JP6192413B2 - Vibration analysis method for bearing device, vibration analysis device for bearing device, and state monitoring device for rolling bearing - Google Patents

Description

  The present invention relates to a vibration analysis method for a bearing device, a vibration analysis device for a bearing device, and a state monitoring device for a rolling bearing, and in particular, a technique for analyzing vibrations of a rolling bearing and a bearing device including a housing thereof by a computer, and The present invention relates to a state monitoring device for a rolling bearing using an analysis result.

  Japanese Patent Laying-Open No. 2006-234785 (Patent Document 1) discloses an abnormality diagnosis device for a rolling bearing. In this abnormality diagnosis apparatus, frequency analysis of an electric signal from a vibration sensor is performed, and a spectrum peak larger than a reference value calculated based on the spectrum obtained by frequency analysis is extracted. Then, the frequency between the peaks and the frequency component resulting from bearing damage calculated based on the rotational speed are compared and collated, and the presence / absence and abnormal part of the rolling bearing are determined based on the collation result. (See Patent Document 1).

JP 2006-234785 A

  In the abnormality diagnosis apparatus described above, a bearing abnormality is diagnosed when the magnitude of the peak of the vibration waveform exceeds a predetermined threshold value. By the way, in order to select the threshold value for abnormality diagnosis, it is necessary to grasp in advance the vibration state at the time of abnormality. As a method of grasping the vibration state at the time of abnormality, for example, it is possible to collect vibration data at the time of abnormality by incorporating a damaged bearing into the actual machine or continuing to operate the actual machine until the bearing is damaged. It is done.

  However, such a method is difficult to apply when the equipment is large, has a long life, or is expensive. In particular, the wind power generation equipment meets the above conditions, and it is difficult to select a threshold value for determining a bearing abnormality in a state monitoring device that monitors the state of the wind power generation equipment. For this reason, in large-scale equipment such as wind power generation equipment, the threshold value for abnormality determination is determined by statistically processing the actual data collected, ignoring the differences in structure and model. Yes.

  Therefore, it is desired that a vibration state when abnormality occurs in the bearing can be analyzed in advance by a computer. If the vibration state of the bearing device can be analyzed in advance by a computer and predicted in advance, it is possible to easily set an abnormality determination threshold value for large-scale equipment such as wind power generation equipment. Further, even when a sensor for detecting the vibration of the bearing device is moved, it is possible to set a threshold value for abnormality determination without collecting data with the actual machine.

  The present invention has been made to solve such a problem, and an object of the present invention is to provide a vibration analysis method and a vibration analysis apparatus for analyzing vibrations of a rolling bearing and a bearing device including the casing by a computer. is there.

  Another object of the present invention is to provide a rolling bearing state monitoring device using an analysis result obtained by such a vibration analysis method.

  According to the present invention, a vibration analysis method for a bearing device is a vibration analysis method for a bearing device for analyzing vibrations of a bearing device including a rolling bearing and its housing by a computer, the rolling element and the raceway of the rolling bearing. The bearing device includes a step of inputting shape data of damage to the contact portion with the surface, a step of calculating a displacement between the inner and outer rings generated in the rolling bearing due to the damage, and a mode analysis program for analyzing a vibration mode of the bearing device. A rolling bearing obtained by multiplying the displacement between the inner and outer rings calculated by the step of calculating a vibration characteristic model indicating the vibration characteristics of the inner ring and the step of calculating the displacement between the inner and outer rings by a spring constant between the inner and outer rings. Calculating a vibration waveform at a predetermined position of the bearing device by giving a history of the generated excitation force to the vibration characteristic model. .

  Preferably, in the step of calculating the vibration waveform, the history of the excitation force is given to at least one point on the central axis of the rotating wheel of the rolling bearing in the vibration characteristic model. In order to consider the influence of the moment, it may be applied to a plurality of points on the central axis of the rotating wheel (for example, the inner ring).

  Preferably, the vibration analysis method of the bearing device further includes a step of determining a vibration magnitude threshold value for determining the rolling bearing as abnormal by using the vibration waveform calculated in the step of calculating the vibration waveform. Including.

  Preferably, in the step of calculating the displacement between the inner and outer rings, the displacement between the inner and outer rings generated in the rolling bearing due to damage when the rotating shaft of the rolling bearing rotates by a dynamic analysis program for performing dynamic analysis of the rolling bearing. Calculating a history.

  Preferably, the rolling bearing is a ball bearing. The step of calculating the displacement history between the inner and outer rings is performed by a contact analysis program for analyzing the contact between the rolling element of the rolling bearing and the raceway surface. A step of calculating a change in approach amount, and a step of calculating a history of displacement between the inner and outer rings generated in the rolling bearing due to the change in the approach amount when the rotating shaft of the rolling bearing rotates by a dynamic analysis program. .

  Preferably, the rolling bearing is a roller bearing. The dynamic analysis program uses a slicing method for calculating a contact load for each minute width portion obtained by dividing the contact portion between the roller and the raceway surface into a minute width along the axial direction of the roller. The vibration analysis method further includes a step of converting, for each slice, a change amount of the roller approach amount caused by the given damage. The step of calculating the history of displacement between the inner and outer wheels includes the step of calculating the history of displacement between the inner and outer wheels by a dynamic analysis program using a slice method.

  Preferably, in the step of calculating the displacement history between the inner and outer rings, the fixed ring of the rolling bearing is connected to the housing via a linear spring in the bearing radial direction of the position of the rolling element in the load range. And

  Preferably, in the step of calculating the vibration waveform, the history of the displacement between the inner and outer rings is given to the rolling elements in the load area according to the distribution of the force supported by each rolling element in the load area. .

  According to the present invention, the vibration analysis device for a bearing device is a vibration analysis device for a bearing device that analyzes vibrations of a rolling bearing and a bearing device including a casing thereof, and includes an input unit, a displacement calculation unit, A vibration characteristic calculation unit and a vibration waveform calculation unit are provided. The input unit is for inputting shape data of damage given to the contact portion between the rolling element of the rolling bearing and the raceway surface. The displacement calculation unit calculates the displacement between the inner and outer rings that occurs in the rolling bearing due to damage. The vibration characteristic calculation unit calculates a vibration characteristic model indicating the vibration characteristic of the bearing device by a mode analysis program for analyzing a vibration mode of the bearing device. The vibration waveform calculation unit calculates, by the vibration characteristic calculation unit, a history of excitation force generated in the rolling bearing, which is obtained by multiplying the displacement between the inner and outer rings calculated by the displacement calculation unit by a spring constant between the inner and outer rings. By giving the vibration characteristic model, a vibration waveform at a predetermined position of the bearing device is calculated.

  Preferably, the displacement calculation unit calculates a history of displacement between the inner and outer rings generated in the rolling bearing due to damage when the rotating shaft of the rolling bearing rotates by a dynamic analysis program for performing dynamic analysis of the rolling bearing.

  Moreover, according to this invention, the state monitoring apparatus of a rolling bearing is provided with a vibration sensor and a determination part. The vibration sensor measures the vibration of the bearing device including the rolling bearing and its housing. The determination unit determines that the rolling bearing is abnormal when the magnitude of vibration measured using the vibration sensor exceeds a predetermined threshold value. Here, the predetermined threshold value is determined using a vibration waveform calculated by a vibration analysis method for analyzing vibration of the bearing device by a computer. The vibration analysis method includes a step of inputting shape data of damage given to a contact portion between the rolling element of the rolling bearing and the raceway surface, a step of calculating a displacement between the inner and outer rings generated in the rolling bearing due to the damage, and a bearing device. The displacement between the inner and outer rings is calculated by the step of calculating the vibration characteristic model indicating the vibration characteristics of the bearing device and the step of calculating the displacement between the inner and outer rings by the mode analysis program for analyzing the vibration mode of Calculating a vibration waveform at a place where the vibration sensor is installed in the bearing device by giving the vibration characteristic model a history of the excitation force generated in the rolling bearing, which is obtained by multiplying by the spring constant.

  Preferably, in the step of calculating the displacement between the inner and outer rings, the displacement between the inner and outer rings generated in the rolling bearing due to damage when the rotating shaft of the rolling bearing rotates by a dynamic analysis program for performing dynamic analysis of the rolling bearing. Calculating a history.

  In this invention, the shape data of the damage of the bearing is input, and the displacement between the inner and outer rings generated in the rolling bearing due to the damage is calculated. Then, the history of excitation force generated in the rolling bearing obtained by multiplying the calculated displacement between the inner and outer rings by the spring constant between the inner and outer rings is given to the vibration characteristic model of the bearing device calculated by the mode analysis program. Then, a vibration waveform at a predetermined position of the bearing device (for example, a vibration sensor installation location) is calculated. Thereby, the vibration waveform of the bearing device when damage occurs inside the bearing can be predicted in advance by the computer. Therefore, according to the present invention, it is possible to appropriately determine the threshold value for determining the abnormality of the rolling bearing in the rolling bearing state monitoring device using the above prediction result.

It is the figure which showed the model of the bearing apparatus analyzed by the vibration analysis method by Embodiment 1 of this invention. FIG. 3 is a block diagram illustrating a main part of a hardware configuration of the vibration analysis apparatus according to the first embodiment. It is a functional block diagram which shows the structure of the vibration analyzer shown in FIG. 2 functionally. It is a flowchart for demonstrating the process sequence of the vibration-analysis method performed with the vibration-analysis apparatus shown in FIG. It is the figure which showed roughly the structure of the wind power generation equipment with which the state monitoring apparatus of a rolling bearing is applied. It is a functional block diagram which shows the structure of the data processor shown in FIG. 5 functionally. It is the figure which showed the vibration waveform of the bearing apparatus when abnormality has not generate | occur | produced in the bearing apparatus. It is the figure which showed the vibration waveform of the bearing apparatus seen when the surface roughness of the bearing ring of a bearing apparatus and poor lubrication generate | occur | produce. It is the figure which showed the vibration waveform of the bearing apparatus in the initial stage when peeling generate | occur | produces in the bearing ring of a bearing apparatus. It is the figure which showed the vibration waveform of the bearing apparatus seen in the last stage of peeling abnormality. Changes in the effective value of the vibration waveform of the bearing device and the effective value of the alternating current component of the envelope waveform when separation occurs on a part of the bearing ring and then the separation moves across the entire ring. FIG. It is the figure which showed the time change of the effective value of the vibration waveform of a bearing device, and the effective value of the alternating current component of an envelope waveform when the surface roughness and poor lubrication of the bearing ring of a bearing device generate | occur | produce. It is a functional block diagram which shows the other structure of a data processor functionally. It is a flowchart for demonstrating the process sequence of the vibration-analysis method performed with the vibration-analysis apparatus by a modification. 6 is a flowchart for explaining a processing procedure of a vibration analysis method executed by the vibration analysis apparatus according to the second embodiment. FIG. 10 is a functional block diagram functionally showing the configuration of a vibration analyzing apparatus according to a third embodiment. 10 is a flowchart for explaining a processing procedure of a vibration analysis method executed by the vibration analysis apparatus according to the third embodiment.

  Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings. In the drawings, the same or corresponding parts are denoted by the same reference numerals and description thereof will not be repeated.

[Embodiment 1]
FIG. 1 is a diagram showing a model of a bearing device 10 analyzed by the vibration analysis method according to Embodiment 1 of the present invention. With reference to FIG. 1, the bearing device 10 includes a rolling bearing 20 and a housing 30. In this Embodiment 1, the case where the rolling bearing 20 is a ball bearing is demonstrated. The rolling bearing 20 includes an inner ring 22, a plurality of rolling elements 24, and an outer ring 26.

  The inner ring 22 is fitted on the rotary shaft 12 and rotates integrally with the rotary shaft 12. The outer ring 26 is a fixed ring that is provided on the outer peripheral side of the inner ring 22 and is fitted into the housing 30. Each of the plurality of rolling elements 24 is a spherical ball, and is interposed between the inner ring 22 and the outer ring 26 while maintaining a distance from each other by a cage (not shown). The housing 30 is fixed to the base 40 with bolts (not shown).

  In this model, the outer ring 26 that is a fixed ring is connected to the housing 30 via linear springs kF1 to kF3 in the bearing radial direction at the position of the rolling element within the load range among the plurality of rolling elements 24. Shall. Moreover, about the coupling | bond part of the housing 30 and the base 40, mass m1, m2 shall act on the linear springs kH1, kH2 imitating bolt coupling etc., respectively.

(Description of vibration analysis method of bearing device 10)
FIG. 2 is a block diagram showing a main part of the hardware configuration of the vibration analyzing apparatus according to the first embodiment. Referring to FIG. 2, vibration analysis apparatus 100 includes an input unit 110, an interface (I / F) unit 120, a CPU (Central Processing Unit) 130, a RAM (Random Access Memory) 140, and a ROM (Read Only). Memory) 150 and an output unit 160.

  The CPU 130 implements a vibration analysis method that will be described in detail later by executing various programs stored in the ROM 150. The RAM 140 is used as a work area by the CPU 130. The ROM 150 records a program including steps of a flowchart (described later) showing the procedure of the vibration analysis method. The input unit 110 is a means for reading data from the outside, such as a keyboard, a mouse, a recording medium, and a communication device. The output unit 160 is a means for outputting a calculation result by the CPU 130 such as a display, a recording medium, or a communication device.

  FIG. 3 is a functional block diagram functionally showing the configuration of the vibration analysis apparatus 100 shown in FIG. Referring to FIG. 3 together with FIG. 1, the vibration analysis apparatus 100 includes an approach amount change amount calculation unit 205, a dynamic analysis model setting unit 210, a displacement calculation unit 220, a vibration characteristic calculation unit 230, and a vibration waveform calculation. Unit 240 and the above-described input unit 110 and output unit 160.

  The vibration prediction of the bearing device 10 by the vibration analysis device 100 is roughly divided into two parts. That is, one is that when the rotary shaft of the rolling bearing 20 rotates due to damage caused in the contact portion between the rolling element 24 of the rolling bearing 20 and the raceway surface (the outer peripheral surface of the inner ring 22 or the inner peripheral surface of the outer ring 26). A history of displacement between the inner and outer rings (between the inner ring 22 and the outer ring 26) generated in the rolling bearing 20 is predicted. The other is to predict the vibration waveform generated at the installation location of a vibration sensor (not shown) installed in the bearing device 10 by the excitation force based on the displacement generated in the rolling bearing 20 being transmitted through the housing 30. is there.

  From the input unit 110, specification data of the rolling bearing 20, data on the shape of damage to the contact portion between the rolling element 24 and the raceway surface (hereinafter also referred to as “damage data”), lubrication conditions, operating conditions (rotational speed, etc.) ), Specification data and the like of the rotary shaft 12 and the housing 30 coupled to the rolling bearing 20 are input. The input unit 110 may be a data input unit using a Web interface, a reading unit that reads data from a recording medium on which the data is recorded according to a predetermined format, or an external unit that is transmitted according to a predetermined format. The communication apparatus etc. which receive the said data which come may be sufficient.

  The approach amount change amount calculation unit 205 receives data relating to the rolling element 24 and its trajectory, and damage data from the input unit 110. Then, the approach amount change amount calculation unit 205 calculates the amount of change in the approach amount between the rolling element 24 and the raceway surface caused by the given damage by a contact analysis program for analyzing the contact between the rolling element 24 and the raceway surface. calculate. The contact analysis program calculates the contact pressure distribution of the contact portion using, for example, a finite element method (FEM), and calculates the amount of change in the approach amount between the rolling element 24 and the raceway surface according to the presence or absence of damage. Is.

  For the contact analysis, it is preferable to use an elasto-plastic analysis taking into account the plastic deformation of the contact portion. This is because when the contact portion between the rolling element 24 and the raceway surface is damaged, the surface pressure may increase to the extent that local plastic deformation occurs. In order to simplify the calculation, the approach amount change amount calculation unit 205 may calculate the amount of change in the elastic approach amount of the rolling element 24 caused by damage using an elastic analysis for the contact analysis.

  The dynamic analysis model setting unit 210 receives the various data input from the input unit 110 and receives the change amount of the approach amount calculated by the approach amount change amount calculation unit 205. Then, the dynamic analysis model setting unit 210 sets a dynamic analysis model of the rolling bearing 20 for performing dynamic analysis in consideration of the dynamic characteristics of the rolling bearing 20. Dynamic analysis is a method in which an equation of motion is established for each component of the rolling bearing 20 (inner ring 22, rolling element 24, and outer ring 26), and simultaneous ordinary differential equations are integrated along the time axis. By the analysis, it is possible to simulate in real time the interference force between the constituent elements that change every moment, the behavior of each constituent element, and the like.

  In this dynamic analysis model, an approach amount change amount calculated by the approach amount change amount calculation unit 205 is given. Each component of the rolling bearing 20 is a rigid body, and the rotating shaft 12 and the housing 30 coupled to the rolling bearing 20 are elastic bodies having a predetermined mass and vibration mode. The inertial force of the rotating body (inner ring, rolling element 24 and rotating shaft 12) and the influence of gravity acting on each component are also reflected in the model.

  The displacement calculation unit 220 uses the dynamic analysis model set by the dynamic analysis model setting unit 210 to change the approach amount between the track and the rolling element given by the damage data input from the input unit 110. A history of the displacement between the inner and outer rings generated in the rolling bearing 20 when the rolling bearing 20 rotates is calculated. More specifically, the displacement calculation unit 220 uses the dynamic analysis model to calculate the amount of approach between the rolling element 24 and the raceway surface when the rotary shaft 12 is operated according to the operation conditions input from the input unit 110. A history of displacement between the inner and outer rings generated in the rolling bearing 20 due to the change is calculated.

  On the other hand, the vibration characteristic calculation unit 230 calculates a vibration characteristic model indicating the vibration transfer characteristic of the bearing device 10 by a mode analysis program for analyzing the vibration mode of the bearing device 10. In the first embodiment, a vibration mode indicating the vibration characteristic of the bearing device 10 is calculated as a vibration characteristic model by so-called theoretical mode analysis. In the mode analysis, various vibrations are obtained by synthesizing a plurality of natural modes, and the natural modes and natural frequencies are obtained. The theoretical mode analysis is to mathematically determine what vibration mode (eigenvalue information) the structure (elastic body) has. Specifically, in the theoretical mode analysis, a model of an object (bearing device 10) is created by determining the shape, mass distribution, rigidity distribution and constraint conditions of the object, and a mass matrix and stiffness representing the mass characteristics of the model. A natural frequency and a natural mode of an object are obtained by solving a natural value and a natural value vector from a stiffness matrix representing characteristics by theoretical analysis or numerical calculation.

  The vibration characteristic calculation unit 230 receives specification data such as the shape, material density, Young's modulus, Poisson's ratio, and the like of the bearing device 10 from the input unit 110. Further, the rolling element 24 is treated as a linear spring, and the vibration characteristic calculation unit 230 has spring information for treating each of the rolling element 24 and the coupling portion (for example, bolt coupling portion) between the housing 30 and the base 40 as a linear spring. Is received from the input unit 110. And the vibration characteristic calculation part 230 calculates the vibration characteristic model (vibration mode) of the bearing apparatus 10 with a mode analysis program (theoretical mode analysis program).

  In the above vibration characteristic model, in order to reproduce the actual vibration characteristics more faithfully, only the connection surface near the bolt among the connection surfaces of the bolt connection portion (for example, the connection portion between the housing 30 and the base 40) is connected. It is good to be in the state that was done. This is because the actual bolt coupling portion is coupled with a high compressive force on the coupling surface near the bolt, and is coupled with a relatively small force on the coupling surface away from the bolt. This tendency becomes more prominent as the rigidity of the parts joined by the bolt is lower. As an example of the shape in the vicinity of the bolt to be coupled, a ring shape concentric with the rotation axis of the bolt, in which the bolt hole diameter is the inner diameter and the bolt head diameter is the outer diameter, can be used.

  The vibration waveform calculation unit 240 performs a transient response analysis using the vibration characteristic model calculated by the vibration characteristic calculation unit 230, thereby generating a vibration waveform at a specified position on the bearing device 10 (for example, a planned installation location of the vibration sensor). calculate. More specifically, the vibration waveform calculation unit 240 receives a history of displacement between the inner and outer rings that occurs in the rolling bearing 20 from the displacement calculation unit 220, and the received spring-constant between the inner and outer rings (hereinafter referred to as “bearing”). Multiplying by "spring constant"), the history of the excitation force generated in the rolling bearing 20 is calculated. Then, the vibration waveform calculation unit 240 gives a history of the excitation force to the vibration characteristic model calculated by the vibration characteristic calculation unit 230, and calculates the vibration waveform at that time.

  The bearing spring constant is calculated as follows, for example. That is, using the Hertz theory, the spring constant at the contact portion between the inner ring 22 and the rolling element 24 (referred to as “first spring constant”) and the spring constant at the contact portion between the outer ring 26 and the rolling element 24 ( (Referred to as “second spring constant”). Next, the first spring constant and the second spring constant are used as the spring constant of the series spring, and the spring constant (referred to as “rolling body spring constant”) for one rolling element 24 is calculated. And a bearing spring constant is calculated by synthesize | combining the rolling element spring constant about the rolling element in the load range.

  In the first embodiment, the history of the excitation force obtained by multiplying the displacement between the inner and outer rings by the bearing spring constant in the vibration waveform calculation unit 240 is the vibration characteristic model calculated by the vibration characteristic calculation unit 230. , At least one point on the central axis of the inner ring 22 of the rolling bearing 20 is given. As a result, a combination of the prediction of the displacement between the inner and outer rings of the rolling bearing 20 using the dynamic analysis program and the excitation force based thereon and the prediction of the vibration transfer characteristic of the bearing device 10 using the mode analysis program are combined. Vibration analysis can be performed.

  The output unit 160 outputs the vibration waveform calculated by the vibration waveform calculation unit 240. The output unit 160 may be a display for displaying the vibration waveform, writing means for writing the vibration waveform data to a recording medium according to a predetermined format, or externally transmitting the vibration waveform data according to a predetermined format. It may be a communication device or the like that transmits to.

  As described above, in the first embodiment, the history of the excitation force generated in the rolling bearing 20 is obtained by multiplying the displacement between the inner and outer rings of the rolling bearing 20 calculated using the dynamic analysis program by the bearing spring constant. And a response analysis (vibration analysis) is performed by giving the history of the calculated excitation force to the vibration characteristic model. By such a method, the inner and outer rings that are actually generated even when the excitation force generated when the rolling element passes through the damaged part is small, for example, because the damaged part shows a gradual shape change such as damage due to wear. Response analysis (vibration analysis) can be performed based on the displacement between the two.

  FIG. 4 is a flowchart for explaining the processing procedure of the vibration analysis method executed by the vibration analysis apparatus 100 shown in FIG. Referring to FIG. 4, first, vibration analysis apparatus 100 inputs data relating to rolling element 24 and its raceway (the outer peripheral surface of inner ring 22 or the inner peripheral surface of outer ring 26) and damage data given to rolling bearing 20. (Step S10).

  Next, the vibration analyzing apparatus 100 calculates a change in the approach amount between the rolling element 24 and the raceway surface caused by the damage input in step S10 in accordance with a contact analysis program prepared in advance (step S20). Next, the vibration analyzing apparatus 100 reads various data for executing dynamic analysis for the rolling bearing 20 (step S30). Specifically, the vibration analysis apparatus 100 reads data such as the specification data and operating conditions of the rolling bearing 20 and the mass and spring characteristics of the rotating shaft 12 and the housing 30 from the input unit 110, and is further calculated in step S20. Read the amount of change in approaching distance.

  Subsequently, the vibration analysis apparatus 100 sets a dynamic analysis model of the rolling bearing 20 based on the various data read in step S30. Then, the vibration analysis apparatus 100 is generated in the rolling bearing 20 by the change in the approach amount when the rotating shaft 12 is operated according to the operation condition input in step S10 according to the dynamic analysis program using the dynamic analysis model. A history of displacement between the inner and outer rings is calculated (step S40).

  Next, the vibration analysis device 100 reads various data for executing the theoretical mode analysis of the bearing device 10 (step S50). Specifically, the vibration analysis device 100 reads data such as the shape of the bearing device 10, the material density, Young's modulus, and Poisson's ratio. The vibration analysis apparatus 100 also reads spring information for handling each of the rolling elements 24 and the coupling portions (for example, bolt coupling portions) between the housing 30 and the base 40 as linear springs. These pieces of data may be read from the input unit 110 or may be previously stored as internal data.

  When each data is input in step S50, vibration analysis device 100 calculates mode information of bearing device 10 in accordance with a theoretical mode analysis program prepared in advance (step S60). Specifically, the vibration analysis device 100 calculates a vibration mode (natural frequency and natural mode) of the bearing device 10 using a theoretical mode analysis program based on each data input in step S50.

  Next, the vibration analysis device 100 reads various data for executing a transient response analysis (mode analysis method) of the bearing device 10 (step S70). Specifically, the vibration analysis apparatus 100 reads the mode information calculated in step S60, the change amount of the approach amount calculated in step S20, the history of the displacement between the inner and outer rings calculated in step S40, and the like. .

  Then, the vibration analysis device 100 calculates a vibration waveform of the bearing device 10 in accordance with a transient response analysis (mode analysis method) program prepared in advance (step S80). Specifically, the vibration analyzing apparatus 100 has the vibration mode calculated in step S60, the history of the excitation force obtained by multiplying the displacement (history) between the inner and outer rings calculated in step S40 by the bearing spring constant. By giving to at least one point on the central axis of the inner ring 22 of the bearing device 10, a vibration waveform generated in the bearing device 10 due to the displacement between the inner and outer rings calculated in step S40 is calculated.

  As described above, in the vibration analyzing apparatus 100, it is possible to simulate the vibration waveform of the bearing apparatus 10 when damage occurs inside the rolling bearing 20. Thus, the vibration analysis apparatus 100 can be used to determine a threshold value for determining a bearing abnormality in a condition monitoring system (Condition Monitoring System) for monitoring the state (abnormality) of the rolling bearing. By using the threshold value, it is possible to determine the abnormality of the rolling bearing in the state monitoring device.

  In the following, as an example, a state monitoring device for a rolling bearing in which a threshold value for determining a bearing abnormality determined using an analysis result of the vibration analysis device 100 is used, and a state monitoring device for a rolling bearing in a wind power generation facility is representative. I will explain it.

(Whole structure of wind power generation equipment)
FIG. 5 is a diagram schematically showing a configuration of a wind power generation facility to which the rolling bearing state monitoring device is applied. Referring to FIG. 5, wind power generation facility 310 includes main shaft 320, blade 330, speed increaser 340, power generator 350, and main shaft bearing device (hereinafter simply referred to as “bearing device”) 360. A vibration sensor 370 and a data processing device 380. The speed increaser 340, the generator 350, the bearing device 360, the vibration sensor 370, and the data processing device 380 are stored in the nacelle 390, and the nacelle 390 is supported by the tower 400.

  The main shaft 320 enters the nacelle 390, is connected to the input shaft of the speed increaser 340, and is rotatably supported by the bearing device 360. The main shaft 320 transmits the rotational torque generated by the blade 330 that receives wind force to the input shaft of the speed increaser 340. The blade 330 is provided at the tip of the main shaft 320 and converts wind force into rotational torque and transmits it to the main shaft 320.

  The bearing device 360 is fixed in the nacelle 390 and supports the main shaft 320 rotatably. The bearing device 360 is composed of a rolling bearing and a housing, and here, the rolling bearing is composed of a ball bearing. The vibration sensor 370 is fixed to the bearing device 360. The vibration sensor 370 detects the vibration of the bearing device 360 and outputs the detected value to the data processing device 380. The vibration sensor 370 is constituted by, for example, an acceleration sensor using a piezoelectric element.

  The speed increaser 340 is provided between the main shaft 320 and the power generator 350, and increases the rotational speed of the main shaft 320 and outputs it to the power generator 350. As an example, the speed increaser 340 is configured by a gear speed increasing mechanism including a planetary gear, an intermediate shaft, a high speed shaft, and the like. Although not specifically shown, a plurality of bearings for rotatably supporting a plurality of shafts are also provided in the speed increaser 340. The generator 350 is connected to the output shaft of the speed increaser 340 and generates electric power by the rotational torque received from the speed increaser 340. The generator 350 is constituted by, for example, an induction generator. The generator 350 is also provided with a bearing that rotatably supports the rotor.

  The data processing device 380 is provided in the nacelle 390 and receives a detection value of vibration of the bearing device 360 from the vibration sensor 370. Then, the data processing device 380 diagnoses an abnormality of the bearing device 360 using a vibration waveform of the bearing device 360 according to a method described later according to a preset program.

  FIG. 6 is a functional block diagram functionally showing the configuration of the data processing device 380 shown in FIG. Referring to FIG. 6, data processing device 380 includes high-pass filters (hereinafter referred to as “HPF (High Pass Filter)”) 410, 450, effective value calculation units 420, 460, envelope processing unit 440, A storage unit 480 and a diagnosis unit 490 are included.

  The HPF 410 receives the detection value of the vibration of the bearing device 360 from the vibration sensor 370. Then, the HPF 410 passes a signal component higher than a predetermined frequency for the received detection signal, and blocks the low frequency component. The HPF 410 is provided to remove a direct current component included in the vibration waveform of the bearing device 360. Note that the HPF 410 may be omitted if the output from the vibration sensor 370 does not include a DC component.

  The effective value calculation unit 420 receives the vibration waveform of the bearing device 360 from which the DC component is removed from the HPF 410. And the effective value calculating part 420 calculates the effective value (it is also called "RMS (Root Mean Square) value") of the vibration waveform of the bearing apparatus 360, and memorize | stores the effective value of the calculated vibration waveform in a memory | storage part. Output to 480.

  Envelope processing unit 440 receives a vibration detection value of bearing device 360 from vibration sensor 370. Envelope processing unit 440 generates an envelope waveform of the vibration waveform of bearing device 360 by performing envelope processing on the received detection signal. Note that various known methods can be applied to the envelope processing calculated by the envelope processing unit 440. As an example, the vibration waveform of the bearing device 360 measured using the vibration sensor 370 is rectified to an absolute value. By passing through a low pass filter (LPF), an envelope waveform of the vibration waveform of the bearing device 360 is generated.

  The HPF 450 receives the envelope waveform of the vibration waveform of the bearing device 360 from the envelope processing unit 440. Then, the HPF 450 passes a signal component higher than a predetermined frequency with respect to the received envelope waveform, and blocks a low frequency component. The HPF 450 is provided to remove a DC component contained in the envelope waveform and extract an AC component of the envelope waveform.

  The effective value calculator 460 receives from the HPF 450 the envelope waveform from which the DC component has been removed, that is, the AC component of the envelope waveform. Then, the effective value calculation unit 460 calculates the effective value (RMS value) of the AC component of the received envelope waveform, and outputs the calculated effective value of the AC component of the envelope waveform to the storage unit 480.

  The storage unit 480 synchronizes the effective value of the vibration waveform of the bearing device 360 calculated by the effective value calculation unit 420 with the effective value of the alternating current component of the envelope waveform calculated by the effective value calculation unit 460 from time to time. To do. The storage unit 480 is configured by, for example, a readable / writable nonvolatile memory.

  The diagnosis unit 490 reads the effective value of the vibration waveform of the bearing device 360 and the effective value of the alternating current component of the envelope waveform, which are stored in the storage unit 480 every moment, from the storage unit 480, and based on the two read effective values. Thus, the abnormality of the bearing device 360 is diagnosed. Specifically, the diagnosis unit 490 diagnoses an abnormality of the bearing device 360 based on the temporal change of the effective value of the vibration waveform of the bearing device 360 and the effective value of the AC component of the envelope waveform.

  That is, since the effective value of the vibration waveform of the bearing device 360 calculated by the effective value calculation unit 420 is the effective value of the raw vibration waveform that has not been subjected to the envelope processing, for example, separation occurs in a part of the raceway ring. However, although the increase in the value is small for the impulse-like vibration in which the amplitude increases only when the rolling element passes through the peeled portion, it occurs when the contact surface between the race and the rolling element is rough or poorly lubricated. For continuous vibrations, the value increases.

  On the other hand, the effective value of the AC component of the envelope waveform calculated by the effective value calculation unit 460 is small and increases in some cases with respect to the continuous vibration that occurs when the raceway surface is rough or poorly lubricated. Although not, the increase in value increases for impulse vibration. Therefore, by using the effective value of the vibration waveform of the bearing device 360 and the effective value of the AC component of the envelope waveform, it is possible to detect an abnormality that cannot be detected by only one of the effective values, and to realize a more accurate abnormality diagnosis. .

  7 to 10 are diagrams showing vibration waveforms of the bearing device 360 measured using the vibration sensor 370. FIG. 7 to 10 show vibration waveforms when the rotation speed of the main shaft 320 (FIG. 5) is constant.

  FIG. 7 is a diagram illustrating a vibration waveform of the bearing device 360 when no abnormality has occurred in the bearing device 360. Referring to FIG. 7, the horizontal axis indicates time, and the vertical axis is an index indicating the magnitude of vibration. In this example, the acceleration of vibration is shown as an example.

  FIG. 8 is a diagram illustrating a vibration waveform of the bearing device 360 that is seen when surface roughness or poor lubrication of the bearing ring of the bearing device 360 occurs. Referring to FIG. 8, when the raceway surface roughness or poor lubrication occurs, the acceleration increases and a state in which the acceleration increases continuously occurs. There are no noticeable peaks in the vibration waveform. Therefore, for such a vibration waveform, the effective value of the vibration waveform (output of the effective value calculation unit 420 (FIG. 6)) and the effective value of the AC component of the envelope waveform (effective) when no abnormality occurs in the bearing device 360. As compared with the output of the value calculation unit 460 (FIG. 6), the effective value of the raw vibration waveform not subjected to the envelope processing increases, and the effective value of the AC component of the envelope waveform does not increase so much.

  FIG. 9 is a diagram illustrating a vibration waveform of the bearing device 360 at an initial stage when separation occurs on the raceway of the bearing device 360. Referring to FIG. 9, the initial stage of the peeling abnormality is a state in which peeling occurs in a part of the raceway, and a large vibration is generated when the rolling element passes through the peeling portion. Vibration occurs periodically according to the rotation of the shaft. When the rolling element passes through other than the peeled portion, the increase in acceleration is small. Therefore, when such a vibration waveform is compared with the effective value of the vibration waveform and the effective value of the alternating current component of the envelope waveform when no abnormality has occurred in the bearing device 360, the effective value of the alternating current component of the envelope waveform increases. The effective value of the raw vibration waveform does not increase so much.

  FIG. 10 is a diagram illustrating a vibration waveform of the bearing device 360 that is seen at the final stage of the peeling abnormality. Referring to FIG. 10, the final stage of the separation abnormality is a state where the separation is transferred to the entire area of the raceway, and the acceleration increases as a whole compared to the initial stage of the abnormality, and the fluctuation with respect to the amplitude of the acceleration. Will weaken. Therefore, when compared with the effective value of the vibration waveform and the effective value of the alternating current component of the envelope waveform at the initial stage of the separation abnormality, the effective value of the raw vibration waveform increases, and the alternating current component of the envelope waveform increases. The effective value decreases.

  FIG. 11 shows the effective value of the vibration waveform of the bearing device 360 and the effective of the alternating current component of the envelope waveform when the separation occurs in a part of the bearing ring of the bearing device 360 and then the separation is transferred to the entire region of the bearing ring. It is the figure which showed the time change of a value. Note that FIG. 11 and FIG. 12 described below show temporal changes in each effective value when the rotation speed of the main shaft 320 is constant.

  Referring to FIG. 11, curve L1 shows a temporal change in the effective value of the vibration waveform that is not subjected to the envelope process, and curve L2 shows a temporal change in the effective value of the AC component of the envelope waveform. At time t1 before separation occurs, both the effective value (L1) of the vibration waveform and the effective value (L2) of the AC component of the envelope waveform are small. Note that the vibration waveform at time t1 is the waveform shown in FIG.

  When separation occurs in a part of the bearing ring of the bearing device 360, as described with reference to FIG. 9, the effective value (L2) of the alternating current component of the envelope waveform is greatly increased, while the vibration waveform that is not subjected to the envelope processing is increased. The effective value (L1) does not increase that much (near time t2).

  After that, when the separation is transferred to the entire area of the raceway, as described with reference to FIG. 10, the effective value (L1) of the vibration waveform not subjected to the envelope processing is greatly increased, while the effective value of the AC component of the envelope waveform is increased. (L2) decreases (near time t3).

  FIG. 12 is a diagram showing temporal changes in the effective value of the vibration waveform of the bearing device 360 and the effective value of the alternating current component of the envelope waveform when surface roughness or poor lubrication of the bearing ring of the bearing device 360 occurs. is there. Referring to FIG. 12, similarly to FIG. 11, a curve L1 indicates a temporal change in the effective value of the vibration waveform that is not subjected to the envelope processing, and a curve L2 indicates a temporal change in the effective value of the AC component of the envelope waveform. Showing change.

  At time t11 before the raceway surface roughness or lubrication failure occurs, both the effective value (L1) of the vibration waveform and the effective value (L2) of the AC component of the envelope waveform are small. The vibration waveform at time t11 is as shown in the above-described FIG.

  When surface roughness or poor lubrication of the bearing ring of the bearing device 360 occurs, as described with reference to FIG. 8, the effective value (L1) of the vibration waveform not subjected to the envelope processing increases, while the AC component of the envelope waveform There is no increase in the effective value (L2) (near time t12).

  As described above, the effective value of the vibration waveform of the bearing device 360 measured using the vibration sensor 370 and the AC component of the envelope waveform generated by performing envelope processing on the vibration waveform measured using the vibration sensor 370. By diagnosing the abnormality of the bearing device 360 based on the effective value of the above, it is possible to realize an accurate abnormality diagnosis as compared with the conventional frequency analysis technique.

  When performing such an abnormality diagnosis, it is necessary to appropriately set a vibration threshold value for performing the abnormality diagnosis. Such a threshold value is determined using the vibration analysis apparatus 100 described above. be able to. That is, the vibration analysis apparatus 100 can provide a model of the bearing apparatus 360 and also provide bearing damage data, and can predict a vibration waveform at a place where the vibration sensor 370 is installed in the bearing apparatus 360. Then, by calculating the effective value of the vibration waveform and the effective value of the AC component of the envelope waveform generated by performing envelope processing on the vibration waveform, the threshold value for abnormality determination in the state monitoring device is appropriately determined. be able to.

  Note that when the rotational speed of the main shaft 320 (FIG. 5) changes, the magnitude of vibration of the bearing device 360 changes. In general, the vibration of the bearing device 360 increases as the rotational speed of the main shaft 320 increases. Therefore, each of the effective value of the vibration waveform of the bearing device 360 and the effective value of the AC component of the envelope waveform is normalized by the rotation speed of the main shaft 320, and the abnormality diagnosis of the bearing device 360 is performed using each normalized effective value. You may make it perform.

  FIG. 13 is a functional block diagram functionally showing another configuration of the data processing apparatus. Referring to FIG. 13, data processing device 380A further includes a modified vibration degree calculating unit 430, a modified modulation degree calculating unit 470, and a speed function generating unit 500 in the configuration of data processing device 380 shown in FIG. Including.

  Speed function generation unit 500 receives a detected value of the rotational speed of main shaft 320 by rotation sensor 510 (not shown in FIG. 5). The rotation sensor 510 may output a detection value of the rotation position of the main shaft 320, and the speed function generation unit 500 may calculate the rotation speed of the main shaft 320. Then, the speed function generator 500 normalizes the effective value of the vibration waveform of the bearing device 360 calculated by the effective value calculator 420 with the rotational speed N of the main shaft 320, and the effective value. A speed function B (N) for normalizing the effective value of the alternating current component of the envelope waveform calculated by the calculation unit 460 with the rotational speed N of the main shaft 320 is generated. As an example, the speed functions A (N) and B (N) are expressed by the following equations.

A (N) = a × N ^−0.5 (1)
B (N) = b × N ^−0.5 (2)
Here, a and b are constants determined in advance by experiments or the like, and may be different values or the same values.

  The corrected vibration degree calculation unit 430 receives the effective value of the vibration waveform of the bearing device 360 from the effective value calculation unit 420 and receives the speed function A (N) from the speed function generation unit 500. Then, the corrected vibration degree calculation unit 430 uses the speed function A (N) to normalize the effective value of the vibration waveform calculated by the effective value calculation unit 420 with the rotation speed of the main shaft 320 (hereinafter referred to as “correction vibration”). Called "degree"). Specifically, using the effective value Vr of the vibration waveform calculated by the effective value calculation unit 420 and the speed function A (N), the corrected vibration degree Vr * is calculated by the following equation.

Here, Vra indicates an average value of Vr at time 0 to T.
Then, the corrected vibration degree calculation unit 430 outputs the corrected vibration degree Vr * calculated by Expression (3) to the storage unit 480.

  The modified modulation degree calculation unit 470 receives the effective value of the AC component of the envelope waveform from the effective value calculation unit 460 and receives the speed function B (N) from the speed function generation unit 500. Then, the modified modulation degree calculation unit 470 uses the speed function B (N) to normalize the effective value of the alternating current component of the envelope waveform calculated by the effective value calculation unit 460 with the rotation speed of the main shaft 320 (hereinafter, referred to as “the actual value”). (Referred to as “modified modulation degree”). Specifically, using the effective value Ve of the alternating current component of the envelope waveform and the speed function B (N) calculated by the effective value calculation unit 460, the modified modulation degree Ve * is calculated by the following equation.

  Here, Vea shows the average value of Ve in time 0-T. The modified modulation degree calculation unit 470 outputs the modified modulation degree Ve * calculated by Expression (4) to the storage unit 480.

  Then, the corrected vibration level Vr * and the corrected modulation degree Ve * stored in the storage unit 480 are read by the diagnosis unit 490 from time to time, and temporal changes in the read corrected vibration level Vr * and corrected modulation level Ve * are read. Based on this transition, the diagnosis unit 490 performs an abnormality diagnosis of the bearing device 360.

  In the above description, the rotation sensor 510 may be attached to the main shaft 320, or a bearing with a rotation sensor in which the rotation sensor 510 is incorporated in the bearing device 360 may be used for the bearing device 360.

  With such a configuration, the modified vibration degree Vr * obtained by normalizing the effective value of the vibration waveform of the bearing device 360 by the rotational speed, and the modified modulation degree Ve * obtained by normalizing the effective value of the AC component of the envelope waveform by the rotational speed. Therefore, a more accurate abnormality diagnosis is realized by removing the disturbance due to the fluctuation of the rotation speed.

  As described above, in the first embodiment, in the vibration analysis apparatus 100, damage data of the rolling bearing 20 to be analyzed is input, and damage is caused when the rotating shaft of the rolling bearing 20 is rotated by the dynamic analysis program. Thus, the displacement history between the inner and outer rings generated in the rolling bearing is calculated. Then, the history of the excitation force obtained by multiplying the calculated displacement between the inner and outer rings by the bearing spring constant is given to the vibration characteristic model of the bearing device 10 calculated by the mode analysis program. A vibration waveform at a predetermined position (for example, a vibration sensor installation location) is calculated. Thereby, the vibration waveform of the bearing device 10 when damage occurs inside the bearing can be predicted in advance. Therefore, according to the first embodiment, for example, in the state monitoring device of the rolling bearing (bearing device 360) applied to the wind power generation facility 310, the abnormality determination of the rolling bearing is performed using the prediction result. Can be appropriately determined.

  As an example, let Vr * 0 and Ve * 0 be the modified vibration degree and the modified modulation degree measured in the initial normal state of the wind power generation facility. For the determination of the occurrence of peeling described with reference to FIG. 11, the rate of increase Ie (= Ve * / Ve * 0) from the initial state of the corrected modulation exceeded the threshold CeFlake for determining the corrected modulation. Later, the occurrence of peeling is determined by confirming that the rate of increase Ir (= Vr * / Vr * 0) from the initial state of the corrected vibration exceeds the threshold CrFlake for determining the corrected vibration. Is done. In addition, regarding the determination of surface roughness and poor lubrication described with reference to FIG. 12, the increase rate of the correction vibration degree in a state where the increase rate Ie of the correction modulation degree does not exceed the threshold value CeSurf for determining the surface roughness of the correction modulation degree. By confirming that Ir has exceeded the threshold value CrSurf for determining the surface roughness of the corrected vibration, occurrence of surface roughness or poor lubrication is determined. In this case, there are four threshold values, CeFlake, CrFlake, CeSurf, and CrSurf.

  Note that the above threshold value and abnormality determination using the threshold value are merely examples, and more complicated pattern recognition may be used. Moreover, you may make it distinguish a surface roughness and poor lubrication by using a temperature sensor together. In any case, as described above, it is necessary to use a threshold value for performing abnormality determination in an increased vibration state.

  In the vibration analyzing apparatus 100, the history of the excitation force obtained by multiplying the displacement between the inner and outer rings caused by the given damage by the bearing spring constant is at least one point on the central axis of the inner ring 22 of the rolling bearing 20. Given to. As a result, a combination of the prediction of the displacement between the inner and outer rings of the rolling bearing 20 using the dynamic analysis program and the excitation force based thereon and the prediction of the vibration transfer characteristic of the bearing device 10 using the mode analysis program are combined. Vibration analysis can be performed.

[Modification]
In the above description, the mode analysis method is used for the transient response analysis when analyzing the vibration characteristics of the bearing device 10. However, a direct integration method may be used instead of the mode analysis method. The direct integration method is a method in which the calculated change in the approach amount between the rolling element and the raceway surface and the history of displacement between the inner and outer rings are given to the finite element model of the bearing device 10 for successive integration. This is effective when the vibration analysis apparatus 100 has sufficient arithmetic processing capability.

  FIG. 14 is a flowchart for explaining a processing procedure of a vibration analysis method executed by the vibration analysis apparatus 100 according to this modification. Referring to FIG. 14, this flowchart includes steps S90 to S94 instead of steps S50 to S80 in the flowchart shown in FIG.

  That is, when the history of displacement between the inner and outer rings generated in the rolling bearing 20 is calculated in step S40, the vibration analyzing apparatus 100 calculates the specification data of the bearing apparatus 10 (the shape and material density of the bearing apparatus 10, the Young's modulus, Based on the Poisson's ratio and the like), a finite element model of the bearing device 10 is calculated (step S90). Next, the vibration analysis device 100 reads various data for executing a transient response analysis (direct integration method) of the bearing device 10 (step S92). Specifically, the vibration analysis apparatus 100 reads the finite element model calculated in step S90, the change amount of the approach amount calculated in step S20, the displacement history between the inner and outer rings calculated in step S40, and the like. Include.

  Then, the vibration analysis device 100 calculates the vibration waveform of the bearing device 10 in accordance with a transient response analysis (direct integration method) program prepared in advance (step S94). Specifically, the vibration analysis apparatus 100 uses the finite element model calculated in step S90 to obtain the excitation force history obtained by multiplying the displacement (history) between the inner and outer rings calculated in step S40 by the bearing spring constant. By giving to at least one point on the central axis of the inner ring 22 of the bearing device 10 shown, a vibration waveform generated in the bearing device 10 is calculated based on the displacement history between the inner and outer rings calculated in step S40.

[Embodiment 2]
In the first embodiment and the modification thereof, the rolling bearing 20 is constituted by a ball bearing. In the second embodiment, a case where the rolling bearing 20 is constituted by a roller bearing will be described.

  When the rolling bearing 20 is constituted by a roller bearing, a displacement history between the inner and outer rings generated in the rolling bearing 20 is calculated by a dynamic analysis model using a so-called slice method. The slicing method is characterized in that the contact load is calculated for each minute width portion obtained by dividing the contact portion between the roller and the raceway surface into a minute width along the axial direction of the roller.

  FIG. 15 is a flowchart for explaining a processing procedure of a vibration analysis method executed by vibration analysis apparatus 100 according to the second embodiment. Referring to FIG. 15, first, vibration analysis apparatus 100 reads data relating to rolling element 24 and its raceway, and damage data applied to rolling bearing 20 from input unit 110 (step S110).

  Next, the vibration analysis apparatus 100 reads various data for executing the dynamic analysis (step S120). Specifically, the vibration analysis apparatus 100 reads from the input unit 110 data such as specification data of the rolling bearing 20, damage shape and operating conditions, and mass and spring characteristics of the rotating shaft 12 and the housing 30.

  When various data are read in step S120, the vibration analysis apparatus 100 changes from the damaged shape to the approach amount change amount between the roller and the raceway surface for each slice of the contact portion between the roller and the raceway surface. Conversion is performed (step S125). Here, the above conversion is performed using the load in the slice and the width of the damaged shape in the rolling direction as main variables. For this conversion, the effect of the width of the recess in the rolling direction on the relationship between the load and the amount of change in the approach amount in contact between the cylindrical objects may be examined in advance and converted into a function. Then, the vibration analyzing apparatus 100 operates the rotating shaft 12 according to the operation condition input in step S120 in accordance with the dynamic analysis program using the slice method in which the approach amount change amount in each slice is input. Then, a history of displacement between the inner and outer rings generated in the rolling bearing 20 due to the damage input in step S110 is calculated (step S130).

  The subsequent processes in steps S140 to S170 are basically the same as the processes in steps S50 to S80 shown in FIG. 4, and thus description thereof will not be repeated.

  As described above, according to the second embodiment, even when the rolling bearing 20 is constituted by a roller bearing, the vibration waveform of the bearing device 10 when the inside of the bearing is damaged can be predicted in advance. it can. As a result, in the rolling bearing state monitoring device applied to the wind power generation facility or the like, it is possible to appropriately determine a threshold value for determining the abnormality of the rolling bearing.

[Embodiment 3]
In the third embodiment, the vibration analysis apparatus calculates up to a threshold value for determining the abnormality of the rolling bearing in the rolling bearing state monitoring apparatus. That is, the vibration analyzing apparatus shown in the third embodiment determines up to a vibration threshold value for abnormality determination in the state monitoring apparatus based on the predicted vibration waveform.

  FIG. 16 is a functional block diagram functionally showing the configuration of the vibration analyzing apparatus according to the third embodiment. In the following, a representative description will be given based on the first embodiment, but the same function can be added to the second embodiment.

  Referring to FIG. 16, vibration analysis apparatus 100 </ b> A further includes an abnormal threshold setting unit 260 and a base vibration input unit 270 in the configuration of vibration analysis apparatus 100 according to the first embodiment shown in FIG. 3.

  The base vibration input unit 270 generates a base vibration waveform indicating a vibration waveform when the rolling bearing 20 is normal. As the base vibration waveform, an actual measurement value of a bearing of the same type is preferable, but an expected value from a measurement value of the same type of device may be used. A vibration waveform assumed when an abnormality occurs is obtained by adding the vibration waveform received from the vibration waveform calculation unit 240 to the base vibration waveform.

  Abnormal threshold setting unit 260 receives from vibration waveform calculation unit 240 the calculated value of the vibration waveform at the place where the vibration sensor is attached in bearing device 10. Then, the abnormal threshold value setting unit 260 uses the vibration waveform received from the vibration waveform calculation unit 240 and the base vibration waveform received from the base vibration input unit 270 to determine the magnitude of vibration for determining the rolling bearing 20 as abnormal. Determine the threshold. As an example, the abnormal threshold setting unit 260 calculates the effective value of the vibration waveform and the effective value of the alternating current component of the envelope waveform from the data of the vibration waveform assumed when an abnormality occurs, and the calculated result Based on this, the threshold value is determined.

  Although not particularly illustrated, the abnormality threshold setting unit 260 gives damage data of various sizes to the displacement calculation unit 220 and calculates a vibration waveform for each damage data to determine a threshold for abnormality determination. The value may be determined.

  FIG. 17 is a flowchart for explaining a processing procedure of a vibration analysis method executed by vibration analysis apparatus 100A according to the third embodiment. Referring to FIG. 17, this flowchart further includes step S82 in the flowchart shown in FIG.

  In the third embodiment, in step S80, the vibration waveform at the place where the vibration sensor is attached in the bearing device 10 is calculated. When the vibration waveform is calculated in step S80, the vibration analysis apparatus 100A uses the calculated vibration waveform to determine the vibration magnitude threshold for determining that the rolling bearing 20 is abnormal in the state monitoring apparatus. A value is determined (step S82).

  Although not shown in particular, the threshold value of vibration for abnormality determination in the state monitoring device is determined based on the vibration waveform predicted by the vibration analysis device in the same manner as in the second embodiment. Can do.

  As described above, according to the third embodiment, in vibration analysis apparatus 100 (100A), it is possible to determine a threshold value for determining abnormality of a rolling bearing in a rolling bearing state monitoring apparatus.

  In each of the above embodiments, a dynamic analysis is used to calculate the history of displacement between the inner and outer rings generated in the rolling bearing, and the response analysis is performed by multiplying the displacement between the inner and outer rings by the bearing spring constant. The history of excitation force given to (vibration analysis) is calculated, but to simplify the calculation, the history of excitation force is calculated based on the calculation result of static contact analysis without using dynamic analysis. It may be calculated.

  Specifically, the amount of change in the amount of approach between the rolling element 24 calculated by contact analysis and the raceway surface is defined as the geometric shape collapse amount (for example, the amount of dent) of the raceway surface, and this shape collapse amount is taken into consideration. The amount of displacement between the inner and outer rings is calculated based on a static force balance analysis of the entire rolling bearing. The value obtained by multiplying the amount of displacement between the inner and outer rings by the bearing spring constant is taken as the maximum value of the excitation force generated in the rolling bearing, and this value is the excitation during the time that the rolling element passes through the damaged part. A waveform (history) of the excitation force is calculated as the maximum value of the force. Note that various shapes such as a sine wave shape, a triangular wave shape, a trapezoidal wave shape, and a rectangular wave shape can be adopted as the waveform shape.

  Further, in each of the above embodiments, as shown in FIG. 1, the outer ring 26 that is a fixed ring is a linear spring in the bearing radial direction at the position of the rolling element within the load range among the plurality of rolling elements 24. Although it is assumed that it is connected to the housing 30 via kF1 to kF3, it may be spring-connected to the housing 30 in the bearing radial direction at the center between the rolling elements in the load range.

  In the first and second embodiments and the third embodiment based thereon, the history of the excitation force obtained by multiplying the displacement between the inner and outer rings caused by the given damage by the bearing spring constant is: Although given to at least one point on the central axis of the inner ring 22 of the rolling bearing 20, the above-mentioned is applied to the rolling elements 24 in the load range according to the distribution of the force supported by the rolling elements 24 in the load range. A history of excitation force may be given.

  Moreover, in the above, as an example, the threshold value for abnormality determination determined using the analysis result of the vibration analysis device is applied to the state monitoring device of the rolling bearing in the wind power generation facility. It is also possible to apply the present invention to, for example, a state monitoring device for a rolling bearing in a railway vehicle.

  The embodiment disclosed this time should be considered as illustrative in all points and not restrictive. The scope of the present invention is shown not by the above description of the embodiments but by the scope of claims for patent, and is intended to include meanings equivalent to the scope of claims for patent and all modifications within the scope.

  DESCRIPTION OF SYMBOLS 10 Bearing apparatus, 12 Rotating shaft, 20 Rolling bearing, 22 Inner ring, 24 Rolling element, 26 Outer ring, 30 Housing, 40 Base, 100, 100A Vibration analysis apparatus, 110 Input part, 120 I / F part, 130 CPU, 140 RAM , 150 ROM, 160 output unit, 205 approach amount change amount calculation unit, 210, 210A dynamic analysis model setting unit, 220 displacement calculation unit, 230, 250 vibration characteristic calculation unit, 240, 240A vibration waveform calculation unit, 260 abnormal Threshold setting unit, 270 base vibration input unit, 310 wind power generation facility, 320 main shaft, 330 blade, 340 speed increaser, 350 generator, 360 bearing, 370 vibration sensor, 380, 380A data processing device, 390 nacelle, 400 tower 410,450 HPF, 420,460 effective Calculation unit, 430 fix the vibrating calculator, 440 envelope processing unit, 470 modify the modulation degree calculation unit, 480 memory unit, 490 diagnostic unit, 500 speed function generator, 510 rotation sensor.

Claims (12)

A vibration analysis method for a bearing device for analyzing vibrations of a bearing device including a rolling bearing and its housing by a computer,
Inputting shape data of damage to the contact portion between the rolling element and the raceway of the rolling bearing;
Calculating a displacement between an inner ring and an outer ring of the rolling bearing, which occurs in the rolling bearing due to the damage;
A step of calculating a vibration characteristic model indicating a vibration characteristic of the bearing device by a mode analysis program for analyzing a vibration mode of the bearing device;
By giving the vibration characteristic model a history of excitation force generated in the rolling bearing obtained by multiplying the displacement calculated by the step of calculating the displacement by a spring constant between the inner ring and the outer ring. Calculating a vibration waveform at a predetermined position of the bearing device.   2. The vibration of the bearing device according to claim 1, wherein in the step of calculating the vibration waveform, the history of the excitation force is given to at least one point on a central axis of a rotating wheel of the rolling bearing in the vibration characteristic model. analysis method.   2. The bearing according to claim 1, further comprising a step of determining a vibration magnitude threshold value for determining that the rolling bearing is abnormal using the vibration waveform calculated in the step of calculating the vibration waveform. Device vibration analysis method.   The step of calculating the displacement includes a step of calculating a history of the displacement generated in the rolling bearing due to the damage when a rotating shaft of the rolling bearing is rotated by a dynamic analysis program for performing a dynamic analysis of the rolling bearing. The vibration analysis method for a bearing device according to claim 1, further comprising: The rolling bearing is a ball bearing,
Calculating the displacement history,
Calculating a change in the amount of approach between the rolling element and the raceway surface caused by the given damage by a contact analysis program for analyzing contact between the rolling element of the rolling bearing and the raceway surface;
And calculating a history of the displacement generated in the rolling bearing due to a change in the approach amount when a rotating shaft of the rolling bearing is rotated by the dynamic analysis program. Vibration analysis method. The rolling bearing is a roller bearing,
The dynamic analysis program uses a slicing method for calculating a contact load for each minute width portion obtained by dividing a contact portion between a roller and a raceway surface into a minute width along the axial direction of the roller,
The vibration analysis method further includes a step of converting, for each slice, a change amount of the approach amount of the roller caused by the given damage,
5. The vibration analysis method for a bearing device according to claim 4, wherein the step of calculating the displacement history includes a step of calculating the displacement history by the dynamic analysis program using the slice method.   In the step of calculating the history of displacement, the fixed ring of the rolling bearing is connected to the housing via a linear spring in a bearing radial direction at a position of a rolling element in a load range. Item 5. The vibration analysis method for a bearing device according to Item 4.   5. The step of calculating the vibration waveform, wherein the displacement history is given to a rolling element in a load range according to a distribution of a force supported by each rolling element in the load range. Vibration analysis method for a bearing device. A vibration analysis device for a bearing device that analyzes vibrations of a rolling bearing and a bearing device including a casing thereof,
An input unit for inputting shape data of damage given to a contact portion between the rolling element and the raceway surface of the rolling bearing;
A displacement calculating unit for calculating a displacement between the inner ring and the outer ring of the rolling bearing, which occurs in the rolling bearing due to the damage;
A vibration characteristic calculation unit that calculates a vibration characteristic model indicating a vibration characteristic of the bearing device by a mode analysis program that analyzes a vibration mode of the bearing device;
Vibration calculated by the vibration characteristic calculation unit, which is obtained by multiplying the displacement calculated by the displacement calculation unit by a spring constant between the inner ring and the outer ring and generated in the rolling bearing. A vibration analysis device for a bearing device, comprising: a vibration waveform calculation unit that calculates a vibration waveform at a predetermined position of the bearing device by giving the characteristic model.   The displacement calculation unit calculates a history of the displacement that occurs in the rolling bearing due to the damage when a rotating shaft of the rolling bearing rotates by a dynamic analysis program that performs dynamic analysis of the rolling bearing. 9. A vibration analysis device for a bearing device according to item 9. A vibration sensor for measuring vibrations of a bearing device including a rolling bearing and a housing thereof;
A determination unit that determines that the rolling bearing is abnormal when the magnitude of vibration measured using the vibration sensor exceeds a predetermined threshold;
The predetermined threshold is determined using a vibration waveform calculated by a vibration analysis method for analyzing vibration of the bearing device by a computer,
The vibration analysis method includes:
Inputting shape data of damage to the contact portion between the rolling element and the raceway of the rolling bearing;
Calculating a displacement between an inner ring and an outer ring of the rolling bearing, which occurs in the rolling bearing due to the damage;
A step of calculating a vibration characteristic model indicating a vibration characteristic of the bearing device by a mode analysis program for analyzing a vibration mode of the bearing device;
By giving the vibration characteristic model a history of excitation force generated in the rolling bearing obtained by multiplying the displacement calculated by the step of calculating the displacement by a spring constant between the inner ring and the outer ring. And a step of calculating a vibration waveform at a place where the vibration sensor is installed in the bearing device.   The step of calculating the displacement includes a step of calculating a history of the displacement generated in the rolling bearing due to the damage when a rotating shaft of the rolling bearing is rotated by a dynamic analysis program for performing a dynamic analysis of the rolling bearing. The rolling bearing state monitoring device according to claim 11, comprising:

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