CN106950018A - A kind of Flexible element dynamic rate measuring method and device - Google Patents
A kind of Flexible element dynamic rate measuring method and device Download PDFInfo
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- CN106950018A CN106950018A CN201710069046.2A CN201710069046A CN106950018A CN 106950018 A CN106950018 A CN 106950018A CN 201710069046 A CN201710069046 A CN 201710069046A CN 106950018 A CN106950018 A CN 106950018A
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- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M5/00—Investigating the elasticity of structures, e.g. deflection of bridges or air-craft wings
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Abstract
The present invention relates to a kind of Flexible element dynamic rate measuring method and device, the measurement of Flexible element dynamic rate is carried out using excitation point measuring method in ISO 10,846 5, excitation point dynamic rate k is obtained11, while measuring the equivalent mass of vibration inertia rigidity ω of test system2m1With the equivalent support stiffness k of test systemi, by formula k21=k11+ω2m1‐kiCalculating obtains revised Flexible element dynamic rate k21.Device is in addition to the device that excitation point measuring method is used in ISO 10,846 5, also including location-plate (108), force snesor (109), acceleration transducer (110), Signal Regulation collection and processing system (112) under Simple Harmonics signal generator (101), power amplifier (102), spacer spring upper location-plate (107), spacer spring.Compared with prior art, the present invention reaches the accuracy and applicable frequency range for effectively improving dynamic stiffness measurement result by carrying out double measurement on the basis of one-shot measurement.
Description
Technical field
Include railroad track technical field the present invention relates to any mechanical engineering field, it is proposed that one kind improves Flexible element
The method of testing and experimental rig of dynamic rate measurement frequency scope and measurement accuracy.
Background technology
Track is because complicated Flexible element is typically not only containing flexible also containing quality and damping etc., so dynamic rate
It can not only be represented comprising direct rigidity simultaneously comprising rigidity is intersected with the mode of matrix, as shown in Figure 1.Flexible element dynamic is just
The general principle of the measurement of degree 1 is by measuring input or power output F and input or output displacement u (or speed or acceleration
Degree), to obtain the dynamic rate of Flexible element.
Flexible element dynamic rate measuring method general at present and experimental rig are according to international standard ISO10846-1:
1997“Laboratory measurement of vibro-acoustic transfer properties of
The sound and vibration transmission characteristic laboratory measurement of resilient elements " Flexible elements, and its rail clip system is directed to accordingly
The European standard ENV 13481-6 of system:2002“Track performance requirements for fastening
The requirement of systems " rail system performance contacting piece systems.
ISO 10846 recommends 3 kinds of flexible member dynamic rate measuring methods, including " ISO 10846-2 direct measurements
Method ", it is " ISO 10846-3 connect mensuration indirectly " and " ISO 10846-5 excitations point mensuration " of the present invention.It is therein to swash
The relatively other two kinds of measuring methods of a measuring method are encouraged, its measurement apparatus and measuring method most simply and are easily achieved.Shown in Fig. 2
To put the experimental rig and basic principle schematic of mensuration measure track fastener system dynamic rate with excitation.Flexible element 1
(rail clip) is placed between one section of rail 3 and rigid base, by static load load isolation spring 2 and experimental rig framework every
Leave, the rigidity of static load loading isolation spring 2 should be less than the rigidity of Flexible element 1 (rail clip).Static state is preloaded by quiet
Carry loading isolation spring 2 to be added on Flexible element 1, exciting force loads ring flange 9 by the moving mass block of vibrator 4 and is added in steel
On the rail head of rail 1.
But with excitation point mensuration measurement have Low rigidity (<, should during the dynamic rate of fastener system 15kN/mm)
The limitation of mensuration has appeared out, and this is due to not consider there is very Low rigidity bullet when initially formulating these standards
The situation of property element.For rail clip system, what development and vibration and noise reducing with rail clip designing technique were required carries
Height, Low rigidity and non-linear rigidity fastener are widely applied, with moving for the Low rigidity fastener system for encouraging point mensuration acquisition
The effective frequency range of state rigidity is far below the practical application frequency range of fastener system in itself.
Excitation point mensuration is the exciting force F by measuring the input of Flexible element 11And displacement components u1Obtain encouraging crawl
Rigidity k11。
{ F }=[k] { u }
F1=k11u1+k12u2
F2=k21u1+k22u2
Its general principle is：In low frequency, effective mass of vibration inertia force of test system is far below the elasticity of Flexible element
Power, so above-mentioned formula can be reduced to the actual dynamic rate k of following formula, i.e. Flexible element21Excitation crawl can be used
State rigidity k11Come approximate, i.e. the dynamic rate of Flexible element 1 is：
k21≈k11=F1/u1
But find in actual applications, the hypothesis shown in above formula has limitation.The additional mass of test system and
Rigidity and the characteristic of Flexible element 1 can directly influence the frequency range and precision of test, when tested Flexible element 1 is with low
During stiffness characteristics, the excitation point dynamic rate k of test can be caused11Deviate transmission and move firm attitude k21, the excitation shown in above-mentioned formula
The basic assumption of point mensuration is no longer set up.
Therefore, although excitation point mensuration the characteristics of be it is simple and easy to apply its measurement result depend not only on experimental rig
Characteristic, while also being influenceed by the characteristic of flexible member (fastener).Subject matter is：
1. in high-frequency, the inertia force of the equivalent mass of vibration of whole test system is tested the bullet of Flexible element relatively
Property power increase, so as to cause to obtain the rigidity transmission result of accurate flexible member input and output side；
2. when test frequency is close to or higher than the combination intrinsic frequency of equivalent mass of vibration and whole test system rigidity,
Because the inertia force of equivalent mass of vibration accounts for leading, the resonance of whole test system leads to not the whole fastener system of accurate measurement
Dynamic rate.
Fig. 3 show the dynamic rate frequency spectrum of the Flexible element measured with excitation point mensuration, Flexible element (track button
Part) rigidity be 4kN/mm, spacer spring rigidity be 1.5kN/mm.It can be seen that in below 30Hz, the average activation point measured
Dynamic rate k11≈ 5.5kN/mm, i.e. Flexible element and spacer spring rigidity kiSum, kiThe lower dynamic rate measured is just
Closer to the true stiffness of Flexible element.As seen from Figure 3, begun to decline in below the 30Hz stiffness curves measured,
There is individual paddy peak near 100Hz, this is the equivalent mass of vibration of measuring system and the resonance point of system stiffness.With the increasing of frequency
Height, the influence increase of the equivalent mass of vibration of system, dynamic rate presents a rapidly rising trend.Measurement result shown in Fig. 3 only exists
Below 30Hz is effectively.
For the measurement result for the Flexible element for comparing different-stiffness, it is identical that Fig. 3 gives measuring condition simultaneously, but rigidity is
40kN/mm result, it can be seen that the effective frequency upper limit of measurement result has brought up to 80Hz, simultaneously because whole measuring system
The rigidity increase of (including Flexible element), the resonant frequency of the equivalent mass of vibration of system has also brought up to about 250Hz.
For fastener system, its design frequency scope is far above 30Hz, so excitation point measuring method is applied to low firm
Degree (<15kN/mm) reduction of its validity is many during fastener system, it is contemplated that can improve measurement result frequency range and
Precision.
The content of the invention
The purpose of the present invention is exactly the defect in order to overcome above-mentioned prior art presence and providing one kind can overcome
The limitation of ISO10846-5 excitation point mensurations simultaneously improves Flexible element dynamic rate measurement frequency scope and measurement accuracy
Method and apparatus.
The purpose of the present invention can be achieved through the following technical solutions：A kind of Flexible element dynamic rate measuring method,
The measurement of Flexible element dynamic rate is carried out using excitation point measuring method in ISO 10846-5, excitation point dynamic rate is obtained
k11, it is characterised in that while measuring the equivalent mass of vibration inertia rigidity ω of test system2m1With the equivalent support stiffness of test system
ki, by formula k21=k11+ω2m1‐kiCalculating obtains revised Flexible element dynamic rate k21, wherein, k21It is dynamic for Flexible element
State rigidity, k11For excitation point dynamic rate, ω is vibration frequency, m1The equivalent mass of vibration of test system, kiFor test system etc.
Imitate support stiffness.
Described excitation point dynamic rate k11It is to use excitation point measuring method measurement in ISO 10846-5 to encourage swashing for point
Encourage power F1And displacement components u1To obtain, i.e.,：k11=F1/u1。
The equivalent mass of vibration m of described test system1Equivalent fastener quality m comprising test system connector11And bullet
The Equivalent Elasticity element quality m of property unit in itself12, m1=m11+m12。
Described equivalent fastener quality m11Pass through the dynamic stiffness k of calibration test11rAnd known rigidity krStandard spring lead to
Cross formula m11=kr/ωr 2Obtain；
Wherein, ωrIt is the resonant frequency ω of standard springr, pass through the dynamic stiffness k of calibration test11rWith vibration frequency ω's
Tried to achieve in spectrogram, i.e. dynamic stiffness k11rFrequency in spectrogram at " paddy " point, as shown in Figure 5；The dynamic stiffness k of calibration test11r
It is the exciting force F for using excitation point measuring method measurement standard spring in ISO 10846-51And displacement components u1To obtain.
Described Equivalent Elasticity element quality m12Pass through formula m12=μmsCalculating is obtained, wherein, msFor the static state of Flexible element
Quality, μ=m11/mp, mpIt is location-plate sum under the additional mass i.e. weight of rail and spacer spring.
The equivalent support stiffness k of described test systemiTo encourage the static load that point measuring method is measured using ISO10846-5
Load the equivalent dynamic rate of isolation spring.
The test frequency set when described vibration frequency ω is test, in the range of 5~400Hz.
A kind of Flexible element dynamic rate measurement apparatus, including Flexible element, loading isolation spring, rail, vibrator, on
Crossbeam, column, vibrator bar, sill, rigid base, described Flexible element are arranged between rigid base and rail, institute
The rigid base stated connects upper crossbeam and sill by column, it is characterised in that also including Simple Harmonics signal generator, work(
Location-plate, force snesor, acceleration transducer, Signal Regulation collection under rate amplifier, spacer spring upper location-plate, spacer spring
And processing system；Described loading isolation spring is arranged under spacer spring upper location-plate and spacer spring between location-plate, its
Middle spacer spring upper location-plate is arranged on location-plate under sill bottom, spacer spring and is arranged on rail, and described single-frequency is humorous
The signal generator that shakes connects vibrator by power amplifier, and vibrator connects spacer spring by vibrator bar and force snesor
Lower location-plate, described acceleration transducer is arranged under spacer spring on location-plate, under described spacer spring location-plate and
Force snesor connection Signal Regulation collection and processing system；
Exciting force is passed by Simple Harmonics signal generator and power amplifier to vibrator, then by vibrator bar and power
Sensor applies exciting force to location-plate under spacer spring；The vibration of location-plate passes through acceleration transducer under rail and spacer spring
Signal and exciting force force snesor signal feeding Signal Regulation collection and processing system process analysis.
The specific method for measuring Flexible element dynamic rate using said apparatus comprises the following steps：
1) Flexible element is arranged between rigid base and rail, passes through Simple Harmonics signal generator and power amplification
Device applies exciting force to vibrator, and the frequency of exciting force is the center of each third-octave in the range of the vibration frequency ω of setting
Frequency, measures the exciting force F of the input of Flexible element1And displacement components u1Obtain excitation point dynamic stiffness k11, k11=F1/u1；Wherein swash
Encourage power F1Directly measured by exciting force force snesor, displacement components u1Drawn by the acceleration and Time Calculation that collect；k11For
The exciting force F that Signal Regulation is gathered and processing system processing is obtained1And displacement components u1The ratio between.
2) known rigidity k is selectedrStandard spring replace flexible member, measure the exciting force of the input of the standard spring
F1’And displacement components u1’Obtain the dynamic stiffness k of calibration test11r, k11r=F1’/u1’, pass through the dynamic stiffness k of calibration test11rWith vibration frequency
The resonant frequency ω of standard spring is tried to achieve in rate ω spectrogramr, i.e. dynamic stiffness k11rFrequency (Fig. 5 in spectrogram at " paddy " point
It is shown)；Pass through formula m11=kr/ωr 2Obtain equivalent fastener quality m11；Reduce equivalent fastener quality m11Elasticity can be improved single
First dynamic stiffness measurement frequency range and measurement accuracy.
3) measurement additional mass mpWith the rest mass m of Flexible elements, additional mass mpWeight and isolation bullet for rail
Location-plate (108) sum under spring, passes through formula μ=m11/mp, m12=μmsCalculating obtains Equivalent Elasticity element quality m12；
4) the equivalent mass of vibration m of test system1By being m1=m11+m12Calculate；
5) the equivalent dynamic rate k of isolation spring is loaded using the ISO10846-5 static loads for encouraging point measuring method to measurei；
6) formula k is passed through21=k11+ω2m1‐kiCalculate Flexible element dynamic rate k21, wherein k11Obtained for step (1)
Arrive, ω is setting value, m1 obtains for step (4), kiObtained for step (5).
According to the general principle of excitation point mensuration, described static load loads the equivalent dynamic stiffness k of isolation springiShould be remote
Less than the dynamic stiffness k of Flexible element21, but in the case that the rigidity of Flexible element in itself is relatively low, kiNo longer it is to neglect
Slightly disregard.
Described excitation point dynamic stiffness k11And equivalent mass of vibration m1, both ratio determines that tested Flexible element is moved
Rigidity k21(≈k11) initial effective frequency upper limit ω0For：ω0=[k11/(2m1)]0.5
Flexible element dynamic rate measurement frequency scope and measurement accuracy are improved, is to be based on formula k21=k11+ω2m1‐ki
To measured excitation point dynamic rate k11The actual dynamic stiffness k of the tested Flexible element obtained after being modified21It is effective
Upper frequency limit ω10It is initial effective frequency upper limit ω0More than 3 times.
Compared with prior art, the method provided by the invention is mainly characterized in that for being obtained with ISO 10846-5 excitations point measuring method
Flexible element excitation point dynamic stiffness k11It is improved, to obtain the true dynamic rate result of Flexible element.Dynamic rate
Improvement is in the excitation point dynamic stiffness k surveyed11It is middle to consider equivalent mass of vibration inertia rigidity ω2m1, and its test system is equivalent
Support stiffness kiInfluence and obtain the actual dynamic rate k of accurate tested Flexible element21；Described equivalent mass of vibration is used to
Property rigidity ω2m1It is equivalent mass of vibration m1With ω squares of product of vibration frequency, i.e. ω2m1；The equivalent branch of described test system
Hold rigidity kiIt is the equivalent dynamic rate that ISO10846-5 excitations point measuring method static load loads isolation spring.
Because with the raising of measurement frequency scope, the equivalent mass of vibration inertia rigidity ω of test system2m1To surveying
The excitation point dynamic rate k obtained11Contribution also increase, simultaneously because the Low rigidity characteristic of tested Flexible element, test system etc.
Imitate support stiffness kiAlso no longer it is negligible, so the present invention is to formula k21≈k11=F1/u1It is improved, it is contemplated that survey
The equivalent mass of vibration inertia rigidity of amount system and spacer spring rigidity are to excitation point dynamic rate k11Influence, by once surveying
Double measurement is carried out on the basis of amount, the accuracy and applicable frequency range for effectively improving dynamic stiffness measurement result is reached.
Brief description of the drawings
Fig. 1 Complex Elastic cellular system stiffness measurement theoretical models；
The existing Flexible element dynamic rate excitation point measuring principles of Fig. 2 a and schematic device；
Fig. 2 b Flexible elements dynamic rate excitation point measurement physical model figure；
The uncorrected Low rigidities of Fig. 3 (=4kN/mm,<15kN/mm) with higher stiffness (40kN/mm) rail clip dynamic stiffness
Spectrum compares；
Flexible element dynamic rate k after Fig. 4 present invention amendments21The basic theories principle displaying figure of each influence component；
Fig. 5 calibrates standard spring dynamic stiffness frequency spectrum；
The revised Low rigidities of Fig. 6 (being less than 15kN/mm) rail clip dynamic stiffness frequency spectrum；
Fig. 7 present invention excitation point measuring method measurement apparatus schematic diagram
Fig. 8 a light rail schematic diagrames；
Fig. 8 b Fig. 8 a upward view
Positioning plate structure schematic diagram under the light-duty spacer springs of Fig. 9；
Figure 10 is Fig. 9 A-A sectional views.
In figure：
1st, Flexible element；2nd, isolation spring is loaded；3rd, rail；4th, vibrator；101st, Simple Harmonics signal generator；102、
Power amplifier；103rd, upper crossbeam；104th, column；105th, vibrator bar；106th, sill；107th, spacer spring upper location-plate；
108th, location-plate under spacer spring；109th, force snesor；110th, acceleration transducer；111st, rigid base；112nd, Signal Regulation
Collection and processing system.
Embodiment
The present invention is described in detail with specific embodiment below in conjunction with the accompanying drawings.
Embodiment 1
As described in Fig. 7~10, a kind of Flexible element dynamic rate measurement apparatus, including Flexible element 1, loading isolation spring
2nd, rail 3, vibrator 4, Simple Harmonics signal generator 101, power amplifier 102, upper crossbeam 103, column 104, vibrator
Location-plate 108, force snesor 109, acceleration are passed under bar 105, sill 106, spacer spring upper location-plate 107, spacer spring
Sensor 110, rigid base 111, Signal Regulation collection and processing system 112, described Flexible element 1 are arranged on rigid base
Between 111 and rail 3, described rigid base 111 connects upper crossbeam 103 and sill 106 by column 104, and described adds
Loading vibration isolation spring 2 is arranged under spacer spring upper location-plate 107 and spacer spring between location-plate 108, wherein on spacer spring
Location-plate 107 is arranged on location-plate 108 under the bottom of sill 106, spacer spring and is arranged on rail 3, described Simple Harmonics
Signal generator 101 connects vibrator 4 by power amplifier 102, and vibrator 4 passes through vibrator bar 105 and force snesor 109
Location-plate 108 under spacer spring is connected, described acceleration transducer 110 is arranged under spacer spring on location-plate 108, described
Spacer spring under location-plate 108 and force snesor 109 connection Signal Regulation collection and processing system 112；Exciting force F passes through list
Frequency resonance signal generator 101 and power amplifier 102 give vibrator 4, then pass through 109 pairs of vibrator bar 105 and force snesor
Location-plate 108 applies exciting force under spacer spring；The vibration of location-plate 108 passes through acceleration sensing under rail 3 and spacer spring
The signal of device 110 and the signal feeding Signal Regulation collection of exciting force force snesor 109 and processing system 112 process analysis.
The specific method for measuring Flexible element dynamic rate using said apparatus comprises the following steps：
1) Flexible element 1 is arranged between rigid base 111 and rail 3, by Simple Harmonics signal generator 101 and
Power amplifier 102 applies exciting force to vibrator 4, and the frequency of exciting force is in the range of the vibration frequency ω of setting each 1/3
The centre frequency of octave, measures the exciting force F of the input of Flexible element1And displacement components u1Obtain excitation point dynamic stiffness k11, k11
=F1/u1；Wherein exciting force F1Directly measured by exciting force force snesor, displacement components u1Pass through the acceleration collected and time
Calculate；k11Gathered for Signal Regulation and processing system handles obtained exciting force F1And displacement components u1The ratio between.
2) known rigidity k is selectedrStandard spring replace flexible member, measure the exciting force of the input of the standard spring
F1' and displacement components u1' obtain the dynamic stiffness k of calibration test11r, k11r=F1’/u1', pass through the dynamic stiffness k of calibration test11rWith vibration
The resonant frequency ω of standard spring is tried to achieve in the spectrogram of frequencies omegar, i.e. dynamic stiffness k11rFrequency in spectrogram at " paddy " point
(shown in Fig. 5)；Pass through formula m11=kr/ωr 2Obtain equivalent fastener quality m11；Reduce equivalent fastener quality m11Bullet can be improved
Property unit dynamic stiffness measurement frequency range and measurement accuracy.
3) measurement additional mass mpWith the rest mass m of Flexible elements, additional mass mpWeight and isolation bullet for rail
The sum of location-plate 108 under spring, passes through formula μ=m11/mp, m12=μmsCalculating obtains Equivalent Elasticity element quality m12；
4) the equivalent mass of vibration m of test system1By being m1=m11+m12Calculate；
5) the equivalent dynamic rate k of isolation spring is loaded using the ISO10846-5 static loads for encouraging point measuring method to measurei；
6) formula k is passed through21=k11+ω2m1‐kiCalculate Flexible element dynamic rate k21, wherein k11Obtained for step (1)
Arrive, ω is setting value, m1 obtains for step (4), kiObtained for step (5).
What this example was provided is to have measured the dynamic for the fastener system that a static rigidity is 4kN/mm just with excitation point mensuration
The frequency spectrum of degree, the rigidity of the spacer spring of measuring system is 1.5kN/mm.
Experimental condition：
Test frequency scope 5-400Hz, test request is by being implemented as follows：
The frequency of exciting force is the centre frequency of each third-octave in 5-400Hz frequency ranges, and excitation speed is 80dB
(ref.5x10-8m/s), exciting force gives vibrator 4 by signal generator 101 and power amplifier 102, then passes through vibrator
Bar 105 and force snesor 109 apply exciting force to location-plate under spacer spring 108；Location-plate 108 under rail 3 and spacer spring
Vibration Signal Regulation collection is sent into by the signal of the signal of acceleration transducer 110 and exciting force force snesor 109 and located
Reason system 112 processes analysis.
The exciting force of each frequency band of measurement and the transmission function of displacement (measurement acceleration, then integrate twice)；
Contacting piece system applies static state and preloaded as 0kN.
According to formula k21=k11+ω2m1‐kiCalculated complex dynamic rate k11, as a result as shown in Figure 3.
Fig. 3 shows that, in the low frequency section less than 30Hz, the fastener dynamic rate of measurement is close to constant, and average value is
5.5kN/mm, is summation of the rigidity with spacer spring rigidity of fastener system.
The fastener system dynamic rate of measurement shown in Fig. 3 has individual peak valley near 100Hz, and this peak valley is test system
Intrinsic frequency, and frequency is when continuing to improve, and dynamic stiffness value starts in rising trend, and this is due to that the equivalent ginseng of test system is shaken
The influence of quality increases with frequency and gradually strengthened.
For sample fastener system, with the obtained dynamic rate of excitation point mensuration only under 30Hz frequency range effectively,
And the design frequency upper limit of fastener system requires more than 400Hz, such measurement result there is no practical value.
According to of the present invention, to obtain the actual dynamic rate frequency spectrum of Flexible element system, it is necessary to the survey shown in Fig. 3
Amount result is improved.Formula k21=k11+ω2m1‐kiWith Fig. 4 show influence measurement result principal element be measuring system etc.
Imitate mass of vibration m1Inertia rigidity ω2m1With the equivalent support stiffness k of test systemi。
How the present embodiment introduction measures the equivalent mass of vibration m of test system1Inertia rigidity ω2m1Frequency spectrum come
The dynamic rate of original measurement shown in Fig. 3 is modified.
Test device and measuring method are same as described above, are a difference in that lower than the Static stiffness of Flexible element with a Static stiffness
Many standard springs replace above-mentioned Flexible element.Then above-mentioned each Frequency point experimental procedure is repeated.In each third-octave
Centre frequency measurement F1And u1, that is, obtain impacting point dynamic rate k11r, because the former Flexible element of the ratio of rigidity of standard spring
Rigidity is much lower, and it is to k11rInfluence can be ignored.
Equivalent mass of vibration m1Equivalent fastener quality m comprising test system connector11With Flexible element in itself etc.
Imitate Flexible element quality m12.For the Equivalent Elasticity element quality m of standard spring its Flexible element in itself12Equivalent Elasticity can be neglected
Slightly disregard, at this moment, m1≈m11Can by Fig. 5 k11rSpectrogram in try to achieve resonant frequency ωrAnd the known pure spring unit of calibration
Nominal rigidity krBy formula m11=kr/ωr 2Calculate.And the actual rest mass m of connectorpBe rail 3 weight plus isolation
The weight of location-plate 108 under spring, mass ratio μ is by formula μ=m11/mpCalculate.
The equivalent mass m for the Flexible element tested12Formula m can be passed through12≈μmsEstimation.
By the dynamic rate in the dynamic rate and Fig. 3 in Fig. 5 according to formula k21=k11+ω2m1‐kiCalculated, just
The real dynamic stiffness of fastener system is can obtain, Fig. 6 is as a result seen, the dynamic stiffness effective frequency upper limit has brought up to 400Hz.Need note
Meaning, when being calculated, the influence of phase will be considered simultaneously.
Measurement apparatus shown in Fig. 7, measuring system frame requirements have enough rigidity, keep steady in exciting force loading procedure
It is fixed.
Embodiment 2：
Test and modification method and embodiment 1 are identical, simply to location-plate under the rail 3 and spacer spring in test device
108 replace location-plate under rail and steel spacer spring using low-density and high-strength alloy materials, and rail's end portion scabbled with
Mass of vibration is reduced, is the rail 3 that head is scabbled as shown in Figure 8, is the spacer spring of the light-duty optimization of correspondence as shown in figs. 9-10
Lower location-plate 108, makes equivalent fastener quality m11Original 25% is reduced to, so that the effective frequency upper limit improves about 2 times or so.
Above-described is only the preferred embodiment of the present invention.It should be pointed out that for one of ordinary skill in the art
For, under the premise without departing from the principles of the invention, the technical characteristic that creative work can just be associated is needed not move through, may be used also
To make some variations and modifications, these changes are obviously regarded as equivalent feature, still fall within protection scope of the present invention.
Claims (7)
1. a kind of Flexible element dynamic rate measuring method, carries out elasticity single using excitation point measuring method in ISO 10846-5
The measurement of first dynamic rate, obtains excitation point dynamic rate k11, it is characterised in that while measuring the equivalent mass of vibration of test system
Inertia rigidity ω2m1With the equivalent support stiffness k of test systemi, by formula k21=k11+ω2m1‐kiCalculating obtains revised elasticity
Unit dynamic rate k21, wherein, k21For Flexible element dynamic rate, k11For excitation point dynamic rate, ω is vibration frequency, m1
The equivalent mass of vibration of test system, kiFor the equivalent support stiffness of test system.
2. a kind of Flexible element dynamic rate measuring method according to claim 1, it is characterised in that described excitation point
Dynamic rate k11It is the exciting force F for using excitation point measuring method measurement excitation point in ISO 10846-51And displacement components u1To obtain
, i.e.,：k11=F1/u1。
3. a kind of Flexible element dynamic rate measuring method according to claim 1, it is characterised in that described test system
Unite equivalent mass of vibration m1Equivalent fastener quality m comprising test system connector11With the Equivalent Elasticity of Flexible element in itself
Element quality m12, m1=m11+m12。
4. a kind of Flexible element dynamic rate measuring method according to claim 3, it is characterised in that described equivalent company
Fitting quality m11Pass through the dynamic stiffness k of calibration test11rAnd known rigidity krStandard spring pass through formula m11=kr/ωr 2Obtain；
Wherein, ωrIt is the resonant frequency ω of standard springr, pass through the dynamic stiffness k of calibration test11rWith vibration frequency ω frequency spectrum
Tried to achieve in figure, i.e. dynamic stiffness k11rFrequencies omega in spectrogram at " paddy " pointr；The dynamic stiffness k of calibration test11rIt is to use ISO
The exciting force F of excitation point measuring method measurement standard spring in 10846-51And displacement components u1To obtain；
Described Equivalent Elasticity element quality m12Pass through formula m12=μmsCalculating is obtained, wherein, msFor the static matter of Flexible element
Amount, μ=m11/mp, mpIt is location-plate sum under the additional mass i.e. weight of rail and spacer spring.
5. a kind of Flexible element dynamic rate measuring method according to claim 1, it is characterised in that described test system
Unite equivalent support stiffness kiTo load the equivalent dynamic of isolation spring using the ISO10846-5 static loads for encouraging point measuring method to measure
State rigidity.
6. a kind of Flexible element dynamic rate measuring method according to claim 1, it is characterised in that described vibration is frequently
The test frequency set when rate ω is test, in the range of 5~400Hz.
7. a kind of Flexible element dynamic rate measurement apparatus, including Flexible element (1), loading isolation spring (2), rail (3), swash
Shake device (4), upper crossbeam (103), column (104), vibrator bar (105), sill (106), rigid base (111), described
Flexible element (1) is arranged between rigid base (111) and rail (3), and described rigid base (111) passes through column (104)
Crossbeam (103) and sill (106) in connection, it is characterised in that also put including Simple Harmonics signal generator (101), power
Location-plate (108), force snesor (109), acceleration are passed under big device (102), spacer spring upper location-plate (107), spacer spring
Sensor (110), Signal Regulation collection and processing system (112)；Described loading isolation spring (2) is arranged on spacer spring fixed
Under position plate (107) and spacer spring between location-plate (108), wherein spacer spring upper location-plate (107) is arranged on sill
(106) location-plate (108) is arranged on rail (3) under bottom, spacer spring, described Simple Harmonics signal generator (101)
Vibrator (4) is connected by power amplifier (102), vibrator (4) is connected by vibrator bar (105) and force snesor (109)
Location-plate under spacer spring (108) is connect, described acceleration transducer (110) is arranged on location-plate under spacer spring (108),
Location-plate (108) and force snesor (109) connection Signal Regulation collection and processing system (112) under described spacer spring；
Exciting force gives vibrator (4) by Simple Harmonics signal generator (101) and power amplifier (102), then passes through exciting
Device bar (105) and force snesor (109) apply exciting force to location-plate under spacer spring (108)；Under rail (3) and spacer spring
The vibration of location-plate (108) is sent into and believed by the signal of acceleration transducer (110) and the signal of exciting force force snesor (109)
Number regulation collection and processing system (112) process analysis.
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| CN108168804A (en) * | 2017-12-01 | 2018-06-15 | 中国直升机设计研究所 | The lateral course stiffness and damping testing stand of helicopter wheel |
| CN108917988A (en) * | 2018-06-14 | 2018-11-30 | 上海工程技术大学 | A kind of portable wheel-rail lateral force caliberating device |
| CN109540441A (en) * | 2019-01-08 | 2019-03-29 | 重庆青山工业有限责任公司 | Automobile gearbox is preloading lower internal vibration transmission function test macro and method |
| CN109883630A (en) * | 2019-03-13 | 2019-06-14 | 北京慧天丰石油机械有限公司 | Six fast rotational viscometer torsional spring dynamometers |
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| CN108168804A (en) * | 2017-12-01 | 2018-06-15 | 中国直升机设计研究所 | The lateral course stiffness and damping testing stand of helicopter wheel |
| CN108917988A (en) * | 2018-06-14 | 2018-11-30 | 上海工程技术大学 | A kind of portable wheel-rail lateral force caliberating device |
| CN108917988B (en) * | 2018-06-14 | 2023-07-04 | 上海工程技术大学 | Portable wheel rail transverse force calibration device |
| CN109540441A (en) * | 2019-01-08 | 2019-03-29 | 重庆青山工业有限责任公司 | Automobile gearbox is preloading lower internal vibration transmission function test macro and method |
| CN109883630A (en) * | 2019-03-13 | 2019-06-14 | 北京慧天丰石油机械有限公司 | Six fast rotational viscometer torsional spring dynamometers |
| CN111307474A (en) * | 2020-03-11 | 2020-06-19 | 清友(苏州)汽车技术有限公司 | Method for testing vibration isolation performance of automotive suspension spring gasket based on MTS loading device |
| CN112729734B (en) * | 2020-12-04 | 2022-11-25 | 中国直升机设计研究所 | Method for measuring transfer characteristics of series-type vibration isolator |
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| CN112903222A (en) * | 2020-12-25 | 2021-06-04 | 日照华斯特林科技有限公司 | System and method for measuring quality of deformation part of plate spring |
| CN112903222B (en) * | 2020-12-25 | 2022-09-30 | 日照华斯特林科技有限公司 | System and method for measuring quality of deformation part of plate spring |
| CN113124998B (en) * | 2021-03-26 | 2022-09-20 | 中铁二院工程集团有限责任公司 | Rail rigidity time-frequency measurement method based on P2 force vibration |
| CN113124998A (en) * | 2021-03-26 | 2021-07-16 | 中铁二院工程集团有限责任公司 | Rail rigidity time-frequency measurement method based on P2 force vibration |
| CN115219124A (en) * | 2021-04-22 | 2022-10-21 | 广州汽车集团股份有限公司 | Buckle performance testing device and method and automotive interior system |
| CN113324714A (en) * | 2021-04-27 | 2021-08-31 | 上海卫星工程研究所 | Method and system for measuring rigidity of cable between double super satellite cabins in orbit |
| CN113358305A (en) * | 2021-06-02 | 2021-09-07 | 中国铁道科学研究院集团有限公司铁道建筑研究所 | Track structure dynamic stiffness identification method, device, system, medium and equipment |
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