schematic diagram of the RB211 rotor test bench shown in the figure shows the foundation for mounting various components. The motor assembly has an applicable voltage range of 190V-250V, an applicable frequency range of 50Hz-60Hz, a maximum current not exceeding 3.0A, an adjustable speed range of 0r / min-12,000r / min, and a key phase measurement position. The rotor assembly includes a 400mm long and 10mm diameter rotor shaft, a balancing disc with 16 holes, two sliding bearings with a span of 350mm and a gap of 0.1mm, and several counterweights. The vibration acquisition assembly includes a key phase sensor, a horizontally (x-direction) mounted vibration sensor, and a vertically (y-direction) mounted vibration sensor. All three sensors use Bently 3300XL 8mm non-contact eddy current sensors with a sensitivity of 7.87V / mm. The assembly also includes supporting brackets, data acquisition, processing, and display equipment.

[0097] The data acquisition and processing equipment of the rotor test bench must have the following functions: (1) use the vibration sensor to collect the original waveform signal (the original waveform signal is the corresponding amplitude and phase angle signal when the rotor rotates), (2) have a filtering function to filter out waveforms of specific frequencies, (3) have the function of calculating and displaying the amplitude and phase of specific frequency components, and (4) have the function of displaying the axis trajectory.

[0098] Based on the above rotor test platform, the mass and direction of the counterweight can be adjusted to verify the effect of the change in imbalance on the rotor vibration. Specifically:

[0099] See also Figure 5 With good alignment (specifically, the error between the horizontal and vertical amplitudes does not exceed 20μm), a 0° balance disc, and a 1g counterweight installed, the actual measured rotor first-order critical speed is approximately 3320r / min. At a rotor speed of 2000r / min, the rotor's X-direction 1st harmonic amplitude is 11.5μm with a phase angle of 140°, and the Y-direction 1st harmonic amplitude is 11.0μm with a phase angle of 220°. At 4000r / min, the rotor's X-direction 1st harmonic amplitude is 11.5μm with a phase angle of 140°, and the Y-direction 1st harmonic amplitude is 11.0μm with a phase angle of 220°.

[0100] See also Figure 6Under the condition of good alignment and 2g counterweight installed at 0° on the balancing disk, the actual measured first-order critical speed of the rotor is about 3320r / min. At a rotor speed of 2000r / min, the amplitude of the rotor's 1st harmonic frequency in the X direction is 21.3μm and the phase angle is 148°, and the amplitude of the rotor's 1st harmonic frequency in the Y direction is 20.4μm and the phase angle is 227°. At 4000r / min, the amplitude of the rotor's 1st harmonic frequency in the X direction is 15.2μm and the phase angle is 312°, and the amplitude of the rotor's 1st harmonic frequency in the Y direction is 15.5μm and the phase angle is 34°.

[0101] See also Figure 7 Under the condition of good alignment and 1g counterweight installed at 90° on the balancing disk, the actual measured first-order critical speed of the rotor is about 3320r / min. At a rotor speed of 2000r / min, the amplitude of the rotor's 1st harmonic frequency in the X direction is 15.7μm and the phase angle is 249°, and the amplitude of the rotor's 1st harmonic frequency in the Y direction is 15.1μm and the phase angle is 330°. At 4000r / min, the amplitude of the rotor's 1st harmonic frequency in the X direction is 11.1μm and the phase angle is 56°, and the amplitude of the rotor's 1st harmonic frequency in the Y direction is 11.4μm and the phase angle is 138°.

[0102] Based on the above Figures 5 to 7 The experimental results can verify the influence of the change of imbalance size and direction on the amplitude and phase angle of the rotor.

[0103] In addition, in the present application, the influence of the change in the composite spring stiffness on the rotor vibration can be verified by adjusting the height of the sliding bearing. The specific process is as follows:

[0104] In the centered state and without the balancing weight installed on the balancing disc, the actual measured first-order critical speed of the rotor is about 3320 r / min. Figure 8 and Figure 9 ,The rotor 1-time frequency axis trajectory diagrams were collected at the rotor speeds of 2000r / min and 4000r / min, and their shapes were all elliptical, close to a circle;

[0105] In the rotor test bench, the 1# bearing is raised by 40μm to increase the spring stiffness in the vertical direction (centering eccentricity), and the balancing disc is not equipped with a counterweight. The actual measured first-order critical speed of the rotor in the direction of weak composite spring stiffness is about 3335r / min, and the first-order critical speed in the direction of strong composite spring stiffness is about 3510r / min, see Figure 10 and Figure 11The rotor 1-harmonic frequency axis trajectory diagrams were collected at rotor speeds of 2000r / min and 4000r / min respectively. The change in composite spring stiffness makes the axis trajectory have a certain directionality. When the rotor speed is lower than the 1st-order critical speed in the direction of weak composite spring stiffness, the major axis direction of the axis trajectory is consistent with the direction of weak composite spring stiffness. When the rotor speed is higher than the 1st-order critical speed in the direction of strong composite spring stiffness, the major axis direction of the axis trajectory is consistent with the direction of strong composite spring stiffness.

[0106] Based on the above experiments, the following conclusions can be drawn:

[0107] (1) Changes in the rotor balance state are mainly manifested as changes in the 1-harmonic frequency amplitude or 1-harmonic frequency phase angle; (2) When the composite spring stiffness is abnormal, the main manifestation is that the axis trajectory corresponding to the 1-harmonic frequency is elliptical and directional; (3) When changes in the rotor imbalance state and abnormal composite spring stiffness occur at the same time, it is possible that the amplitude of the rotor in a certain direction exceeds the alarm value.

[0108] Based on the conclusions obtained from the above experiments, the method for determining abnormal rotor balance state and abnormal bearing support stiffness provided in this embodiment includes the following steps:

[0109] Step S110, obtaining the mass of an initial focus point of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus point and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus point is the angular position of the residual unbalance amount of the rotor after dynamic balancing;

[0110] Step S120, determining the 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0111] Step S130: If the 1st harmonic amplitude of the rotor is greater than a set value, it is determined that the balance state of the rotor has changed and the bearing support stiffness has become abnormal.

[0112] The above-mentioned set value refers to a pre-set alarm value, which can be determined based on experiments. Different rotor systems may have different corresponding set values. It should be noted that if the rotor's 1st harmonic amplitude is not greater than the set value, it cannot be used to determine whether the rotor's balance state has changed or whether the bearing support stiffness has abnormalities. Based on the rotor's 1st harmonic amplitude, it is possible to determine whether the balance state has changed, as will be explained below.

[0113] When the balance state of the rotor changes and the bearing support stiffness becomes abnormal, it may indicate that a fault has occurred in the rotor system. Therefore, when it is found that the balance state of the rotor has changed and the bearing support stiffness has become abnormal, the rotor system can be promptly analyzed and checked for faults, and the faults can be eliminated in time to ensure the normal operation of the rotor system.

[0114] It is understood that the rotor system refers to the rotating structure in the rotating equipment.

[0115] Optionally, according to the first formula described above, determining the 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity includes:

[0116] The rotor's 1st harmonic amplitude is determined according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity using a first formula, wherein the first formula is:

[0117]

[0118] Where A is the 1-harmonic amplitude, m is the mass of the initial focus, r is the distance between the initial focus and the rotor center, Ω is the angular velocity, K is the bearing support stiffness, and M is the rotor mass.

[0119] Optionally, if the bearing support stiffness includes a first stiffness and a second stiffness, the first stiffness is the stiffness in the horizontal direction, and the second stiffness is the stiffness in the vertical direction;

[0120] Then, according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity, determining the 1st harmonic amplitude of the rotor includes:

[0121] determining a 1st harmonic amplitude of the rotor in a horizontal direction according to the rotor mass, the first stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0122] The 1-fold frequency amplitude of the rotor in the vertical direction is determined according to the rotor mass, the second stiffness, the mass of the initial focus, the distance, and the angular velocity. The 1-fold frequency amplitude of the rotor includes the 1-fold frequency amplitude of the rotor in the horizontal direction and the 1-fold frequency amplitude of the rotor in the vertical direction.

[0123] At this time, in step S130, if the 1-harmonic frequency amplitude of the rotor is greater than the set value, it means that the 1-harmonic frequency amplitude of the rotor in the horizontal direction is greater than the set value, and the 1-harmonic frequency amplitude of the rotor in the vertical direction is also greater than the set value.

[0124] Based on the conclusions obtained from the above experiments, in the present application, changes in the balance state of the rotor and abnormalities in the bearing support stiffness can also be judged separately.

[0125] Optionally, the method further includes:

[0126] Determining whether a 1st harmonic phase angle changes when the rotor rotates according to the rotor mass and the bearing support stiffness;

[0127] If the 1st harmonic frequency phase angle changes, it is determined that the bearing support stiffness is abnormal.

[0128] The change in the 1st harmonic phase angle refers to a change in the phase angle relative to the rotor's equilibrium position. At this point, the phase angle of the rotor's high point is out of phase with the phase angle of the rotor's center point, indicating a change in the phase δ of the rotor's center point.

[0129] Optionally, one implementation of determining whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness is:

[0130] determining a critical speed of the rotor according to the rotor mass and the bearing support stiffness;

[0131] If the angular velocity is less than the critical speed, it is determined that the phase angle of the 1st harmonic frequency during the rotation of the rotor does not change; in this case, α=δ, which means that the vibration peak and the focus are in phase;

[0132] If the angular velocity is greater than the critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes. At this time, α=-δ, which is called the anti-phase between the vibration peak and the vibration focus.

[0133] The critical speed of the rotor can be determined according to the rotor mass and the bearing support stiffness by the second formula mentioned above, which will not be repeated here.

[0134] Optionally, if the bearing support stiffness includes a first stiffness and a second stiffness, the first stiffness is the stiffness in the horizontal direction, and the second stiffness is the stiffness in the vertical direction;

[0135] Another implementation of determining whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness is:

[0136] determining a first critical speed of the rotor in a horizontal direction according to the rotor mass and the first stiffness;

[0137] determining a second critical speed of the rotor in a vertical direction according to the rotor mass and the second stiffness, wherein the critical speed includes the first critical speed and the second critical speed;

[0138] If the angular velocity is less than the first critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation has not changed. At this time, the vibration peak and the vibration focus are in phase, and the 1st harmonic amplitude in the direction of the weak composite spring stiffness (first stiffness) is greater than the 1st harmonic amplitude in the direction of the strong composite spring stiffness (second stiffness).

[0139] If the angular velocity is greater than the second critical speed, it is determined that the 1st harmonic phase angle during the rotation of the rotor changes. At this time, the vibration high point and the focus are in opposite phases, and the 1st harmonic amplitude in the direction of the weak composite spring stiffness (first stiffness) is lower than the 1st harmonic amplitude in the direction of the strong composite spring stiffness (second stiffness).

[0140] The first critical speed and the second critical speed can both be determined based on the second formula above, which will not be described in detail here.

[0141] Optionally, the method further includes:

[0142] Obtaining the axis trajectory of the rotor when it rotates;

[0143] If the axis trajectory is elliptical and directional, it is determined that the bearing support stiffness is abnormal.

[0144] The above-mentioned axis trajectory can be obtained and displayed through a rotor test bench. The directionality of the axis trajectory means that the long axis direction of the axis trajectory remains stable when the rotor speed is constant.

[0145] The solution of the present invention can promptly detect rotor imbalance and abnormal changes in composite spring stiffness based on changes in rotor vibration. This helps relevant technical personnel promptly detect rotor imbalance and abnormal changes in composite spring stiffness, further determine the fault location, identify the cause of the fault, and develop targeted maintenance plans to ensure the safe operation of rotating equipment.

[0146] Based on Figure 1 Based on the same principle as the method shown in , the embodiment of the present invention further provides a device 20 for determining abnormal rotor balance state and abnormal bearing support stiffness, such as Figure 12 As shown in , the rotor balance state abnormality and bearing support stiffness abnormality determination device 20 may include a data acquisition module 210, an amplitude determination module 220 and an abnormality judgment module 230, wherein:

[0147] a data acquisition module 210 configured to acquire the mass of an initial focal point of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focal point and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focal point is the angular position of the residual unbalance amount of the rotor after dynamic balancing;

[0148] an amplitude determination module 220 for determining a 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0149] The abnormality judgment module 230 is used to determine that the balance state of the rotor has changed and the bearing support stiffness has become abnormal when the 1st harmonic amplitude of the rotor is greater than a set value.

[0150] Optionally, the above device further includes:

[0151] a phase angle change determination module, configured to determine whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness;

[0152] The first bearing support stiffness abnormality judgment module is used to determine that the bearing support stiffness is abnormal when the 1st harmonic frequency phase angle changes.

[0153] Optionally, when determining the 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity, the amplitude determination module 220 is specifically configured to:

[0154] The rotor's 1st harmonic amplitude is determined according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity using a first formula, wherein the first formula is:

[0155]

[0156] Where A is the 1-harmonic amplitude, m is the mass of the initial focus, r is the distance between the initial focus and the rotor center, Ω is the angular velocity, K is the bearing support stiffness, and M is the rotor mass.

[0157] Optionally, the above device further includes:

[0158] An axis trajectory acquisition module, used to acquire the axis trajectory of the rotor when it rotates;

[0159] The second bearing support stiffness abnormality judgment module is used to determine that the bearing support stiffness is abnormal when the axis trajectory is elliptical and directional.

[0160] Optionally, when determining whether the 1st harmonic phase angle changes during the rotation of the rotor based on the rotor mass and the bearing support stiffness, the phase angle change determination module is specifically configured to:

[0161] determining a critical speed of the rotor according to the rotor mass and the bearing support stiffness;

[0162] If the angular velocity is less than the critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change;

[0163] If the angular velocity is greater than the critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

[0164] Optionally, the bearing support stiffness includes a first stiffness and a second stiffness, wherein the first stiffness is the stiffness in the horizontal direction and the second stiffness is the stiffness in the vertical direction;

[0165] When determining the 1st harmonic amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity, the amplitude determination module 220 is specifically configured to:

[0166] determining a 1st harmonic amplitude of the rotor in a horizontal direction according to the rotor mass, the first stiffness, the mass of the initial focus, the distance, and the angular velocity;

[0167] The 1-fold frequency amplitude of the rotor in the vertical direction is determined according to the rotor mass, the second stiffness, the mass of the initial focus, the distance, and the angular velocity. The 1-fold frequency amplitude of the rotor includes the 1-fold frequency amplitude of the rotor in the horizontal direction and the 1-fold frequency amplitude of the rotor in the vertical direction.

[0168] Optionally, the bearing support stiffness includes a first stiffness and a second stiffness, the first stiffness is the stiffness in the horizontal direction, and the second stiffness is the stiffness in the vertical direction;

[0169] The phase angle change determination module is specifically used to determine whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness:

[0170] determining a first critical speed of the rotor in a horizontal direction according to the rotor mass and the first stiffness;

[0171] determining a second critical speed of the rotor in a vertical direction according to the rotor mass and the second stiffness, wherein the critical speed includes the first critical speed and the second critical speed;

[0172] If the angular velocity is less than the first critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change;

[0173] If the angular velocity is greater than the second critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

[0174] The device for determining abnormal rotor balance state and abnormal bearing support stiffness of an embodiment of the present invention can execute the method for determining abnormal rotor balance state and abnormal bearing support stiffness provided by the embodiment of the present invention. The implementation principle is similar. The actions performed by each module and unit in the device for determining abnormal rotor balance state and abnormal bearing support stiffness in each embodiment of the present invention correspond to the steps in the method for determining abnormal rotor balance state and abnormal bearing support stiffness in each embodiment of the present invention. For the detailed functional description of each module of the device for determining abnormal rotor balance state and abnormal bearing support stiffness, please refer to the description in the corresponding method for determining abnormal rotor balance state and abnormal bearing support stiffness shown in the previous text, which will not be repeated here.

[0175] Among them, the above-mentioned device for determining abnormal rotor balance state and abnormal bearing support stiffness can be a computer program (including program code) running in a computer device, for example, the device for determining abnormal rotor balance state and abnormal bearing support stiffness is an application software; the device can be used to execute the corresponding steps in the method provided in the embodiment of the present invention.

[0176] In some embodiments, the device for determining abnormal rotor balance state and abnormal bearing support stiffness provided by an embodiment of the present invention can be implemented in a combination of software and hardware. As an example, the device for determining abnormal rotor balance state and abnormal bearing support stiffness provided by an embodiment of the present invention can be a processor in the form of a hardware decoding processor, which is programmed to execute the method for determining abnormal rotor balance state and abnormal bearing support stiffness provided by an embodiment of the present invention. For example, the processor in the form of a hardware decoding processor can adopt one or more application-specific integrated circuits (ASICs), DSPs, programmable logic devices (PLDs), complex programmable logic devices (CPLDs), field-programmable gate arrays (FPGAs) or other electronic components.

[0177] In other embodiments, the device for determining abnormal rotor balance state and abnormal bearing support stiffness provided by the embodiment of the present invention can be implemented in a software manner. Figure 12 A device for determining abnormal rotor balance state and abnormal bearing support stiffness stored in a memory is shown, which can be software in the form of a program and plug-in, and includes a series of modules, including a data acquisition module 210, an amplitude determination module 220 and an abnormality judgment module 230, for implementing the method for determining abnormal rotor balance state and abnormal bearing support stiffness provided in an embodiment of the present invention.

[0178] The modules involved in the embodiments of the present invention may be implemented in software or hardware, wherein the name of a module does not necessarily limit the module itself.

[0179] Based on the same principle as the method shown in the embodiments of the present invention, an electronic device is also provided in the embodiments of the present invention, which may include but is not limited to: a processor and a memory; the memory is used to store computer programs; the processor is used to execute the method shown in any embodiment of the present invention by calling the computer program.

[0180] In an alternative embodiment, an electronic device is provided, such as Figure 13 As shown, Figure 13 The electronic device 4000 shown includes: a processor 4001 and a memory 4003. The processor 4001 and the memory 4003 are connected, for example, via a bus 4002. Optionally, the electronic device 4000 may further include a transceiver 4004, which can be used for data exchange between the electronic device and other electronic devices, such as data transmission and / or data reception. It should be noted that in actual applications, the number of transceivers 4004 is not limited to one, and the structure of the electronic device 4000 does not constitute a limitation on the embodiments of the present invention.

[0181] Processor 4001 may be a CPU (Central Processing Unit), a general-purpose processor, a DSP (Digital Signal Processor), an ASIC (Application Specific Integrated Circuit), an FPGA (Field Programmable Gate Array), or other programmable logic devices, transistor logic devices, hardware components, or any combination thereof. It may implement or execute the various exemplary logic blocks, modules, and circuits described in conjunction with the present disclosure. Processor 4001 may also be a combination that implements computing functions, such as a combination of one or more microprocessors, a combination of a DSP and a microprocessor, and the like.

[0182] Bus 4002 may include a path for transmitting information between the above components. Bus 4002 may be a PCI (Peripheral Component Interconnect) bus or an EISA (Extended Industry Standard Architecture) bus. Bus 4002 may be divided into an address bus, a data bus, a control bus, etc. For ease of representation, Figure 13 Only one thick line is used in the diagram, but this does not mean that there is only one bus or one type of bus.

[0183] The memory 4003 may be a ROM (Read Only Memory) or other types of static storage devices that can store static information and instructions, a RAM (Random Access Memory) or other types of dynamic storage devices that can store information and instructions, or an EEPROM (Electrically Erasable Programmable Read Only Memory), a CD-ROM (Compact Disc Read Only Memory) or other optical disk storage, optical disk storage (including compact discs, laser discs, optical discs, digital versatile discs, Blu-ray discs, etc.), a magnetic disk storage medium or other magnetic storage device, or any other medium that can be used to carry or store desired program code in the form of instructions or data structures and can be accessed by a computer, but is not limited to these.

[0184] The memory 4003 is used to store application code (computer program) for executing the solution of the present invention, and is controlled by the processor 4001. The processor 4001 is used to execute the application code stored in the memory 4003 to implement the content shown in the above method embodiment.

[0185] Among them, the electronic device can also be a terminal device, Figure 13 The electronic device shown is only an example and should not limit the functions and scope of use of the embodiments of the present invention.

[0186] An embodiment of the present invention provides a computer-readable storage medium having a computer program stored thereon. When the computer-readable storage medium is run on a computer, the computer can execute the corresponding contents of the aforementioned method embodiment.

[0187] According to another aspect of the present invention, a computer program product or computer program is provided. The computer program product or computer program includes computer instructions stored in a computer-readable storage medium. A processor of a computer device reads the computer instructions from the computer-readable storage medium and executes the computer instructions, causing the computer device to perform the methods for determining abnormal rotor balance and bearing support stiffness provided in the various implementations described above.

[0188] Computer program code for performing the operations of the present invention may be written in one or more programming languages, or a combination thereof, including object-oriented programming languages such as Java, Smalltalk, C++, and conventional procedural programming languages such as "C" or similar programming languages. The program code may be executed entirely on the user's computer, partially on the user's computer, as a stand-alone software package, partially on the user's computer and partially on a remote computer, or entirely on the remote computer or server. In cases involving a remote computer, the remote computer may be connected to the user's computer through any type of network, including a local area network (LAN) or a wide area network (WAN), or may be connected to an external computer (e.g., through the Internet using an Internet service provider).

[0189] It should be understood that the flowcharts and block diagrams in the accompanying drawings illustrate the possible implementation architecture, functions and operations of the methods and computer program products according to various embodiments of the present invention. In this regard, each box in the flowchart or block diagram can represent a module, program segment, or a part of code, and the module, program segment, or a part of code contains one or more executable instructions for implementing the specified logical function. It should also be noted that in some alternative implementations, the functions marked in the box can also occur in a different order than the order marked in the accompanying drawings. For example, two boxes represented in succession can actually be executed substantially in parallel, and they can sometimes be executed in the opposite order, depending on the functions involved. It should also be noted that each box in the block diagram and / or flowchart, and the combination of the boxes in the block diagram and / or flowchart, can be implemented using a dedicated hardware-based system that performs the specified function or operation, or can be implemented using a combination of dedicated hardware and computer instructions.

[0190] The computer-readable storage medium provided by the embodiments of the present invention may be, for example, but not limited to, an electrical, magnetic, optical, electromagnetic, infrared, or semiconductor system, device or component, or any combination thereof. More specific examples of computer-readable storage media may include, but are not limited to, an electrical connection with one or more wires, a portable computer disk, a hard disk, a random access memory (RAM), a read-only memory (ROM), an erasable programmable read-only memory (EPROM or flash memory), an optical fiber, a portable compact disk read-only memory (CD-ROM), an optical storage device, a magnetic storage device, or any suitable combination thereof. In the present invention, a computer-readable storage medium may be any tangible medium containing or storing a program that can be used by or in conjunction with an instruction execution system, device or device.

[0191] The computer-readable storage medium carries one or more programs. When the one or more programs are executed by the electronic device, the electronic device executes the method shown in the above embodiment.

[0192] The above description is merely a preferred embodiment of the present invention and an illustration of the technical principles employed. Those skilled in the art should understand that the scope of disclosure involved in the present invention is not limited to the technical solutions formed by the specific combination of the above-mentioned technical features, but also includes other technical solutions formed by any combination of the above-mentioned technical features or their equivalents without departing from the above-mentioned disclosed concepts. For example, a technical solution formed by replacing the above-mentioned features with (but not limited to) technical features with similar functions disclosed in the present invention.

Claims

1. A method for determining abnormal rotor balance state and abnormal bearing support stiffness, characterized in that: The following steps are involved: Obtaining the mass of an initial focus point of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus point and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus point is the angular position of the residual unbalance amount of the rotor after dynamic balancing; Determining a 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity; If the 1st harmonic amplitude of the rotor is greater than a set value, it is determined that the balance state of the rotor has changed and the bearing support stiffness has become abnormal; The method further comprises: Determining whether a 1st harmonic phase angle changes when the rotor rotates according to the rotor mass and the bearing support stiffness; If the 1st harmonic frequency phase angle changes, it is determined that the bearing support stiffness is abnormal.

2. The method according to claim 1, characterized in that Determining the 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity includes: The rotor's 1st harmonic amplitude is determined according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity using a first formula, wherein the first formula is: Where A is the 1-harmonic amplitude, m is the mass of the initial focus, r is the distance between the initial focus and the rotor center, Ω is the angular velocity, K is the bearing support stiffness, and M is the rotor mass.

3. The method according to claim 1, characterized in that The method further comprises: Obtaining the axis trajectory of the rotor when it rotates; If the axis trajectory is elliptical and directional, it is determined that the bearing support stiffness is abnormal.

4. The method according to claim 1, wherein The determining, based on the rotor mass and the bearing support stiffness, whether the 1st harmonic phase angle changes when the rotor rotates includes: determining a critical speed of the rotor according to the rotor mass and the bearing support stiffness; If the angular velocity is less than the critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change; If the angular velocity is greater than the critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

5. The method according to any one of claims 1 to 4, characterized in that The bearing support stiffness includes a first stiffness and a second stiffness, wherein the first stiffness is the stiffness in the horizontal direction and the second stiffness is the stiffness in the vertical direction; Determining the 1st harmonic amplitude of the rotor according to the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity includes: determining a 1st harmonic amplitude of the rotor in a horizontal direction according to the rotor mass, the first stiffness, the mass of the initial focus, the distance, and the angular velocity; The 1-fold frequency amplitude of the rotor in the vertical direction is determined according to the rotor mass, the second stiffness, the mass of the initial focus, the distance, and the angular velocity. The 1-fold frequency amplitude of the rotor includes the 1-fold frequency amplitude of the rotor in the horizontal direction and the 1-fold frequency amplitude of the rotor in the vertical direction.

6. The method according to any one of claims 1 to 4, characterized in that The bearing support stiffness includes a first stiffness and a second stiffness, wherein the first stiffness is the stiffness in the horizontal direction and the second stiffness is the stiffness in the vertical direction; The determining, based on the rotor mass and the bearing support stiffness, whether the 1st harmonic phase angle changes when the rotor rotates includes: determining a first critical speed of the rotor in a horizontal direction according to the rotor mass and the first stiffness; determining a second critical speed of the rotor in a vertical direction according to the rotor mass and the second stiffness, wherein the critical speed includes the first critical speed and the second critical speed; If the angular velocity is less than the first critical speed, determining that the 1st harmonic phase angle of the rotor during rotation does not change; If the angular velocity is greater than the second critical speed, it is determined that the 1st harmonic phase angle of the rotor during rotation changes.

7. A device for determining abnormal rotor balance state and abnormal bearing support stiffness, characterized in that: include: a data acquisition module, configured to acquire the mass of an initial focus of the rotor, the rotor mass of the rotor, the bearing support stiffness, the distance between the initial focus and the rotor center, and the angular velocity of the rotor during rotation, wherein the initial focus is the angular position of the residual unbalance amount of the rotor after dynamic balancing; an amplitude determination module, configured to determine a 1-harmonic frequency amplitude of the rotor based on the rotor mass, the bearing support stiffness, the mass of the initial focus, the distance, and the angular velocity; an abnormality judgment module, configured to determine that the balance state of the rotor has changed and the bearing support stiffness has become abnormal when the amplitude of the rotor's 1st harmonic frequency is greater than a set value; The device further comprises: a phase angle change determination module, configured to determine whether the 1st harmonic phase angle changes when the rotor rotates based on the rotor mass and the bearing support stiffness; The first bearing support stiffness abnormality judgment module is used to determine that the bearing support stiffness is abnormal when the 1st harmonic frequency phase angle changes.

8. An electronic device, characterized in that: The method comprises a memory, a processor, and a computer program stored in the memory and executable on the processor, wherein the processor implements the method according to any one of claims 1 to 6 when executing the computer program.

9. A computer-readable storage medium, characterized in that The computer-readable storage medium stores a computer program, and when the computer program is executed by a processor, the method according to any one of claims 1 to 6 is implemented.

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