CN116256173A - Bearing stress state measuring method and related device based on resonance attenuation method - Google Patents
Bearing stress state measuring method and related device based on resonance attenuation method Download PDFInfo
- Publication number
- CN116256173A CN116256173A CN202310094985.8A CN202310094985A CN116256173A CN 116256173 A CN116256173 A CN 116256173A CN 202310094985 A CN202310094985 A CN 202310094985A CN 116256173 A CN116256173 A CN 116256173A
- Authority
- CN
- China
- Prior art keywords
- bearing
- stress state
- nonlinear
- time
- frequency
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Pending
Links
- 238000000034 method Methods 0.000 title claims abstract description 65
- 230000004044 response Effects 0.000 claims abstract description 42
- 238000012360 testing method Methods 0.000 claims abstract description 35
- 238000004458 analytical method Methods 0.000 claims abstract description 32
- 238000005259 measurement Methods 0.000 claims abstract description 19
- 238000013507 mapping Methods 0.000 claims abstract description 16
- 230000001052 transient effect Effects 0.000 claims abstract description 16
- 238000004590 computer program Methods 0.000 claims description 20
- 238000005096 rolling process Methods 0.000 claims description 17
- 230000006870 function Effects 0.000 claims description 14
- 230000006399 behavior Effects 0.000 claims description 12
- 238000004364 calculation method Methods 0.000 claims description 10
- 229910000976 Electrical steel Inorganic materials 0.000 claims description 9
- 238000006073 displacement reaction Methods 0.000 claims description 7
- 230000005284 excitation Effects 0.000 claims description 7
- 230000003068 static effect Effects 0.000 claims description 6
- 238000011160 research Methods 0.000 claims description 5
- 238000003860 storage Methods 0.000 claims description 4
- 238000004422 calculation algorithm Methods 0.000 claims description 3
- 238000010276 construction Methods 0.000 claims description 3
- 238000009499 grossing Methods 0.000 claims description 3
- 230000009466 transformation Effects 0.000 claims description 3
- 108010076504 Protein Sorting Signals Proteins 0.000 claims description 2
- 230000002457 bidirectional effect Effects 0.000 claims description 2
- 238000013016 damping Methods 0.000 claims description 2
- 230000005484 gravity Effects 0.000 claims description 2
- 239000011159 matrix material Substances 0.000 claims 2
- 230000001133 acceleration Effects 0.000 claims 1
- 230000008569 process Effects 0.000 abstract description 7
- 230000035882 stress Effects 0.000 description 48
- 238000010586 diagram Methods 0.000 description 9
- 230000008859 change Effects 0.000 description 4
- XEEYBQQBJWHFJM-UHFFFAOYSA-N Iron Chemical group [Fe] XEEYBQQBJWHFJM-UHFFFAOYSA-N 0.000 description 3
- 230000008878 coupling Effects 0.000 description 3
- 238000010168 coupling process Methods 0.000 description 3
- 238000005859 coupling reaction Methods 0.000 description 3
- 238000001514 detection method Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 238000011897 real-time detection Methods 0.000 description 3
- 230000009471 action Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 230000007423 decrease Effects 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000004048 modification Effects 0.000 description 2
- 238000012986 modification Methods 0.000 description 2
- 230000009022 nonlinear effect Effects 0.000 description 2
- 238000012545 processing Methods 0.000 description 2
- 238000003491 array Methods 0.000 description 1
- 230000005540 biological transmission Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 125000004122 cyclic group Chemical group 0.000 description 1
- 230000006355 external stress Effects 0.000 description 1
- 230000006872 improvement Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000000691 measurement method Methods 0.000 description 1
- 230000003287 optical effect Effects 0.000 description 1
- 230000010355 oscillation Effects 0.000 description 1
- 238000004088 simulation Methods 0.000 description 1
Images
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
- G01M13/04—Bearings
- G01M13/045—Acoustic or vibration analysis
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F30/00—Computer-aided design [CAD]
- G06F30/20—Design optimisation, verification or simulation
-
- G—PHYSICS
- G06—COMPUTING; CALCULATING OR COUNTING
- G06F—ELECTRIC DIGITAL DATA PROCESSING
- G06F2119/00—Details relating to the type or aim of the analysis or the optimisation
- G06F2119/14—Force analysis or force optimisation, e.g. static or dynamic forces
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T90/00—Enabling technologies or technologies with a potential or indirect contribution to GHG emissions mitigation
Landscapes
- Physics & Mathematics (AREA)
- Engineering & Computer Science (AREA)
- General Physics & Mathematics (AREA)
- Theoretical Computer Science (AREA)
- Acoustics & Sound (AREA)
- Computer Hardware Design (AREA)
- Evolutionary Computation (AREA)
- Geometry (AREA)
- General Engineering & Computer Science (AREA)
- Testing Of Devices, Machine Parts, Or Other Structures Thereof (AREA)
Abstract
The invention discloses a bearing stress state measuring method based on a resonance attenuation method and a related device. And acquiring an attenuation response curve by a resonance attenuation method in a nonlinear parameter identification method, acquiring instantaneous frequency and envelope amplitude based on a transient time-frequency signal analysis method, and further identifying a main curve from a measured bearing-main shaft system. And establishing a quasi-static model of the bearing, acquiring a mapping relation between the bearing stress state and the nonlinear time-varying rigidity, and effectively and accurately detecting the bearing external load state through multiple tests on the nonlinear rigidity in the actual running process of the bearing system. The invention is suitable for the assembly angle contact ball bearings with different types and is suitable for the accurate measurement work of the bearing stress state.
Description
Technical Field
The invention belongs to the technical field of bearing state measurement, and relates to a bearing stress state measurement method based on a resonance attenuation method and a related device.
Background
Bearings have been used in the aspects of the modern industry as one of the important basic components in the mechanical field. A mechanical device generates various acting forces in the actual operation process. Bearings in mechanical devices often function to support and transmit forces and torques during operation, and the stress conditions are relatively complex and may be accompanied by vibration and noise. Therefore, the bearing load and the stress state of the bearing need to be tested, so that the problem of bearing noise of mechanical equipment can be solved, the mechanical operation precision is improved, and the production benefit of the equipment is improved.
For the existing bearing stress state research, most of theoretical research and simulation analysis and calculation are performed; when the bearing stress state is to be actually measured, direct measurement is often carried out by adopting various force sensors, the technical principle is simple, and the measurement accuracy is limited. For bearing components moving continuously at any time, the stress state of the bearing under the actual working condition is required to be accurately measured, and the prior art method is difficult to realize. Therefore, under real conditions, it becomes increasingly important to measure the exact stress conditions during the operation of the bearing.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a bearing stress state measuring method and a related device based on a resonance attenuation method, which are used for researching the evolution of the bearing external stress state under the real working condition in the actual running process of a bearing, indirectly acquiring the actual stress state of the bearing based on the measured rigidity and a theoretical analysis result, and then completing the calculation and analysis of the nonlinear non-time-varying rigidity behavior of the bearing to measure the accurate stress state of the bearing.
In order to achieve the above purpose, the invention is realized by adopting the following technical scheme:
in a first aspect, the present invention provides a method for measuring a stress state of a bearing based on a resonance attenuation method, including the steps of:
exciting main resonance response behaviors of the test bearing-main shaft system;
acquiring an attenuation response curve of a nonlinear system in a main resonance region, and acquiring the instantaneous frequency and envelope amplitude of a tested bearing-spindle system by a transient time-frequency signal analysis method to obtain a trunk curve of the tested bearing-spindle system in a main resonance response interval range;
analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
and (3) establishing a bearing quasi-static model, obtaining a mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the stress state of the bearing based on nonlinear time-varying rigidity measurement.
In a second aspect, the present invention provides a bearing stress state measurement system based on a resonance attenuation method, including:
the corresponding behavior excitation module is used for exciting the main resonance response behavior of the test bearing-spindle system;
the main curve calculation module is used for acquiring an attenuation response curve of the nonlinear system in the main resonance region, acquiring the instantaneous frequency and the envelope amplitude of the test bearing-main shaft system through a transient time-frequency signal analysis method, and acquiring a main curve of the tested bearing-main shaft system in the main resonance response interval range;
the rigidity calculation module is used for analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the bearing stress state based on nonlinear time-varying rigidity measurement.
In a third aspect, the present invention provides a bearing stress state measuring device based on a resonance attenuation method, including:
the electromagnetic loading device is arranged on the supporting seat; the main shaft to be measured is arranged on the electromagnetic loading device; the front end supporting ball bearing, the hydraulic loading device and the rear end supporting ball bearing are sleeved on the main shaft; the main shaft is connected with the motor through a coupler;
the electromagnetic loading device comprises cylindrical silicon steel sheets, a plurality of stator cores are uniformly arranged on the side surfaces of the silicon steel sheets along the circumferential direction, a coil is wound on each stator core, and the coils and the stator cores form an electromagnet; the coil is connected with the controller through a power amplifier, and a plurality of eddy current displacement sensors are further arranged on the side face of the main shaft;
and the hydraulic loading devices are arranged at two sides of the electromagnetic loading device.
In a fourth aspect, the present invention provides a computer device comprising a memory, a processor and a computer program stored in the memory and executable on the processor, the processor implementing the steps of the method as described above when executing the computer program.
In a fifth aspect, the present invention provides a computer readable storage medium storing a computer program which, when executed by a processor, implements the steps of a method as described above.
Compared with the prior art, the invention has the following beneficial effects:
the loading mode of the main shaft system adopts non-contact electromagnetic loading, so that redundant information input to the main shaft system due to contact friction is avoided; when the external load is larger, the nonlinear rigidity characteristic of the bearing plays a leading role, and the nonlinear time-varying characteristic of the rigidity of the bearing is fully considered in the calculation and analysis process; the invention adopts a resonance attenuation method in a nonlinear parameter identification method, estimates instantaneous amplitude, frequency and damping from attenuation response caused by steady-state oscillation, can accurately identify a main curve of a bearing nonlinear system, and accurately acquires the instantaneous frequency and amplitude in the bearing system; because a certain mapping relation exists between the bearing stress state and the nonlinear rigidity of the bearing, the measured value and the theoretical calculated value have better consistency, and the invention constructs a quasi-static model of the bearing, so that the accurate bearing stress state can be calculated.
The invention discloses a bearing stress state measuring method and device based on a resonance attenuation method. The precision of the backup rotation is important. The invention considers the nonlinear non-time-varying system rigidity in the bearing operation process under the real working condition. The accurate detection of the bearing stress state is beneficial to prolonging the bearing operation life and improving the rotation precision of mechanical equipment. The traditional detection method of the bearing stress state usually adopts a force sensor to directly measure, the technical principle is simple, the detection precision is limited, the measurement error is relatively large for moving parts such as the bearing, and the measurement of the bearing stress state under the actual working condition state cannot be realized. The invention adopts a resonance attenuation method, can extract a main curve of the bearing nonlinear system, accurately acquire the frequency and the amplitude in the bearing system, and calculate the accurate stress state based on the mapping relation between the nonlinear time-invariant rigidity and the stress state of the bearing system.
Drawings
For a clearer description of the technical solutions of the embodiments of the present invention, the drawings that are needed in the embodiments will be briefly described below, it being understood that the following drawings only illustrate some embodiments of the present invention and should not be considered as limiting the scope, and other related drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.
FIG. 1 is a flow chart of the method of the present invention.
Fig. 2 is a schematic diagram of the system of the present invention.
Fig. 3 is a schematic diagram showing the contact load of the rolling element at the lowest end of the bearing and the inner ring along with the change of the rotating speed.
FIG. 4 is a graphical representation of radial stiffness as a function of radial force.
Fig. 5 is a graphical representation of radial stiffness as a function of radial displacement.
Fig. 6 is a technical roadmap of a method for measuring the stress state of a bearing.
Fig. 7 is a diagram showing an embodiment of the resonance attenuation method.
Fig. 8 is a schematic diagram of a test platform of a bearing stress state measuring device.
Fig. 9 is a schematic structural view of a non-contact electromagnetic loading device.
Fig. 10 is a schematic circuit diagram of a non-contact electromagnetic loading device.
Wherein: the device comprises a motor 1, a main shaft 2, a coupler 3, a front end supporting ball bearing 4, a hydraulic loading device 5, a rear end supporting ball bearing 6, an electromagnetic loading device 7, a coil 8, a vortex displacement sensor 9, a supporting seat 10, a silicon steel sheet 11, an electromagnet 12, a power amplifier 13 and a controller 14.
Detailed Description
For the purpose of making the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention, and it is apparent that the described embodiments are some embodiments of the present invention, but not all embodiments of the present invention. The components of the embodiments of the present invention generally described and illustrated in the figures herein may be arranged and designed in a wide variety of different configurations.
Thus, the following detailed description of the embodiments of the invention, as presented in the figures, is not intended to limit the scope of the invention, as claimed, but is merely representative of selected embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
It should be noted that: like reference numerals and letters denote like items in the following figures, and thus once an item is defined in one figure, no further definition or explanation thereof is necessary in the following figures.
In the description of the embodiments of the present invention, it should be noted that, if the terms "upper," "lower," "horizontal," "inner," and the like indicate an azimuth or a positional relationship based on the azimuth or the positional relationship shown in the drawings, or the azimuth or the positional relationship in which the inventive product is conventionally put in use, it is merely for convenience of describing the present invention and simplifying the description, and does not indicate or imply that the apparatus or element to be referred to must have a specific azimuth, be configured and operated in a specific azimuth, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used merely to distinguish between descriptions and should not be construed as indicating or implying relative importance.
Furthermore, the term "horizontal" if present does not mean that the component is required to be absolutely horizontal, but may be slightly inclined. As "horizontal" merely means that its direction is more horizontal than "vertical", and does not mean that the structure must be perfectly horizontal, but may be slightly inclined.
In the description of the embodiments of the present invention, it should also be noted that, unless explicitly specified and limited otherwise, the terms "disposed," "mounted," "connected," and "connected" should be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention can be understood by those of ordinary skill in the art according to the specific circumstances.
The invention is described in further detail below with reference to the attached drawing figures:
referring to fig. 1, the embodiment of the invention discloses a bearing stress state measuring method based on a resonance attenuation method, which comprises the following steps:
s1, exciting main resonance response behaviors of the test bearing-main shaft system, and particularly loading the test bearing-main shaft system in a non-contact electromagnetic loading mode.
S2, acquiring an attenuation response curve of the nonlinear system in a main resonance region, and acquiring the instantaneous frequency and envelope amplitude of the tested bearing-spindle system by a transient time-frequency signal analysis method to obtain a trunk curve of the tested bearing-spindle system in a main resonance response interval range;
the transient time-frequency signal analysis method comprises a Hilbert transient time-frequency signal analysis method or a wavelet transformation transient time-frequency signal analysis method.
The acquiring the instantaneous frequency of the test bearing-spindle system includes:
detecting zero crossing points of the response signals, and determining crossing time by using a standard deviation algorithm; smoothing around the intersection point using a moving average filter; after determining the crossing time sequence, calculating an estimated value of the instantaneous frequency at the next moment of any crossing point; constructing a moving average filter, and calculating a final instantaneous frequency:
where f () represents the instantaneous frequency,
represents the crossover time, N represents the order of the moving average filter, +.>
Represents the instantaneous frequency at the crossing, < >>
Another crossing time is represented, i represents any crossing point, and j represents another crossing point.
The acquiring envelope amplitude of the test bearing-spindle system includes:
extracting a response envelope by tracking signal peaks within each individual zero crossing time interval; at each interval
The maximum absolute value of the internal search signal X and the corresponding time of occurrence thereof>
wherein ,
represents signal peak, X (t) represents signal sequence,>
representing a time interval; while calculating the instantaneous frequency, the instantaneous amplitude is estimated from the interpolation function.
The trunk curve is obtained by adopting the following method:
the backbone curve is a function of frequency and amplitude parameterization over time, pairing the sequence a (t) and the frequency f (t) correspondingly:
where A () represents the instantaneous amplitude, Γ (t) is the digital sequence
The polynomial interpolation function of (2) represents the envelope of the decay time signal.
S3, analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
and S4, establishing a bearing quasi-statics model, obtaining a mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the stress state of the bearing based on nonlinear time-varying rigidity measurement.
The specific analysis flow of the nonlinear rigidity and the bearing stress state is as follows:
for a bearing in a static state, the nonlinear relationship between load and deformation is determined by fractional contact stiffness and contact angle between rolling elements and raceways in the bearing. For the bearing under high speed, the contact angles between the rolling element and the rolling inner and outer rings in the rolling sports in the bearing are not equal any more under the action of high-speed centrifugal force, so that the contact rigidity between the rolling element and the inner and outer raceways can not be subjected to simple superposition operation, and the typical geometrical nonlinearity is shown. At this time, the radial stiffness calculation expression of the bearing is as follows:
wherein ,αik and αok Contact angles of the rolling bodies and the inner and outer raceways are respectively; k (k) ik and kok The contact stiffness of the rolling bodies with the inner and outer raceways.
The nonlinear stiffness characteristic of the bearing-rotor system can be embodied under (cyclic) external load excitation, so that the stress state of the bearing is calculated by adopting a bidirectional sweep frequency analysis method for researching the nonlinear vibration response of the rotor system.
At this time, the external force F applied to the bearing-rotor system includes static acting force and dynamic sweep force at the shaft end besides gravity, and the expression of the external force applied to the bearing is:
wherein f is the shaft end sweep frequency force; omega is the frequency of the shaft end sweep force;
is a static radial force at the shaft end.
As shown in fig. 2, an embodiment of the present invention discloses a bearing stress state measurement system based on a resonance attenuation method, including:
the corresponding behavior excitation module is used for exciting the main resonance response behavior of the test bearing-spindle system;
the main curve calculation module is used for acquiring an attenuation response curve of the nonlinear system in the main resonance region, acquiring the instantaneous frequency and the envelope amplitude of the test bearing-main shaft system through a transient time-frequency signal analysis method, and acquiring a main curve of the tested bearing-main shaft system in the main resonance response interval range;
the rigidity calculation module is used for analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the bearing stress state based on nonlinear time-varying rigidity measurement. The principle of the invention is as follows:
the principle of the invention is as follows:
firstly, loading a test bearing-main shaft system in a non-contact electromagnetic loading mode; secondly, acquiring an attenuation response curve of a nonlinear system in a main resonance region by a nonlinear parameter identification method, acquiring the instantaneous frequency and envelope amplitude of a test bearing-spindle system by a transient time-frequency signal analysis method such as Hilbert or wavelet transformation, further identifying a main curve (amplitude-frequency response curve) of the test bearing-spindle system in a main resonance response interval range, and calculating the nonlinear (non-time-varying) rigidity of a tested bearing by a nonlinear modal analysis method; and finally, establishing a bearing quasi-statics model, and obtaining a mapping relation between the nonlinear (time-invariant) rigidity of the tested bearing and the stress state of the tested bearing, so as to realize the test of the bearing stress state based on nonlinear time-invariant rigidity measurement.
In the actual running state of the bearing, the bearing-rotor system is subjected to load and deformation to show a high nonlinear relation due to the fractional stiffness generated by Hertz contact in the bearing and the geometric nonlinear effect generated by the centrifugal force of the rolling body, and the stiffness of the rotor system shows nonlinear time-varying characteristics. The invention realizes real-time detection of bearing stress state by carrying out multiple tests on the nonlinear rigidity of the bearing in a real service state.
In practical engineering applications, rolling bearings are usually subjected to rotational movements, which require the transmission of forces and torques from mechanical devices. The bearing is stressed in a complex manner, and vibration and noise may be generated during the running process. Meanwhile, the bearing stress has a great influence on the dynamic performance, namely the stress state of the bearing can be changed along with the working condition and the thermal deformation factor, so that the bearing needs to be accurately measured and accurately detected on line. Taking the bottommost rolling element of the angular contact ball bearing as an example, fig. 3 is a schematic diagram of the contact load of the rolling element and the inner ring along with the change of the rotation speed when the bearing operates.
For a bearing-rotor system with good pre-tightening condition, the bearing-rotor system is loaded and deformed by virtue of the fractional stiffness generated by Hertz contact in the bearing and the geometric nonlinear effect generated by the centrifugal force of rolling bodies, so that the bearing-rotor system has a high nonlinear relation, and the stiffness of the rotor system has nonlinear time-varying characteristics. When the external load is relatively large, the nonlinear stiffness characteristic of the load gradually plays a dominant role.
In the actual running process of the bearing, different nonlinear stiffness effects can be displayed under the action of different external loads and rotating speeds. It may exhibit a "soft spring effect" in which the system stiffness decreases with increasing external load, or a "firm spring effect" in which the system stiffness decreases with increasing external load. The bearing rigidity and the loading condition have a mapping relation, and fig. 4 and 5 are schematic diagrams of radial rigidity of the bearing along with radial force and radial displacement, which show the hard rigidity characteristic of the bearing.
As shown in fig. 6, fig. 6 is an overall technical roadmap of the invention. According to the invention, on one hand, through main resonance response research, a nonlinear parameter identification method is adopted to obtain an attenuation curve in a main resonance region, hilbert or wavelet change is used to identify a main curve of a test bearing-main shaft system, and a nonlinear modal analysis method is used to calculate nonlinear time-varying rigidity of a tested bearing. On the other hand, the mapping relation between the nonlinear rigidity and the stress state is obtained by establishing a quasi-statics model of the bearing. And finally, calculating an accurate bearing external loading state based on the mapping relation, and realizing real-time detection of the bearing loading state.
Meanwhile, the invention also constructs a set of measuring device for the external loading state of the bearing, and the device comprises 6 parts of an electromagnetic loading platform, a hydraulic loading platform, a measured bearing system, a supporting main shaft system, a driving system and a measuring system.
As shown in fig. 7, fig. 7 is an embodiment diagram of a main resonance response identification study of a test bearing-spindle system based on a resonance decay method. First, the attenuation response needs to be obtained: based on a resonance attenuation method in a nonlinear parameter identification method, a normal force mode distribution method is needed to be used, a reasonable force distribution mode is estimated, undamped natural frequency and normal vibration mode of a tested system are extracted by exciting the mode of the tested bearing system, then harmonic excitation is used for a system under related frequency, nonlinearity of a system structure is activated, attenuation is generated correspondingly, and an attenuation response curve in a main resonance area can be obtained.
The transient time-frequency signal analysis method such as Hilbert or wavelet change is adopted to obtain the transient frequency and envelope amplitude of the test bearing-spindle system.
Acquiring instantaneous frequency: zero crossings of the response signal are detected and a standard deviation algorithm is used to determine the crossing time. Smoothing around the intersection is performed using a suitable moving average filter. Once the crossover time series is determined, an estimate of the instantaneous frequency at the next time of any crossover point can be calculated. A moving average filter is constructed to calculate the final instantaneous frequency, which is defined as follows:
the moving average filter can effectively reduce random noise and can maintain clear step response of the frame. The filter order is selected one by one according to the noise level present in the signal.
Acquiring instantaneous amplitude: the response envelope is extracted by tracking the signal peak in each individual zero crossing time interval to obtain the decay response instantaneous amplitude. At each interval
The maximum absolute value of the internal search signal X and the corresponding time of occurrence thereof>
Is defined by the use of the equation:
defining Γ (t) as a digital sequence
A polynomial interpolation function of (c) defining an envelope of the decay time signal. While calculating the instantaneous frequency, the instantaneous amplitude is estimated from the interpolation function.
The trunk curve can be correspondingly paired with the sequences a (t) and f (t) as a function of frequency and amplitude parameterization over time, and the trunk curve is obtained.
Calculating the bearing stress state: based on an amplitude-frequency response curve of the nonlinear system, a bearing quasi-statics model is established, and a mapping relation between the nonlinear rigidity of the tested bearing system and the stress state of the tested bearing system is obtained. And calculating the stress state of the bearing based on the mapping relation between the bearing stress state and the nonlinear time-varying rigidity of the bearing, so as to realize the real-time detection of the external load of the bearing.
As shown in fig. 8, an embodiment of the present invention provides a bearing stress state measuring device based on a resonance attenuation method, which includes a supporting seat 10, an electromagnetic loading device 7 and a hydraulic loading device 5.
The electromagnetic loading device 7 is arranged on the supporting seat 10; the main shaft 2 to be measured is arranged on the electromagnetic loading device 7; the main shaft 2 is sleeved with a front end supporting ball bearing 4, a hydraulic loading device 5 and a rear end supporting ball bearing 6, and the hydraulic loading device is arranged on two sides of an electromagnetic loading device 7. The main shaft 2 is connected with the motor 1 through a coupling 3.
As shown in fig. 9, the electromagnetic loading device 7 includes a cylindrical silicon steel sheet 11, and a plurality of stator cores are uniformly arranged on the side surface of the silicon steel sheet 11 along the circumferential direction, and each stator core is wound with a coil 8, and the coils 8 and the stator cores form an electromagnet 12.
As shown in fig. 10, fig. 10 is a schematic circuit diagram of a non-contact electromagnetic loading device, a coil 8 is connected with a controller 14 through a power amplifier 13, and a plurality of eddy current displacement sensors 9 are further arranged on the side surface of the main shaft 2.
The working principle of the measuring device is as follows:
the electromagnetic loading is a non-contact loading mode, and the control of loading frequency and load can be realized through the external controller 14, so that the excitation of the main resonance response behavior of the test bearing-main shaft system is realized. The non-contact electromagnetic hardware is an electromagnetic loading platform, and the electromagnetic loading platform comprises an embedded eddy current displacement sensor 9, a coil 8 and the like; the software system includes an experimental software platform, an operator interface, and a controller 14, among others. The electromagnetic loading device 7 is similar to the electromagnetic bearing in structure, and mainly comprises a silicon steel sheet 11, a stator iron core and a coil 8 wound on the stator iron core, wherein the coils 8 on every two adjacent magnetic poles are connected in series to form a magnetic pole pair, and when current is introduced into the coils 8, a closed magnetic circuit is generated among the silicon steel sheet 11, the iron core and an air gap, so that electromagnetic force is generated. The electromagnetic loading platform mainly acts on the main shaft 2.
And (3) hydraulic loading: and carrying out radial static loading on the tested bearing through a hydraulic loading platform, and simulating the stress state of the tested bearing under the real work. The hydraulic loading platform mainly acts on the bearing outer ring.
The bearing system to be tested: the angular contact bearing is assembled and a ball bearing is taken as an example of demonstration in the bearing external loading state measuring device in fig. 8.
Supporting a main shaft system: and the two ends of the high-rigidity main shaft system in a back-to-back symmetrical mode are respectively provided with a supporting structure.
A driving system: the device is provided with a motor 11, a high-speed motorized spindle 2 is arranged in a matched mode, and is connected with a test bearing-spindle system through a flexible coupling 3 and is driven.
Measurement system: and carrying out main resonance response identification, realizing bearing time-varying rigidity fluctuation analysis and main resonance response research on the basis of a multi-field and multi-degree-of-freedom rolling bearing force-thermal coupling analysis model, and feeding back measurement data to the terminal equipment in real time.
The embodiment of the invention provides computer equipment. The computer device of this embodiment includes: a processor, a memory, and a computer program stored in the memory and executable on the processor. The steps of the various method embodiments described above are implemented when the processor executes the computer program. Alternatively, the processor may implement the functions of the modules/units in the above-described device embodiments when executing the computer program.
The computer program may be divided into one or more modules/units, which are stored in the memory and executed by the processor to accomplish the present invention.
The computer equipment can be a desktop computer, a notebook computer, a palm computer, a cloud server and other computing equipment. The computer device may include, but is not limited to, a processor, a memory.
The processor may be a central processing unit (Central Processing Unit, CPU), but may also be other general purpose processors, digital signal processors (Digital Signal Processor, DSP), application specific integrated circuits (Application Specific Integrated Circuit, ASIC), off-the-shelf programmable gate arrays (Field-Programmable Gate Array, FPGA) or other programmable logic devices, discrete gate or transistor logic devices, discrete hardware components, or the like.
The memory may be used to store the computer program and/or modules, and the processor may implement various functions of the computer device by running or executing the computer program and/or modules stored in the memory, and invoking data stored in the memory.
The modules/units integrated with the computer device may be stored in a computer readable storage medium if implemented in the form of software functional units and sold or used as stand alone products. Based on such understanding, the present invention may implement all or part of the flow of the method of the above embodiment, or may be implemented by a computer program to instruct related hardware, where the computer program may be stored in a computer readable storage medium, and when the computer program is executed by a processor, the computer program may implement the steps of each of the method embodiments described above. Wherein the computer program comprises computer program code which may be in source code form, object code form, executable file or some intermediate form etc. The computer readable medium may include: any entity or device capable of carrying the computer program code, a recording medium, a U disk, a removable hard disk, a magnetic disk, an optical disk, a computer memory, a Read-only memory (ROM), a random access memory (RAM, randomAccessMemory), an electrical carrier signal, a telecommunication signal, a software distribution medium, and so forth. It should be noted that the computer readable medium contains content that can be appropriately scaled according to the requirements of jurisdictions in which such content is subject to legislation and patent practice, such as in certain jurisdictions in which such content is subject to legislation and patent practice, the computer readable medium does not include electrical carrier signals and telecommunication signals.
The above is only a preferred embodiment of the present invention, and is not intended to limit the present invention, but various modifications and variations can be made to the present invention by those skilled in the art. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention should be included in the protection scope of the present invention.
Claims (10)
1. The bearing stress state measuring method based on the resonance attenuation method is characterized by comprising the following steps of:
exciting main resonance response behaviors of the test bearing-main shaft system;
acquiring an attenuation response curve of a nonlinear system in a main resonance region, and acquiring the instantaneous frequency and envelope amplitude of a tested bearing-spindle system by a transient time-frequency signal analysis method to obtain a trunk curve of the tested bearing-spindle system in a main resonance response interval range;
analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
and (3) establishing a bearing quasi-static model, obtaining a mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the stress state of the bearing based on nonlinear time-varying rigidity measurement.
2. The method for measuring the bearing stress state based on the resonance attenuation method according to claim 1, wherein the excitation of the main resonance response behavior of the test bearing-spindle system is performed by loading the test bearing-spindle system in a non-contact electromagnetic loading manner; the transient time-frequency signal analysis method comprises a Hilbert transient time-frequency signal analysis method or a wavelet transformation transient time-frequency signal analysis method.
3. The method for measuring bearing stress state based on resonance attenuation method according to claim 1 or 2, wherein the acquiring the instantaneous frequency of the test bearing-spindle system comprises:
detecting zero crossing points of the response signals, and determining crossing time by using a standard deviation algorithm; smoothing around the intersection point using a moving average filter; after determining the crossing time sequence, calculating an estimated value of the instantaneous frequency at the next moment of any crossing point; constructing a moving average filter, and calculating a final instantaneous frequency:
where f () represents the instantaneous frequency,
represents the crossover time, N represents the order of the moving average filter, +.>
Represents the instantaneous frequency at the crossing, < >>
Another crossing time is represented, i represents any crossing point, and j represents another crossing point.
4. The method for measuring bearing stress state based on resonance attenuation method according to claim 1 or 2, wherein the acquiring envelope amplitude of the test bearing-spindle system comprises:
extracting a response envelope by tracking signal peaks within each individual zero crossing time interval; at each interval
The maximum absolute value of the internal search signal X and the corresponding time of occurrence thereof>
wherein ,
represents signal peak, X (t) represents signal sequence,>
representing a time interval; while calculating the instantaneous frequency, the instantaneous amplitude is estimated from the interpolation function.
5. The method for measuring the bearing stress state based on the resonance attenuation method according to claim 1 or 2, wherein the main curve is obtained by adopting the following method:
the backbone curve is a function of frequency and amplitude parameterization over time, pairing the sequence a (t) and the frequency f (t) correspondingly:
where A () represents the instantaneous amplitude, Γ (t) is the digital sequence
The polynomial interpolation function of (2) represents the envelope of the decay time signal.
6. The method for measuring the bearing stress state based on the resonance attenuation method according to claim 1 or 2, wherein the obtaining the mapping relation between the nonlinear stiffness of the measured bearing and the stress state thereof, to complete the test of the bearing stress state based on the nonlinear time-varying stiffness measurement, comprises the following steps:
radial stiffness K of bearing yy The following are provided:
wherein Z represents the number of rolling bodies, and k represents the contact stiffness; alpha ik and αok Contact angles of the rolling bodies and the inner and outer raceways are respectively; k (k) ik and kok The contact rigidity of the rolling bodies and the inner and outer raceways;
calculating the stress state of the bearing by adopting a bidirectional sweep frequency analysis method for nonlinear vibration response research of a rotor system;
the bearing receives external force F as follows:
wherein ,N1 Is a left pass matrix;
is dynamic sweep frequency force; />
Is static sweep frequency force; m is m r Is the mass of the bearing rotor system; g is gravity acceleration; t is a matrix transpose symbol; f is the shaft end sweep frequency force; omega is the frequency of the shaft end sweep force; t is the run time; />
Is a static radial force at the shaft end.
7. A bearing stress state measurement system based on a resonance attenuation method, comprising:
the corresponding behavior excitation module is used for exciting the main resonance response behavior of the test bearing-spindle system;
the main curve calculation module is used for acquiring an attenuation response curve of the nonlinear system in the main resonance region, acquiring the instantaneous frequency and the envelope amplitude of the test bearing-main shaft system through a transient time-frequency signal analysis method, and acquiring a main curve of the tested bearing-main shaft system in the main resonance response interval range;
the rigidity calculation module is used for analyzing and calculating a trunk curve by adopting a nonlinear modal analysis method to obtain the nonlinear rigidity of the bearing to be measured;
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the nonlinear rigidity of the tested bearing and the stress state of the tested bearing, and completing the test of the bearing stress state based on nonlinear time-varying rigidity measurement.
8. A bearing stress state measuring device based on a resonance damping method for implementing the method according to any one of claims 1 to 6, comprising:
the electromagnetic loading device comprises a supporting seat (10), wherein an electromagnetic loading device (7) is arranged on the supporting seat (10); the main shaft (2) to be measured is arranged on the electromagnetic loading device (7); the front end supporting ball bearing (4), the hydraulic loading device (5) and the rear end supporting ball bearing (6) are sleeved on the main shaft (2); the main shaft (2) is connected with the motor (1) through a coupler (3);
the electromagnetic loading device (7), the electromagnetic loading device (7) comprises cylindrical silicon steel sheets (11), a plurality of stator cores are uniformly arranged on the side surfaces of the silicon steel sheets (11) along the circumferential direction, each stator core is wound with a coil (8), and the coils (8) and the stator cores form an electromagnet (12); the coil (8) is connected with the controller (14) through the power amplifier (13), and a plurality of eddy current displacement sensors (9) are also arranged on the side surface of the main shaft (2);
and the hydraulic loading devices are arranged on two sides of the electromagnetic loading device (7).
9. A computer device comprising a memory, a processor and a computer program stored in the memory and executable on the processor, characterized in that the processor implements the steps of the method according to any of claims 1-6 when the computer program is executed.
10. A computer readable storage medium storing a computer program, characterized in that the computer program when executed by a processor implements the steps of the method according to any of claims 1-6.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310094985.8A CN116256173A (en) | 2023-02-07 | 2023-02-07 | Bearing stress state measuring method and related device based on resonance attenuation method |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310094985.8A CN116256173A (en) | 2023-02-07 | 2023-02-07 | Bearing stress state measuring method and related device based on resonance attenuation method |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN116256173A true CN116256173A (en) | 2023-06-13 |
Family
ID=86682020
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202310094985.8A Pending CN116256173A (en) | 2023-02-07 | 2023-02-07 | Bearing stress state measuring method and related device based on resonance attenuation method |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN116256173A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116484512A (en) * | 2023-06-22 | 2023-07-25 | 西北工业大学 | Identification method for pre-tightening state of disc-drum rotor of aero-engine |
-
2023
- 2023-02-07 CN CN202310094985.8A patent/CN116256173A/en active Pending
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116484512A (en) * | 2023-06-22 | 2023-07-25 | 西北工业大学 | Identification method for pre-tightening state of disc-drum rotor of aero-engine |
| CN116484512B (en) * | 2023-06-22 | 2023-09-01 | 西北工业大学 | Identification method for pre-tightening state of disc-drum rotor of aero-engine |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| Tiwari et al. | Identification of bearing dynamic parameters and unbalance states in a flexible rotor system fully levitated on active magnetic bearings | |
| Sawicki et al. | Detecting cracked rotors using auxiliary harmonic excitation | |
| CN104568313B (en) | Influence coefficient dynamic balance method on rotating machine with multiple plane, multiple-points and multiple revolving speed shafting | |
| Yang et al. | The varying compliance resonance in a ball bearing rotor system affected by different ball numbers and rotor eccentricities | |
| Saleem et al. | Detection of unbalance in rotating machines using shaft deflection measurement during its operation | |
| CN104048595A (en) | Angle misalignment fault quantitative detection system and method for rotating machine | |
| JPS60214228A (en) | Vibration analyzing method | |
| CN116256173A (en) | Bearing stress state measuring method and related device based on resonance attenuation method | |
| CN110118632A (en) | By the method for the degree of unbalancedness of displacement sensor axis elastic rotor | |
| Ciulli et al. | Set-up of a novel test plant for high power turbomachinery tilting pad journal bearings | |
| CN116222475A (en) | Bearing dynamic clearance measurement method and related device based on resonance attenuation method | |
| CN104101464A (en) | Multi-wheel-disc rotor dynamic balancing test method based on rotating coordinate system | |
| Bhende | A new rotor balancing method using amplitude subtraction and its performance analysis with phase angle measurement-based rotor balancing method | |
| CN203981346U (en) | Routine test hydro-extractor is quiet-mobile equilibrium monitoring device | |
| CN110702314B (en) | Non-trial-weight transient high-speed dynamic balancing method based on flexible rotor acceleration response information | |
| Chen et al. | Identification of linearized dynamic characteristics of rolling element bearings | |
| CN109357827B (en) | Reciprocating equipment shafting vibration experiment and analysis method | |
| CN104165729A (en) | Dynamic balancing method for high-speed rotors | |
| Santiago et al. | Experimental identification of bearing dynamic force coefficients in a flexible rotor—further developments | |
| Choudhury | Vibration monitoring of rotating electrical machines: vibration monitoring | |
| JP5671834B2 (en) | Degradation diagnosis method for rolling bearings | |
| Sui et al. | Laser-based measurement for micro-unbalance of cylindrical rollers of the high-speed precision rolling bearings | |
| Wang et al. | Analysis on high-speed spindle online dynamic balancing regulation characteristics | |
| Song et al. | Dynamic Compliance of Measuring Device for Force on High-speed Rotors | |
| CN113720607B (en) | Thrust sliding bearing dynamic characteristic testing device based on non-contact electromagnetic vibration exciter |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination |