CN103308333A - Method for testing dynamic stiffness of vibration isolator - Google Patents
Method for testing dynamic stiffness of vibration isolator Download PDFInfo
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- CN103308333A CN103308333A CN2013101853524A CN201310185352A CN103308333A CN 103308333 A CN103308333 A CN 103308333A CN 2013101853524 A CN2013101853524 A CN 2013101853524A CN 201310185352 A CN201310185352 A CN 201310185352A CN 103308333 A CN103308333 A CN 103308333A
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- vibration isolator
- dynamic stiffness
- frequency response
- power spectrum
- response function
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Abstract
The invention relates to a method for testing the dynamic stiffness of a vibration isolator, comprising the following steps of (1) arranging an acceleration sensor in a coupling site via a mode that a vibration structure is connected in a coupling way by the vibration isolator; (2) directly measuring system level frequency response functions; and (3) directly calculating according to the measured system level frequency response functions to obtain the dynamic stiffness Kc of the vibration isolator. Compared with an existing technique, the method for testing the dynamic stiffness of the vibration isolator has the advantages of measurement without dismantling equipment, good project practicability and simplicity, precision, feasibility and the like.
Description
Technical field
The present invention relates to the mechanical vibration technical field of measurement and test, especially relate to a kind of vibration isolator dynamic stiffness method of testing.
Background technology
Along with the raising of people's environmental consciousness, control is had higher requirement to the vibration and noise in the productive life, the with serious pollution fields of vibration and noise such as particularly communications and transportation, the manufacturing, building, and how vibration isolation becomes the problem that needs are considered.The appropriate combination of the normally passive flexible member of vibration isolator and damping element, thereby have certain rigidity and damping.As the critical component of vibration and noise reducing system, the dynamic property of vibration isolator is directly connected to vibration isolating effect.Dynamic stiffness is an important indicator of vibration isolator evaluation of dynamic, has a great impact for the vibration isolator anti-vibration performance.
The at present test of vibration isolator dynamic stiffness mainly contains two kinds of methods: power-displacement method and acceleration method.Power-displacement method is the method for testing of comparatively commonly using, and this method test philosophy is simple and precision is high, but requires to use expensive electro-hydraulic servo high frequency actuator, rigidly fixes the end technical requirement in the experiment also higher, simultaneously the test frequency narrow range.Acceleration method needn't be considered the problems such as the rigidity of stiff end and system resonance, also enlarged the frequency range of dynamic characteristic test simultaneously, but precision does not have power-displacement method high.
Summary of the invention
Purpose of the present invention is exactly to provide a kind of vibration isolator dynamic stiffness method of testing for the defective that overcomes above-mentioned prior art existence.
Purpose of the present invention can be achieved through the following technical solutions:
A kind of vibration isolator dynamic stiffness method of testing is characterized in that, may further comprise the steps:
(1) by vibration isolator vibrational structure is of coupled connections, arranges acceleration transducer in coupling place;
(2) direct Department of Survey's irrespective of size frequency response function;
(3) directly calculate vibration isolator dynamic stiffness [K according to the system-level frequency response function that records
c].
Described vibrational structure comprises structure A and structure B, and structure A and structure B are of coupled connections by vibration isolator.
Described system-level frequency response function comprises [H
S]
C (a) c (a), [H
S]
C (b) c (a), [H
S]
C (b) c (b)[H
S]
C (a) c (b)
The described irrespective of size frequency response function [H of Department of Survey
S]
C (a) c (a), [H
S]
C (b) c (a)Measuring process is as follows:
At first in structure A and vibration isolator coupling place excitation; Gather again time-domain signal and all acceleration transducer response signals of excitation; Then time-domain signal is carried out Fourier transform and obtain frequency-region signal, adopt H
1Method of estimation estimated frequency response function:
[H
S]
C (a) c (a)=G
AF/ G
FF, G in the formula
AFStructure A and vibration isolator coupling place acceleration responsive { X}
C (a)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum;
[H
S]
C (b) c (a)=G
BF/ G
FF, G in the formula
BFStructure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum.
The described irrespective of size frequency response function [H of Department of Survey
S]
C (b) c (b), [H
S]
C (a) c (b)Measuring process as follows:
At first in structure B and vibration isolator coupling place excitation; Gather again time-domain signal and all acceleration transducer response signals of excitation; Then adopt H
1Method of estimation estimated frequency response function:
[H
S]
C (a) c (b)=G
AF'/G
FF', G in the formula
AF' be structure A and vibration isolator coupling place acceleration responsive { X}
C (a)And pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum,
[H
S]
C (b) c (b)=G
BF'/G
FF', G in the formula
BF' be structure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum.
Described vibration isolator dynamic stiffness [K
c] calculation expression be:
Compared with prior art, the inventive method can be measured under the situation of detaching equipment not, has good engineering practicability and simplicity, and accurately feasible.
Description of drawings
Fig. 1 is a mechanical system structure figure of the present embodiment.
Fig. 2 is the instrumentation plan of the system-level frequency response function of the present invention.
Fig. 3 is system-level frequency response function [H
S]
C (a) c (a)Measured curve, (a), phase-frequency figure wherein; (b), the width of cloth-frequency figure.
Fig. 4 is system-level frequency response function [H
S]
C (b) c (a)Measured curve, (a), phase-frequency figure wherein; (b), the width of cloth-frequency figure.
Fig. 5 is system-level frequency response function [H
S]
C (a) c (b)Measured curve, (a), phase-frequency figure wherein; (b), the width of cloth-frequency figure.
Fig. 6 is system-level frequency response function [H
S]
C (b) c (b)Measured curve, (a), phase-frequency figure wherein; (b), the width of cloth-frequency figure.
Fig. 7 is the dynamic stiffness K that the inventive method obtains
cCurve.
Fig. 8 is the drag angle curve that the inventive method obtains.
Fig. 9 is theoretical dynamic stiffness curve.
Figure 10 is theoretical drag angle curve.
Embodiment
The present invention is described in detail below in conjunction with the drawings and specific embodiments.
Embodiment
Vibration isolator dynamic stiffness method of testing of the present invention may further comprise the steps:
(1) by vibration isolator vibrational structure is of coupled connections, arranges acceleration transducer in coupling place;
As shown in Figure 1, a mechanical system can be expressed as structure A and structure B composition, and structure A and structure B are of coupled connections by vibration isolator C, and the quiet rigidity of vibration isolator C is 4 * 10
5N/m, ratio of damping are 400Ns/m, wherein { X}
C (x)The output response of expression minor structure x, x=a, b; { F}
C (x)The external drive of expression minor structure x, x=a, b; [K
c] be the vibration isolator dynamic stiffness.
(2) direct Department of Survey's irrespective of size frequency response function;
As shown in Figure 2, system-level frequency response function comprises [H
S]
C (a) c (a), [H
S]
C (b) c (a), [H
S]
C (b) c (b), [H
S]
C (a) c (b)
The described irrespective of size frequency response function [H of Department of Survey
S]
C (a) c (a), [H
S]
C (b) c (a)May further comprise the steps: at first in structure A and vibration isolator C coupling place excitation; Gather again the time-domain signal { F} of excitation
C (a), structure A and vibration isolator C coupling place acceleration transducer time-domain signal { X}
C (a)And the time-domain signal { X} of structure B and vibration isolator C coupling place acceleration transducer
C (b)Then time-domain signal is carried out Fourier transform and obtain frequency-region signal, adopt H
1Method of estimation estimated frequency response function:
[H
S]
C (a) c (a)=G
AF/ G
FF, G in the formula
AFStructure A and vibration isolator coupling place acceleration responsive { X}
C (a)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum, [H as shown in Figure 3
S]
C (a) c (a)Measured curve,
[H
S]
C (b) c (a)=G
BF/ G
FF, G in the formula
BFStructure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum, [H as shown in Figure 4
S]
C (b) c (a)Measured curve.
The described irrespective of size frequency response function [H of Department of Survey
S]
C (b) c (b), [H
S]
C (a) c (b)May further comprise the steps: at first in structure B and vibration isolator coupling place excitation; Gather again the time-domain signal { F} of excitation
C (b), structure A and vibration isolator C coupling place acceleration transducer time-domain signal { X}
C (a)And the time-domain signal { X} of structure B and vibration isolator coupling place acceleration transducer
C (b)Then adopt H
1Method of estimation estimated frequency response function:
[H
S]
C (a) c (b)=G
AF//G
FF/, G in the formula
AF' be structure A and vibration isolator coupling place acceleration responsive { X}
C (aAnd pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum, [H as shown in Figure 5
S]
C (a) c (b)Measured curve,
[H
S]
C (b) c (b)=G
BF'/G
FF', G in the formula
BF' be structure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum, [H as shown in Figure 6
S]
C (b) c (b)Measured curve.
(3) directly calculate vibration isolator dynamic stiffness [K according to the measured system-level frequency response function of step (2)
c]:
Experiment institute's dynamic stiffness amplitude of surveying and drag angle curve are distinguished as shown in Figure 7 and Figure 8, and the theoretical dynamic stiffness amplitude of dynamic stiffness and drag angle curve are distinguished as shown in Figure 9 and Figure 10.Comparison diagram 7 and Fig. 9 and Fig. 8 and Figure 10, its result is basically identical, and experimental result shows that the inventive method is accurately feasible.
Claims (6)
1. a vibration isolator dynamic stiffness method of testing is characterized in that, may further comprise the steps:
(1) by vibration isolator vibrational structure is of coupled connections, arranges acceleration transducer in coupling place;
(2) direct Department of Survey's irrespective of size frequency response function;
(3) directly calculate vibration isolator dynamic stiffness [K according to the system-level frequency response function that records
c].
2. a kind of vibration isolator dynamic stiffness method of testing according to claim 1 is characterized in that, described vibrational structure comprises structure A and structure B, and structure A and structure B are of coupled connections by vibration isolator.
3. a kind of vibration isolator dynamic stiffness method of testing according to claim 2 is characterized in that, described system-level frequency response function comprises [H
S]
C (a) c (a), [H
S]
C (b) c (a), [H
S]
C (b) c (b)[H
S]
C (a) c (b)
4. a kind of vibration isolator dynamic stiffness method of testing according to claim 3 is characterized in that, the described irrespective of size frequency response function [H of Department of Survey
S]
C (a) c (a), [H
S]
C (b) c (a)Measuring process is as follows:
At first in structure A and vibration isolator coupling place excitation; Gather again time-domain signal and all acceleration transducer response signals of excitation; Then time-domain signal is carried out Fourier transform and obtains frequency-region signal, adopt H1 method of estimation estimated frequency response function:
[H
S]
C (a) c (a)=G
AF/ G
FF, G in the formula
AFStructure A and vibration isolator coupling place acceleration responsive { X}
C (a)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum;
[H
S]
C (b) c (a)=G
BF/ G
FF, G in the formula
BFStructure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (a)Cross-power spectrum, G
FFPumping signal { F}
C (a)Auto-power spectrum.
5. a kind of vibration isolator dynamic stiffness method of testing according to claim 4 is characterized in that, the described irrespective of size frequency response function [H of Department of Survey
S]
C (b) c (b), [H
S]
C (a) c (b)Measuring process as follows:
At first in structure B and vibration isolator coupling place excitation; Gather again time-domain signal and all acceleration transducer response signals of excitation; Then adopt H
1Method of estimation estimated frequency response function:
[H
S]
C (a) c (b)=G
AF'/G
FF', G in the formula
AF' be structure A and vibration isolator coupling place acceleration responsive { X}
C (a)And pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum,
[H
S]
C (b) c (b)=G
BF'/G
FF', G in the formula
BF' be structure B and vibration isolator coupling place acceleration responsive { X}
C (b)And pumping signal { F}
C (b)Cross-power spectrum, G
FF' be pumping signal { F}
C (b)Auto-power spectrum.
6. a kind of vibration isolator dynamic stiffness method of testing according to claim 5 is characterized in that, described vibration isolator dynamic stiffness [K
c] calculation expression be:
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Cited By (13)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
CN103808499A (en) * | 2014-01-21 | 2014-05-21 | 江苏科技大学 | Method and device for testing dynamic stiffness of vibration isolator |
CN104198141A (en) * | 2014-09-11 | 2014-12-10 | 江南大学 | Method for indirectly measuring frequency response function of extremely-fragile part |
CN104236834A (en) * | 2014-09-24 | 2014-12-24 | 江南大学 | High-precision method for measuring frequency response functions of fragile parts online |
CN104236833A (en) * | 2014-09-24 | 2014-12-24 | 江南大学 | High-precision method for measuring frequency response function of extremely-fragile part |
CN104236829A (en) * | 2014-09-11 | 2014-12-24 | 江南大学 | Method for detecting very-fragile part uncoupling interface frequency response function |
CN104330150A (en) * | 2014-11-03 | 2015-02-04 | 中国舰船研究设计中心 | Indirect testing method of multi-degree-of-freedom vibrating exciting force of multi-surface mounting device |
CN104677587A (en) * | 2015-03-25 | 2015-06-03 | 重庆邮电大学 | Pier buffering and vibration isolating type multifunctional test platform based on intelligent magnetic rubber supporting seat |
CN108170643A (en) * | 2017-12-26 | 2018-06-15 | 上海交通大学 | Fractionation minor structure frequency response function recognition methods is exempted from based in situ measurement frequency response function |
CN110095241A (en) * | 2019-02-20 | 2019-08-06 | 上海卫星工程研究所 | Cable stiffness test measuring method between separate type spacecraft module |
CN113252261A (en) * | 2021-05-31 | 2021-08-13 | 奇瑞汽车股份有限公司 | Vibration isolation testing method for rubber bushing of automobile electronic water pump |
CN113532630A (en) * | 2021-06-24 | 2021-10-22 | 哈尔滨工程大学 | Marine vibration noise rapid test evaluation device |
CN114778048A (en) * | 2022-06-17 | 2022-07-22 | 中国飞机强度研究所 | Dynamic stiffness and consistency test method for airplane vibration damping component |
CN114778047A (en) * | 2022-06-17 | 2022-07-22 | 中国飞机强度研究所 | Dynamic stiffness and consistency testing device for airplane vibration damping component |
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Cited By (21)
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CN103808499A (en) * | 2014-01-21 | 2014-05-21 | 江苏科技大学 | Method and device for testing dynamic stiffness of vibration isolator |
CN103808499B (en) * | 2014-01-21 | 2016-06-08 | 江苏科技大学 | A kind of vibration isolator dynamic stiffness method of testing and device thereof |
CN104198141A (en) * | 2014-09-11 | 2014-12-10 | 江南大学 | Method for indirectly measuring frequency response function of extremely-fragile part |
CN104236829A (en) * | 2014-09-11 | 2014-12-24 | 江南大学 | Method for detecting very-fragile part uncoupling interface frequency response function |
CN104236834A (en) * | 2014-09-24 | 2014-12-24 | 江南大学 | High-precision method for measuring frequency response functions of fragile parts online |
CN104236833A (en) * | 2014-09-24 | 2014-12-24 | 江南大学 | High-precision method for measuring frequency response function of extremely-fragile part |
CN104330150A (en) * | 2014-11-03 | 2015-02-04 | 中国舰船研究设计中心 | Indirect testing method of multi-degree-of-freedom vibrating exciting force of multi-surface mounting device |
CN104330150B (en) * | 2014-11-03 | 2017-05-03 | 中国舰船研究设计中心 | Indirect testing method of multi-degree-of-freedom vibrating exciting force of multi-surface mounting device |
CN104677587A (en) * | 2015-03-25 | 2015-06-03 | 重庆邮电大学 | Pier buffering and vibration isolating type multifunctional test platform based on intelligent magnetic rubber supporting seat |
CN104677587B (en) * | 2015-03-25 | 2017-03-22 | 重庆邮电大学 | Pier buffering and vibration isolating type multifunctional test platform based on intelligent magnetic rubber supporting seat |
CN108170643A (en) * | 2017-12-26 | 2018-06-15 | 上海交通大学 | Fractionation minor structure frequency response function recognition methods is exempted from based in situ measurement frequency response function |
CN108170643B (en) * | 2017-12-26 | 2021-02-09 | 上海交通大学 | Resolution-free substructure frequency response function identification method |
CN110095241A (en) * | 2019-02-20 | 2019-08-06 | 上海卫星工程研究所 | Cable stiffness test measuring method between separate type spacecraft module |
CN110095241B (en) * | 2019-02-20 | 2022-03-25 | 上海卫星工程研究所 | Method for testing and determining rigidity of cable between separate spacecraft cabins |
CN113252261A (en) * | 2021-05-31 | 2021-08-13 | 奇瑞汽车股份有限公司 | Vibration isolation testing method for rubber bushing of automobile electronic water pump |
CN113252261B (en) * | 2021-05-31 | 2022-06-10 | 奇瑞汽车股份有限公司 | Vibration isolation testing method for rubber bushing of automobile electronic water pump |
CN113532630A (en) * | 2021-06-24 | 2021-10-22 | 哈尔滨工程大学 | Marine vibration noise rapid test evaluation device |
CN114778048A (en) * | 2022-06-17 | 2022-07-22 | 中国飞机强度研究所 | Dynamic stiffness and consistency test method for airplane vibration damping component |
CN114778047A (en) * | 2022-06-17 | 2022-07-22 | 中国飞机强度研究所 | Dynamic stiffness and consistency testing device for airplane vibration damping component |
CN114778048B (en) * | 2022-06-17 | 2022-09-02 | 中国飞机强度研究所 | Dynamic stiffness and consistency test method for airplane vibration damping component |
CN114778047B (en) * | 2022-06-17 | 2022-09-02 | 中国飞机强度研究所 | Dynamic stiffness and consistency testing device for airplane vibration damping component |
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Application publication date: 20130918 |