CN116222475A - Bearing dynamic clearance measurement method and related device based on resonance attenuation method - Google Patents
Bearing dynamic clearance measurement method and related device based on resonance attenuation method Download PDFInfo
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Abstract
The invention discloses a bearing dynamic clearance measuring method and a related device based on a resonance attenuation method, comprising the following steps: the bearing-spindle system is loaded by means of electromagnetic loading. And acquiring an attenuation response curve by a resonance attenuation method, acquiring instantaneous frequency and envelope amplitude based on a transient time-frequency signal analysis method, and further identifying a trunk curve. Establishing a quasi-static model of the bearing, obtaining the mapping relation between the bearing clearance and the mean value and fluctuation range of the time-varying rigidity fluctuation, and further effectively and accurately detecting the dynamic clearance inside the bearing through multiple tests of the dynamic time-varying rigidity in the actual running process of the bearing system. The process is realized by a set of test device, and mainly comprises 6 parts of an electromagnetic loading platform, a hydraulic loading platform, a tested bearing system, a supporting main shaft system, a driving system and a measuring system. The invention is suitable for the positive clearance rolling bearings with different types and is suitable for the accurate measurement work of the dynamic clearance of the bearings.
Description
Technical Field
The invention belongs to the technical field of bearing state measurement, and relates to a bearing dynamic clearance measurement method based on a resonance attenuation method and a related device.
Background
Play is an important structural parameter of the bearing. Reasonable play parameters will be indicative of various performance characteristics of the bearing, such as: the life-friction resistance-mechanical operation accuracy-temperature rise-noise-vibration-reliability of the bearing has a great influence. It can be found by theoretical analysis and engineering study that: when the radial play of the bearing is too small, the problems of bearing heating, lubricating oil viscosity reduction, adhesive wear and the like are easily caused, and when the radial play of the bearing is too large, the problem of cage slipping, bearing kinematic pair impact and bearing pitting, part wear and the like are easily aggravated.
Most of the existing measuring methods for bearing clearance are static measuring methods for mainly measuring radial clearance. For example: in the national standard JB3573-2004T, a simple measurement method for the radial play of a roller bearing is described. However, during the actual running process of the bearing, the bearing can generate radial deformation, and the internal clearance can change in real time under the combined action of the assembly interference force, the centrifugal inertia force and the thermal stress, so that the accurate measurement of the dynamic clearance of the bearing becomes more important.
As shown in fig. 1, in order to avoid problems such as friction and excessive heat generation, the rolling bearing is usually rotated in practical engineering applications, and therefore, the rolling bearing inner member must have a certain clearance, which is called play. Play is an important parameter in rolling bearings, and standard range values of the play of rolling bearings are noted in national standards. For the bearing, if the clearance is too small, the problems of aggravation of friction, increase of temperature rise and the like can occur, the service life of the bearing is further influenced, but if the clearance is too large, the problem that the rotation precision cannot meet the requirement during the bearing operation can also occur, the vibration impact of the bearing is aggravated, the service life of the bearing can also be shortened, and therefore the clearance is an important parameter about whether the bearing can work normally or not. The bearing internal clearance can be divided into radial clearance and axial clearance according to the direction of movement.
As shown in fig. 2, the play of the bearing changes when the bearing is mounted in the spindle system. Meanwhile, during the actual operation of the bearing, the internal clearance of the bearing is subjected to the coupling action of assembly interference force, centrifugal inertia force and thermal stress, and radial expansion of the bearing can be generated at the moment, so that the internal clearance of the bearing can be further changed.
In the conventional bearing system analysis process, a certain simplification process is usually carried out on the bearing system, so that the influence of the circumferential position change of the bearing roller on the bearing rigidity characteristic is often ignored, namely the time-varying characteristic of the bearing rigidity is ignored. As shown in fig. 5, during actual operation of the bearing, the number of rollers involved in bearing of the bearing changes periodically, that is, the bearing area changes, which causes obvious time-varying fluctuation of the rigidity of the bearing, resulting in time-varying nonlinear characteristics of the rigidity of the bearing. As shown in fig. 6, in one cycle of the bearing roller position, when the number of contact rollers increases or decreases, a significant fluctuation change in the bearing rigidity occurs.
Disclosure of Invention
The invention aims to solve the problems in the prior art, and provides a method and a related device for measuring the dynamic clearance of a bearing based on a resonance attenuation method, which are used for researching the evolution of the internal clearance of the bearing along with the adjustment parameters and the temperature under the actual working condition in the actual running process of the bearing, completing the analysis of the time-varying rigidity fluctuation behavior of the bearing, measuring the accurate dynamic clearance of the bearing and ensuring the rotation precision of bearing equipment.
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 dynamic play of a bearing based on a resonance damping method, comprising 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 mean value size and the fluctuation range of the time-varying rigidity of the measured bearing;
and establishing a bearing quasi-statics model, obtaining the average value of the time-varying rigidity of the measured bearing and the mapping relation between the fluctuation range and the internal clearance of the measured bearing, and completing real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement.
In a second aspect, the present invention provides a bearing dynamic play measurement system based on resonance damping method, comprising:
a corresponding behavior excitation module for exciting the main resonance response behavior of the test bearing-spindle system,
a main curve calculation module for obtaining the attenuation response curve of the nonlinear system in the main resonance region, obtaining the instantaneous frequency and envelope amplitude of the test bearing-main shaft system by a transient time-frequency signal analysis method, obtaining the main curve of the tested bearing-main shaft system in the main resonance response interval range,
the mean value and fluctuation calculation module is used for analyzing and calculating the trunk curve by adopting a nonlinear modal analysis method to obtain the mean value size and the fluctuation range of the time-varying rigidity of the measured bearing,
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the mean value of the time-varying rigidity of the measured bearing and the fluctuation range and the internal clearance of the measured bearing, and completing real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement.
In a third aspect, the present invention provides a bearing dynamic play measurement device based on a resonance damping method, comprising:
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 invention discloses a method and a device for measuring dynamic clearance of a bearing based on a resonance attenuation method. According to the invention, the number of the rollers involved in bearing of the bearing is periodically changed in the running process of the bearing under the real working condition, and the rigidity of the bearing can be obviously periodically changed. The internal clearance of the bearing is critical to the performance parameters such as the service life, the rotation precision and the like of the bearing, however, in the actual running process of the bearing, the internal clearance of the bearing can change in real time under the combined action of the assembly interference force, the centrifugal inertia force and the thermal stress. In addition, the traditional bearing clearance measuring method is mostly a static measuring method for mainly measuring radial clearance, and the dynamic clearance measuring method is seldom concerned. 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 dynamic play based on the mapping relation between the play and the resonance frequency.
Furthermore, the loading mode of the main shaft system adopts non-contact electromagnetic loading, so that redundant information is prevented from being input into the main shaft system due to contact friction.
Furthermore, in the simulation calculation analysis process, the influence of the change of the circumferential position of the bearing roller on the rigidity characteristic of the bearing is focused, and the time-varying characteristic of the rigidity of the bearing is fully considered.
Furthermore, 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.
Furthermore, a certain mapping relation exists between the internal clearance of the bearing and the time-varying rigidity of the fluctuation of the bearing, the measured value and the theoretical calculated value have good consistency, a quasi-static model of the bearing is built, and the accurate dynamic clearance of the bearing can be calculated.
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 schematic view of the radial-axial play of a bearing.
Fig. 2 is a schematic illustration of the effect of radial expansion on bearing play.
Fig. 3 is a flow chart of the method of the present invention.
Fig. 4 is a schematic diagram of the system of the present invention.
FIG. 5 is a schematic illustration of the periodic variation of the number of roller contacts with circumferential position.
FIG. 6 is a schematic diagram of a time-varying characteristic of bearing stiffness.
Fig. 7 is a technical roadmap of a method for measuring dynamic play of a bearing.
Fig. 8 is a diagram showing an embodiment of the resonance attenuation method.
Fig. 9 is a schematic diagram of a test platform of a bearing stress state measuring device.
Fig. 10 is a schematic structural view of a non-contact electromagnetic loading device.
Fig. 11 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
In order to make 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 are used for indicating the orientation or positional relationship based on the orientation or positional relationship shown in the drawings, or the orientation or positional relationship in which the inventive product is conventionally put in use, they are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or elements referred to must have a specific orientation-construct and operation in a specific orientation, and therefore 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, integrally connected, mechanically connected, electrically connected, directly connected, indirectly connected through an intermediary, or 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. 3, the embodiment of the invention discloses a method for measuring dynamic clearance of a bearing 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 response signals, determining crossing time by using a standard deviation algorithm, smoothing the periphery of the crossing points by using a moving average filter, calculating an estimated value of instantaneous frequency at the next moment of any crossing point after determining a crossing time sequence, constructing the moving average filter, and calculating 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 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 the time interval, the instantaneous amplitude is estimated from the interpolation function while the instantaneous frequency is calculated.
The trunk curve is obtained by adopting the following method:
the backbone curve is a function of frequency and amplitude parameterization over time, pairing sequences a (t) and Γ (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, adopting a nonlinear modal analysis method to analyze and calculate a trunk curve to obtain the mean value size and the fluctuation range of the time-varying rigidity of the measured bearing,
s4, a bearing quasi-statics model is established, the mapping relation between the mean value of the time-varying rigidity of the measured bearing and the fluctuation range and the internal clearance of the measured bearing is obtained, and real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement is completed.
The method for obtaining the mapping relation between the mean value size and the fluctuation range of the time-varying rigidity of the measured bearing and the internal clearance of the measured bearing, and completing the real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement comprises the following steps:
constructing a five-degree-of-freedom mechanical balance equation of the rotor, and rewriting the equation into a matrix form:
F m ＝N 1 (d 1 )×F L +N 2 (d 1 )×F R
wherein ,d1 N is the distance between the center of the rotor and the center of the bearing 1 and N2 To transfer matrix, F L and FR Is an elastic restoring force.
And solving the matrix equation by adopting a multi-layer iterative nested iterative algorithm, wherein the iteration of the inner layer is the calculation of a bearing local rolling body mechanical equation set. After the rolling bodies in the bearing revolve along with the retainer for one circle, the bearing can experience a complete rigidity fluctuation period. At this time, the common angle of the rolling elements inside the bearing is:
the complete stiffness fluctuation curve of the bearing-rotor system in a single period can be obtained by changing the magnitude of the common angle of the rolling bodies, namely the common angle is in the single period
Uniformly taking values in the interval:
wherein Z is the number of rolling bodies, N b For the number of points taken during a single period of stiffness fluctuation.
Adopting a coupling sweep analysis method to obtain a Y-direction acceleration sweep response result-Z-direction acceleration sweep response result-Y-direction deceleration sweep response result-Z-direction deceleration sweep response result, constructing a mapping relation between bearing play and time-varying rigidity, and further calculating dynamic play:
δ(t)＝F[ψ(t)]
wherein delta (t) is the dynamic play of the bearing.
As shown in fig. 4, an embodiment of the present invention discloses a dynamic bearing play measurement system based on a resonance attenuation method, including:
a corresponding behavior excitation module for exciting the main resonance response behavior of the test bearing-spindle system,
a main curve calculation module for obtaining the attenuation response curve of the nonlinear system in the main resonance region, obtaining the instantaneous frequency and envelope amplitude of the test bearing-main shaft system by a transient time-frequency signal analysis method, obtaining the main curve of the tested bearing-main shaft system in the main resonance response interval range,
the mean value and fluctuation calculation module is used for analyzing and calculating the trunk curve by adopting a nonlinear modal analysis method to obtain the mean value size and the fluctuation range of the time-varying rigidity of the measured bearing,
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the mean value of the time-varying rigidity of the measured bearing and the fluctuation range and the internal clearance of the measured bearing, and completing real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement.
The principle of the invention is as follows:
as shown in fig. 7, the overall technical roadmap of the invention. On the one hand, through parameter resonance response research, a nonlinear parameter identification method is adopted to obtain an attenuation curve in a parameter resonance region, hilbert or wavelet change is used to identify a main curve of a measured bearing-main shaft system, and a nonlinear modal analysis method is used to calculate the mean value of the time-varying rigidity and the fluctuation range of the measured bearing. On the other hand, a quasi-statics model of the bearing is established through bearing time-varying rigidity fluctuation analysis, and the mapping relation between rigidity fluctuation and internal clearance is obtained. And finally, calculating accurate dynamic clearance inside the bearing based on the mapping relation, and realizing real-time detection of the bearing clearance. Meanwhile, the invention also constructs a device for measuring the dynamic clearance inside 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. 8, fig. 8 is an embodiment of a parametric resonance response identification study for a bearing-spindle system based on resonance decay. Firstly, an attenuation response needs to be obtained, a normal force mode distribution method is needed to be used for calculating a proper system mode based on a resonance attenuation method (RDM) in a nonlinear parameter identification method, and then harmonic excitation is used for activating nonlinearity of a system structure to generate an attenuation response curve in a parameter resonance region.
And a transient time-frequency signal analysis method such as Hilbert or wavelet change is adopted to obtain the instantaneous frequency and envelope amplitude of the measured 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 internal play: based on an amplitude-frequency response curve of a nonlinear system, a bearing quasi-statics model is established, and the mapping relation between the fluctuation mean value of the rigidity fluctuation of the measured bearing and the fluctuation range and the internal clearance of the fluctuation mean value is obtained. Based on the mapping relation between the bearing clearance and the bearing time-varying rigidity, the dynamic clearance of the bearing is calculated, and the real-time detection of the internal clearance change of the bearing is realized.
As shown in fig. 9, the embodiment of the invention discloses a bearing dynamic clearance measuring device based on a resonance attenuation method, which comprises 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. 10, 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. 11, fig. 11 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 an external controller, so that the excitation of the resonance response behavior of the measured bearing-spindle system parameter is realized. The electromagnetic loading platform comprises an embedded eddy current displacement sensor-coil and the like, and the software system comprises a controller and the like, and the schematic device diagram and the schematic circuit diagram of the electromagnetic loading platform are shown in fig. 10 and 11. The electromagnetic loading device is similar to the electromagnetic bearing in structure, and mainly comprises a silicon steel sheet-stator iron core and coils wound on the stator iron core, wherein each two adjacent coils on the two magnetic poles are connected in series to form a magnetic pole pair, and when current is introduced into the coils, a closed magnetic circuit is generated between the silicon steel sheet-iron core and an air gap, so that electromagnetic force is generated. The electromagnetic loading platform mainly acts on the main shaft.
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: in the dynamic play measuring device in the bearing in fig. 9, a ball bearing is taken as an example of demonstration in a rolling bearing having positive play under the working action of a deep groove ball bearing, a cylindrical roller bearing and the like.
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, a high-speed motorized spindle is arranged in a matched mode, and the motor is connected with a tested bearing-spindle system through a flexible coupling and drives the tested bearing-spindle system.
Measurement system: and carrying out parameter resonance response identification, realizing bearing time-varying rigidity fluctuation analysis and parameter resonance response research on the basis of a multi-field-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., which are within the spirit and principles of the present invention, are intended to be included in the scope of the present invention.
Claims (10)
1. The method for measuring the dynamic clearance of the bearing 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 mean value size and the fluctuation range of the time-varying rigidity of the measured bearing;
and establishing a bearing quasi-statics model, obtaining the average value of the time-varying rigidity of the measured bearing and the mapping relation between the fluctuation range and the internal clearance of the measured bearing, and completing real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement.
2. The method for measuring the dynamic bearing clearance 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 carried out 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 dynamic play of a bearing based on resonance damping method according to claim 1 or 2, characterized in that the acquiring the instantaneous frequency of the test bearing-spindle system comprises:
detecting zero crossing points of response signals, determining crossing time by using a standard deviation algorithm, smoothing the periphery of the crossing points by using a moving average filter, calculating an estimated value of instantaneous frequency at the next moment of any crossing point after determining a crossing time sequence, constructing the moving average filter, and calculating 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 dynamic play of a bearing based on resonance damping method according to claim 1 or 2, wherein the acquiring envelope amplitude of the test bearing-spindle system comprises:
extracting 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 the time interval, the instantaneous amplitude is estimated from the interpolation function while the instantaneous frequency is calculated.
5. The method for measuring dynamic play of a bearing based on resonance attenuation method according to claim 1 or 2, wherein the backbone curve is obtained by the following method:
the backbone curve is a function of frequency and amplitude parameterization over time, pairing sequences a (t) and Γ (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 dynamic bearing play based on resonance attenuation method according to claim 1 or 2, wherein the obtaining the mapping relationship between the mean value of the time-varying rigidity of the measured bearing and the fluctuation range and the internal play thereof, and completing the real-time detection of the internal play of the bearing based on the time-varying rigidity measurement, comprises:
the five-degree-of-freedom mechanical equilibrium equation of the rotor is constructed, and the matrix form is as follows:
F m ＝N 1 (d 1 )×F L +N 2 (d 1 )×F R
wherein ,Fm Is the external force vector applied to the center of the rotor, d 1 N is the distance between the center of the rotor and the center of the bearing 1 and N2 Transfer matrices on left and right sides, respectively, F L and FR Elastic restoring forces of the left side and the right side respectively;
solving the matrix equation by adopting a multi-layer iterative nested iterative algorithm, wherein the iteration of the inner layer is the calculation of a bearing local rolling physical force equation set; when the rolling bodies in the bearing revolve along with the retainer for a circle, the bearing can experience a complete rigidity fluctuation period; at this time, the revolution angle ψ of the rolling elements inside the bearing VC The method comprises the following steps:
wherein Z is the number of rolling bodies;
by varying the magnitude of the revolution angle of the rolling bodies, the complete stiffness fluctuation curve of the bearing-rotor system in a single period is obtained, i.e. the revolution angle is in
Uniformly taking values in the interval:
wherein ,ψ0 Is the revolution angle of the rolling bodies in the bearing, N b The number of points taken in a single rigidity fluctuation period is m, and the rigidity fluctuation period experienced by the bearing is m;
adopting a coupling sweep analysis method to obtain a Y-direction acceleration sweep response result-Z-direction acceleration sweep response result-Y-direction deceleration sweep response result-Z-direction deceleration sweep response result, constructing a mapping relation between bearing clearance and time-varying rigidity, and further calculating a bearing dynamic clearance delta (t):
δ(t)＝F[ψ(t)]
wherein F is the mapping relation between bearing play and time-varying rigidity, and ψ (t) is the complete rigidity fluctuation curve in a single period of the bearing.
7. A bearing dynamic play measurement system based on a resonance decay method, comprising:
a corresponding behavior excitation module for exciting the main resonance response behavior of the test bearing-spindle system,
a main curve calculation module for obtaining the attenuation response curve of the nonlinear system in the main resonance region, obtaining the instantaneous frequency and envelope amplitude of the test bearing-main shaft system by a transient time-frequency signal analysis method, obtaining the main curve of the tested bearing-main shaft system in the main resonance response interval range,
the mean value and fluctuation calculation module is used for analyzing and calculating the trunk curve by adopting a nonlinear modal analysis method to obtain the mean value size and the fluctuation range of the time-varying rigidity of the measured bearing,
the model construction module is used for establishing a bearing quasi-statics model, obtaining the mapping relation between the mean value of the time-varying rigidity of the measured bearing and the fluctuation range and the internal clearance of the measured bearing, and completing real-time detection of the internal clearance of the bearing based on the time-varying rigidity measurement.
8. A dynamic play measuring device for bearings based on resonance damping method for implementing the method according to any one of claims 1-6, characterized by 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.
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| CN117288383A (en) * | 2023-11-23 | 2023-12-26 | 南通进宝机械制造有限公司 | Machine static and dynamic balance optimization test method based on data analysis |
| CN117288383B (en) * | 2023-11-23 | 2024-05-10 | 南通进宝机械制造有限公司 | Machine static and dynamic balance optimization test method based on data analysis |
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