CN108031642A - A kind of more excitation systems and its power output adjusting method for modal test - Google Patents

A kind of more excitation systems and its power output adjusting method for modal test Download PDF

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Publication number
CN108031642A
CN108031642A CN201711256719.1A CN201711256719A CN108031642A CN 108031642 A CN108031642 A CN 108031642A CN 201711256719 A CN201711256719 A CN 201711256719A CN 108031642 A CN108031642 A CN 108031642A
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Prior art keywords
counterweight
coupled system
vibrator
excitation point
work top
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CN201711256719.1A
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CN108031642B (en
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吴志刚
马成骥
杨超
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Beihang University
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Beihang University
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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B3/00—Methods or apparatus specially adapted for transmitting mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • G—PHYSICS
    • G01—MEASURING; TESTING
    • G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
    • G01M7/00—Vibration-testing of structures; Shock-testing of structures
    • G01M7/02—Vibration-testing by means of a shake table
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B06—GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS IN GENERAL
    • B06B—METHODS OR APPARATUS FOR GENERATING OR TRANSMITTING MECHANICAL VIBRATIONS OF INFRASONIC, SONIC, OR ULTRASONIC FREQUENCY, e.g. FOR PERFORMING MECHANICAL WORK IN GENERAL
    • B06B1/00—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency
    • B06B1/02—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy
    • B06B1/04—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with electromagnetism
    • B06B1/045—Methods or apparatus for generating mechanical vibrations of infrasonic, sonic, or ultrasonic frequency making use of electrical energy operating with electromagnetism using vibrating magnet, armature or coil system

Abstract

It is contemplated that the multiple exciting forces acted on test specimen and the Amplitude Ration acted between the Ampere force on moving coil component are that constant, phase difference are 0 ° as far as possible as far as possible, and the coupling between each vibrator is set to be weakened as far as possible.For this reason, the present invention is by according to the jth rank modal frequency ω to be measuredj, main counterweight (7) and fine setting counterweight (8) are adjusted, makes main counterweight (7), fine setting counterweight (8), fastening bolt (9), the gross mass of exciting rod (10), is allowed to meet

Description

A kind of more excitation systems and its power output adjusting method for modal test
Technical field
The present invention relates to a kind of more excitation systems and its power output adjusting method for modal test.
Background technology
Nowadays modal test has become the important means for solving vibration problem in engineering, in machinery, Aeronautics and Astronautics, soil The engineering fields such as wood, building, shipbuilding, chemical industry are widely used.
The purpose of modal test is the modal parameter of measuring system, i.e. resonant frequency, damped coefficient and Mode Shape.These Modal parameter describes the vibration characteristics of system.One important step of modal test research is to apply a dynamic to structure to swash Encourage power.Exciting force can be added on single a application point of structure, can also be added at the same time on multiple points.Apply the mesh of exciting force Be to make structure in selected frequency range internal vibration, and require applied exciting force to measure, structure is to swashing The response for encouraging power is also what can be measured.Obviously, exciting force is the important component of mode experiment process：It produces structure Vibration, this is the necessary condition for the dynamic characteristic that any object is studied by modal test.
Using phase resonance method, apply sinusoidal excitation power successively in each intrinsic frequency, adjust exciting force frequency and width (when being in resonance state, institute is effectively and response is single-phase, and exciting force and response have until motivating a normal mode for value 90 ° of phase offsets, architectural characteristic are substantially identical with a single-mode system).
Current trend is to use multi input testing program.Input energy preferably can be assigned to whole examination by multi input On part (this is critically important for big test specimen).This method can reduce because excitation force is just selected in certain rank to greatest extent The chance for can not swashing Chu Lai the rank mode on mode node.(such as drum, disk or square plate for the structure with repeated root Deng symmetrical structure), these repeated roots can just only be detected using multi input measurement, and need to have not between each vibrator Same amplitude and phase relation, in order to preferably motivate corresponding mode.
Electromagnetic exciter is a kind of device for converting electrical energy into mechanical energy, is common driving source in modal test.Fig. 1 Show the basic structure of electric activator, wherein：Moving coil component (3) links together with work top (1), is positioned at magnetic field (5) in.After moving coil component (3) is passed through electric current, it will produce Ampere force, so that work top (1) moves, pass through exciting rod (10) etc. (see Fig. 2), test specimen is given to provide an exciting force.Support spring (2) plays the role of supporting work top (1).
The content of the invention
In modal test, it is desirable to multiple exciting forces for acting on test specimen and act on Ampere force on moving coil component it Between Amplitude Ration be that constant, phase difference are 0 ° as far as possible as far as possible；For this reason, using between Ampere force and input current into simple Proportional relation, it appears that power output can be controlled by control input electric current, achieve the purpose that effectively to encourage test specimen, still, by It can not often accomplish this point in following factor：
1) impedance mismatch between vibrator and test specimen, the output drive power of vibrator and the Ampere force that is acted on moving-coil it Between characteristic be not flat in whole frequency range；
2) Multiexciter acts on elastic test specimen at the same time, can produce coupling, and then influence each other.
So, it is necessary to solve the problems, such as to include in modal test：How to make to act on multiple exciting forces on test specimen with The Amplitude Ration acted between the Ampere force on moving coil component is that constant, phase difference are 0 ° as far as possible as far as possible, and as far as possible Weaken the coupling between each vibrator, effectively swashed to control power output by control input electric current so as to reach Encourage the purpose of test specimen.
It is contemplated that multiple exciting forces for acting on test specimen and acting between the Ampere force on moving coil component Amplitude Ration is that constant, phase difference are 0 ° as far as possible as far as possible, and the coupling between each vibrator is weakened as far as possible.
According to an aspect of the invention, there is provided a kind of more excitation systems for modal test, for encouraging two certainly By degree system, the coupled system is by following parameter characterization：
The mass M of coupled systemsi,
The out-damping C of coupled systemsi,
The support stiffness K of coupled systemsi,
The Coupling Damping C of coupled systems,
The stiffness K of coupled systems,
It is characterized by comprising：
Two vibrators, wherein i-th driver be positioned at i-th of excitation point, i=1,2,
Wherein each vibrator includes：
Vibrator moving coil component,
Work top,
Support spring,
Main counterweight,
Finely tune counterweight,
Fastening bolt,
Exciting rod,
Wherein,
Moving coil component links together with work top, is positioned in a magnetic field,
After moving coil component is passed through electric current, it will produce Ampere force, move work top, which is given by exciting rod Test specimen applies an exciting force,
Support spring is used to support work top,
Main counterweight is connected with fine setting counterweight by fastening bolt, forms adjustable counter balance, for changing vibrator impedance operator, Be allowed to test specimen impedance matching,
Wherein,
mpiFor the main counterweight at i-th of excitation point, counterweight, fastening bolt, the gross mass of exciting rod are finely tuned,
meiIt is the gross mass of vibrator moving coil component at i-th of excitation point and work top,
cei(i=1,2) is the equivalent damping of the support spring at i-th of excitation point,
kei(i=1,2) is the equivalent stiffness of the support spring at i-th of excitation point,
If the angular frequency of first and second rank mode of two degrees of freedom test specimen is respectively ω1And ω2, surveyed when using phase resonance method During flow control j rank mode, wherein j=1,2, that is, the angular frequency of the Ampere force acted on moving-coil is ωj,
Main counterweight, fine setting counterweight at i-th of excitation point, fastening bolt, the gross mass m of exciting rodpiMeet：
Wherein i=1,2；J=1,2.
According to another aspect of the present invention, there is provided a kind of power output of more excitation systems for modal test is adjusted Method, more excitation systems are used to encourage coupled system,
The coupled system is by following parameter characterization：
The mass M of coupled systemsi,
The out-damping C of coupled systemsi,
The support stiffness K of coupled systemsi,
The Coupling Damping C of coupled systems,
The stiffness K of coupled systems,
More excitation systems include two vibrators, wherein i-th driver be positioned at i-th of excitation point, i=1,2,
Wherein each vibrator includes：
Vibrator moving coil component,
Work top,
Support spring,
Main counterweight,
Finely tune counterweight,
Fastening bolt,
Exciting rod,
The power output adjusting method is characterized in that including：
Moving coil component and work top are linked together, are positioned in a magnetic field,
Moving coil component is passed through electric current, produce Ampere force, so that work top moves, the movement is by exciting rod to examination Part applies an exciting force,
Work top is supported with support spring,
Main counterweight is connected with fine setting counterweight by fastening bolt, form adjustable counter balance, for changing vibrator impedance spy Property, be allowed to test specimen impedance matching, wherein,
mpiFor the main counterweight at i-th of excitation point, counterweight, fastening bolt, the gross mass of exciting rod are finely tuned,
meiIt is the gross mass of vibrator moving coil component at i-th of excitation point and work top,
cei(i=1,2) is the equivalent damping of the support spring at i-th of excitation point,
kei(i=1,2) is the equivalent stiffness of the support spring at i-th of excitation point,
When the angular frequency of first and second rank mode of two degrees of freedom test specimen is respectively ω1And ω2When, when using phase resonance method When measuring jth rank mode, wherein j=1,2, the angular frequency of the Ampere force acted on moving-coil is ωj, make at i-th of excitation point Main counterweight, fine setting counterweight, fastening bolt, the gross mass m of exciting rodpiMeet：
Wherein i=1,2；J=1,2.
Brief description of the drawings
Fig. 1 is a kind of organigram of typical prior art vibrator.
Fig. 2 is the schematic diagram of modal test system according to an embodiment of the invention.
Fig. 3 is the concrete form of counter weight device.
Total counterweight m is shown in a simulated example according to the present invention in Fig. 4 Ap1=mp2When=1kg is not with adding counterweight The exciting force f of first excitation point1With Ampere force F1Between transfer function H11Frequency response curve contrast.
Total counterweight m in above-mentioned simulated example according to the present invention is shown in Fig. 4 Bp1=mp2When=1kg is not with adding counterweight The exciting force f of second excitation point2With Ampere force F1Between transfer function H21Frequency response curve contrasts.
Total counterweight m in above-mentioned simulated example according to the present invention is shown in Fig. 4 Cp1=mp2When=1kg is not with adding counterweight Exciting force f1With Ampere force F2Between transfer function H12Frequency response curve contrasts.
Total counterweight m in above-mentioned simulated example according to the present invention is shown in Fig. 4 Dp1=mp2When=1kg is not with adding counterweight Exciting force f2With Ampere force F2Between transfer function H22Frequency response curve contrasts.
Description of reference numerals：
1-work top, 2-support spring, 3-moving coil component
4-magnetic core, 5-magnetic flux path, 6-housing
7-main counterweight 8-fine setting 9-fastening bolt of counterweight
10-exciting rod, 11-force snesor, 12-two degrees of freedom test specimen
Embodiment
As shown in Fig. 2, be a kind of schematic diagram for modal test system according to an embodiment of the invention, its In, main counterweight (7) is connected with fine setting counterweight (8) by fastening bolt (9), adjustable counter balance is formed, for changing vibrator impedance Characteristic, is allowed to and test specimen impedance matching.
Fig. 3 is the schematic diagram that coupled system (12) is encouraged with 2 vibrators.Msi(i=1,2) it is coupled system (12) quality, Csi(i=1,2), Ksi(i=1,2) is coupled system (12) out-damping and support stiffness respectively, Cs、 KsIt is coupled system (12) Coupling Damping, rigidity respectively.
mei(i=1,2), cei(i=1,2), kei(i=1,2) respectively be encourage point i (i=1,2) place vibrator moving-coil Gross mass, support spring (2) equivalent stiffness and the equivalent damping of component (3) and work top (1).mpi(i=1,2) it is excitation point Main counterweight (7), fine setting counterweight (8), fastening bolt (9), the gross mass of exciting rod (10) at i (i=1,2) place.
Fi(i=1,2) it is that the vibrator moving coil component (3) for encouraging point i (i=1,2) place is passed through electric current Ii(i=1,2) produced when Raw Ampere force, Fi(i=1,2) and Ii(i=1,2) there is simple proportional relation；fi(i=1,2) it is to act on excitation point i (i=1,2) exciting force at place；xi(i=1,2) be encourage point i (i=1,2) place move displacement.
Vibrator output drive power f=[f1 f2]TWith acting on the Ampere force F=[F on vibrator moving coil component (3)1 F2]TBetween relation the transmission function of formula (1) and formula (2) can be used to represent
F=HF (1)
Wherein transmission function
If the angular frequency of first and second rank mode of two degrees of freedom test specimen is respectively ω1And ω2, surveyed when using phase resonance method (j=1,2 during flow control j rank mode；The angular frequency for acting on the Ampere force on moving-coil is ωj), to ensure that exciting force can be with Track exciting current, need to will adjust counterweight, by main counterweight (7), fine setting counterweight (8), fastening bolt (9), total matter of exciting rod (10) Amount is adjusted to
If ignore the damping of vibrator, i.e. cei≈ 0 (i=1,2), with angular frequencyj(j=1,2) to test specimen into row energization When, then this up-to-date style (2) is changed into formula (4)
Understood according to formula (4), excitation point 1, the exciting force f=[f of 2 output of excitation point1 f2]TWith acting on vibrator moving-coil Ampere force F=[F on component (3)1 F2]TApproximately equal, and do not coupled between Multiexciter, i.e.,：Reach and acted on examination Multiple exciting forces on part and the Amplitude Ration acted between the Ampere force on moving coil component (3) are as far as possible constant, phase difference It is 0 ° of purpose as far as possible.
Example：
If the parameter of test specimen is Ms1=Ms2=1kg, Ks1=Ks2=10kN/m, Cs1=Cs2=3N/ (m/s), Ks=30kN/ m,Cs=3N/ (m/s), the first natural frequency of test specimen is 15.91Hz.The exciter parameters for encouraging point i (i=1,2) place are me1 =me2=0.5kg, ke1=ke2=15kN/m, ce1=ce2=3.5N/ (m/s).In modal test, if wanting to measure the one of test specimen The intrinsic frequency and the vibration shape of rank mode, then can calculate m according to formula (3)p1=mp2=1kg, i.e. adjustment excitation point i (i=1, 2) the main counterweight (7) of the vibrator at place, fine setting counterweight (8), make main counterweight (7), the fine setting counterweight at excitation point i (i=1,2) place (8), fastening bolt (9), the gross mass m of exciting rod (10)p1、mp2For 1kg.
Fig. 4 A- Fig. 4 D are total counterweight mp1=mp2Transmission between=1kg and the exciting force f and Ampere force F that do not add counterweight Jacobian matrix frequency response curve contrasts.Wherein, total counterweight m is shown in a simulated example according to the present invention in Fig. 4 Ap1=mp2 The exciting force f of first excitation point when=1kg is not with adding counterweight1With Ampere force F1Between transfer function H11Frequency response curve pair Than；Total counterweight m in above-mentioned simulated example according to the present invention is shown in Fig. 4 Bp1=mp2Second swashs when=1kg is not with adding counterweight Encourage exciting force f a little2With Ampere force F1Between transfer function H21Frequency response curve contrasts；Fig. 4 C are shown according to the present invention Total counterweight m in above-mentioned simulated examplep1=mp2=1kg is not with adding exciting force f during counterweight1With Ampere force F2Between transmission function H12Frequency response curve contrasts；Total counterweight m in above-mentioned simulated example according to the present invention is shown in Fig. 4 Dp1=mp2=1kg is not with adding Exciting force f during counterweight2With Ampere force F2Between transfer function H22Frequency response curve contrasts.
As illustrated in figs. 4 a-4d, in the case where adding counterweight, near first order resonance frequency 15.91Hz, point i (i are encouraged =1,2) the characteristic tool of the transfer function matrix between the exciting force at place and corresponding Ampere force improves significantly, major embodiment Both ways：1. force tracking effect improves, H11、H22In amplitude frequency curve, phase frequency curve be changed into flat, Amplitude Ration is approximately normal Number, phase difference is near 0 °；2. near first order resonance frequency 15.91Hz, H12、H21Amplitude frequency curve be less than non-counterweight situation, Illustrate the coupling between vibrator than weakening during non-counterweight.
The advantages of the present invention include：According to the modal frequency to be measured, by adjusting main counterweight (7) with Counterweight (8) is finely tuned, makes main counterweight (7), fine setting counterweight (8), fastening bolt (9), the gross mass of exciting rod (10), meets formula (3), It can then realize the multiple exciting forces for making to act on test specimen and act on the Amplitude Ration between the Ampere force on moving coil component (3) It is that constant, phase difference are 0 ° as far as possible as far as possible, and weakens the coupling between each vibrator as far as possible, so as to reaches The purpose of test specimen is effectively encouraged to control power output by control input electric current.

Claims (2)

  1. A kind of 1. more excitation systems for modal test, for encouraging coupled system (12), the coupled system (12) by following parameter characterization：
    The mass M of coupled system (12)si,
    The out-damping C of coupled system (12)si,
    The support stiffness K of coupled system (12)si,
    The Coupling Damping C of coupled system (12)s,
    The stiffness K of coupled system (12)s,
    It is characterized by comprising：
    Two vibrators, wherein i-th driver be positioned at i-th of excitation point, i=1,2,
    Wherein each vibrator includes：
    Vibrator moving coil component (3),
    Work top (1),
    Support spring (2),
    Main counterweight (7),
    Counterweight (8) is finely tuned,
    Fastening bolt (9),
    Exciting rod (10),
    Wherein,
    Moving coil component (3) links together with work top (1), is positioned in a magnetic field (5),
    After moving coil component (3) is passed through electric current, it will produce Ampere force, move work top (1), which passes through exciting rod (10) an exciting force is applied to test specimen,
    Support spring (2) is used to support work top (1),
    Main counterweight (7) is connected with fine setting counterweight (8) by fastening bolt (9), adjustable counter balance is formed, for changing vibrator impedance Characteristic, be allowed to test specimen impedance matching,
    Wherein,
    mpiFor the main counterweight (7) at i-th of excitation point, counterweight (8), fastening bolt (9), the gross mass of exciting rod (10) are finely tuned,
    meiIt is the gross mass of the vibrator moving coil component (3) at i-th of excitation point and work top (1),
    cei(i=1,2) is the equivalent damping of the support spring (2) at i-th of excitation point,
    kei(i=1,2) is the equivalent stiffness of the support spring (2) at i-th of excitation point,
    If the angular frequency of first and second rank mode of two degrees of freedom test specimen is respectively ω1And ω2, when using phase resonance method measurement the During j rank mode, wherein j=1,2, that is, the angular frequency of the Ampere force acted on moving-coil is ωj,
    Main counterweight (7), fine setting counterweight (8) at i-th of excitation point, fastening bolt (9), the gross mass m of exciting rod (10)piIt is full Foot：
    Wherein i=1,2；J=1,2.
  2. 2. a kind of power output adjusting method of more excitation systems for modal test, which is used to encourage two freely Degree system (12),
    The coupled system (12) is by following parameter characterization：
    The mass M of coupled system (12)si,
    The out-damping C of coupled system (12)si,
    The support stiffness K of coupled system (12)si,
    The Coupling Damping C of coupled system (12)s,
    The stiffness K of coupled system (12)s,
    More excitation systems include two vibrators, wherein i-th driver be positioned at i-th of excitation point, i=1,2,
    Wherein each vibrator includes：
    Vibrator moving coil component (3),
    Work top (1),
    Support spring (2),
    Main counterweight (7),
    Counterweight (8) is finely tuned,
    Fastening bolt (9),
    Exciting rod (10),
    The power output adjusting method is characterized in that including：
    Moving coil component (3) and work top (1) are linked together, are positioned in a magnetic field (5),
    Moving coil component (3) is passed through electric current, produce Ampere force, so that work top (1) moves, which passes through exciting rod (10) an exciting force is applied to test specimen,
    Work top (1) is supported with support spring (2),
    Main counterweight (7) is connected with fine setting counterweight (8) by fastening bolt (9), form adjustable counter balance, for changing vibrator resistance Anti- characteristic, be allowed to test specimen impedance matching, wherein,
    mpiFor the main counterweight (7) at i-th of excitation point, counterweight (8), fastening bolt (9), the gross mass of exciting rod (10) are finely tuned,
    meiIt is the gross mass of the vibrator moving coil component (3) at i-th of excitation point and work top (1),
    cei(i=1,2) is the equivalent damping of the support spring (2) at i-th of excitation point,
    kei(i=1,2) is the equivalent stiffness of the support spring (2) at i-th of excitation point,
    When the angular frequency of first and second rank mode of two degrees of freedom test specimen is respectively ω1And ω2When, measured when using phase resonance method During jth rank mode, wherein j=1,2, the angular frequency of the Ampere force acted on moving-coil is ωj, make the master at i-th of excitation point Counterweight (7), fine setting counterweight (8), fastening bolt (9), the gross mass m of exciting rod (10)piMeet：
    Wherein i=1,2；J=1,2.
CN201711256719.1A 2017-12-03 2017-12-03 A kind of more excitation systems and its power output adjusting method for modal test Active CN108031642B (en)

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US20120302293A1 (en) * 2011-05-27 2012-11-29 Apple Inc. Haptic alert device having a linear vibrator
CN103852233A (en) * 2012-11-30 2014-06-11 波音公司 Electrodynamic Modal Test Impactor System and Method
CN105004620A (en) * 2015-07-16 2015-10-28 浙江工业大学 High-frequency fatigue testing machine dynamic load error compensation method
CN206132338U (en) * 2016-05-23 2017-04-26 脉创测控装备科技（苏州）有限公司 Multi -functional novel vibration exciter
CN107051296A (en) * 2017-01-23 2017-08-18 西安近代化学研究所 A kind of electromagnetic excitation resonance mixing arrangement and its control method

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Publication number Priority date Publication date Assignee Title
US20120302293A1 (en) * 2011-05-27 2012-11-29 Apple Inc. Haptic alert device having a linear vibrator
CN103852233A (en) * 2012-11-30 2014-06-11 波音公司 Electrodynamic Modal Test Impactor System and Method
CN105004620A (en) * 2015-07-16 2015-10-28 浙江工业大学 High-frequency fatigue testing machine dynamic load error compensation method
CN206132338U (en) * 2016-05-23 2017-04-26 脉创测控装备科技（苏州）有限公司 Multi -functional novel vibration exciter
CN107051296A (en) * 2017-01-23 2017-08-18 西安近代化学研究所 A kind of electromagnetic excitation resonance mixing arrangement and its control method

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN114813005A (en) * 2022-06-29 2022-07-29 中国飞机强度研究所 System and method for testing vibration fatigue characteristics of airplane components
CN114813005B (en) * 2022-06-29 2022-09-20 中国飞机强度研究所 System and method for testing vibration fatigue characteristics of airplane components

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