CN107941488A - A kind of vehicle sheet steel spring dynamic stiffness assay method - Google Patents
A kind of vehicle sheet steel spring dynamic stiffness assay method Download PDFInfo
- Publication number
- CN107941488A CN107941488A CN201711156386.5A CN201711156386A CN107941488A CN 107941488 A CN107941488 A CN 107941488A CN 201711156386 A CN201711156386 A CN 201711156386A CN 107941488 A CN107941488 A CN 107941488A
- Authority
- CN
- China
- Prior art keywords
- msub
- mrow
- spring
- mfrac
- dynamic stiffness
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M13/00—Testing of machine parts
Landscapes
- Physics & Mathematics (AREA)
- General Physics & Mathematics (AREA)
- Springs (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The present invention relates to a kind of vehicle sheet steel spring dynamic stiffness assay method, belong to automotive suspension technical field, resonant frequency on spring is measured by vehicle driving-cycle, based under resonant frequency on spring and spring, sprung mass, the inverse problem of parameter leaf spring dynamic stiffness such as tire stiffness, can accurately and efficiently measure leaf spring dynamic stiffness when resonating on spring.
Description
Technical field
The present invention relates to a kind of vehicle sheet steel spring dynamic stiffness assay method, belong to automotive suspension technical field.
Background technology
Leaf spring is a kind of flexible member in automotive suspension, and since its is simple in structure, maintenance is convenient, is manufactured into
This is low and the features such as can double as guiding mechanism, the extensive use in commercial car.In Leaf Spring Suspension System, resonant frequency on spring
And based on this matched Parameters of Dampers be influence vehicle ride comfort an important factor for, wherein, resonant frequency is subject to steel on spring
The influence of flat spring dynamic rate, but influenced by rubbing, the dynamic rate that leaf spring is shown when driving in vehicle
The few leaf spring vehicle poor commonly greater than design rigidity, particularly multiple-leaf spring vehicle or some lubrications, its dynamic stiffness may several times
In design rigidity, therefore, if suspension system progress dynamic properties design is occurred based on the design rigidity of leaf spring larger
Deviation, the ride comfort of vehicle is deteriorated.
At present, domestic and foreign scholars' influence of leaf spring friction by experimental study, it is indicated that axle load is to influence with amplitude
The factor of dynamic stiffness, dynamic stiffness all may be different under different axle loads, road excitation, tire excitation for same frame leaf spring.
Therefore, may be because of the shadow of friction if being loaded by rack, the design rigidity Prediction of Suspension system dynamic characteristic of unloading curve measure
Pilot causes relatively large deviation；Alternatively, measuring its dynamic rate by the operating mode that resonates on bench simulation spring then tests process cumbersome, the cycle
It is long, need to dismantle leaf spring during experiment, it is time-consuming and laborious.Therefore, leaf spring is dynamic firm when how to obtain resonance on spring
Degree becomes the problem of urgent need to resolve in suspension system dynamic properties design.
The content of the invention
To solve technical deficiency above, the present invention provides a kind of vehicle sheet steel spring dynamic stiffness assay method, leads to
Cross vehicle driving-cycle measure spring on resonant frequency, based under resonant frequency on spring and spring, sprung mass, tire stiffness etc. ginseng
Number reverse leaf spring dynamic stiffness, can accurately and efficiently measure leaf spring dynamic stiffness when resonating on spring.
Technical scheme is as follows：A kind of vehicle sheet steel spring dynamic stiffness assay method, mainly includes the following steps that：
Step 1, vehicle bridge position by vehicle after the arrangement acceleration transducer of spring upper frame position with driving into test road under spring
Road；
Step 2, carries out driving cycle test, and the acceleration signal that acceleration transducer is measured carries out frequency-domain transform, base
In covibration on frequency spectrum discerning spring, resonant frequency f on spring is recordedi；
Step 3, according to resonant frequency f on springi, unsprung mass m1, sprung mass m2With tire stiffness KtSpring is tried to achieve in calculating
Leaf spring dynamic stiffness k, calculation formula are during upper resonance,
Technical scheme further includes：Resonant frequency is averaged and is calculated on spring in the step 3, is denoted as
Mean resonance frequency fe, the calculation formula of leaf spring dynamic stiffness k is when resonating on spring,
Technical scheme further includes：The mean resonance frequency feAcquisition methods be,
The first step, when vehicle is travelling working condition measurement, based on covibration on frequency spectrum discerning spring, when resonating on record spring
Rotary speed property parameter；
Second step, carries out N wheels based on rotary speed property parameter and at the uniform velocity tests, wherein N values 2-100, record often wheel test
Resonant frequency is f on springi, wherein i=1,2,3 ..., N；
3rd step, is averaged resonant frequency on N number of spring, obtains mean resonance frequency
Technical scheme further includes：The test road at the uniform velocity tested in the second step is unidirectional same
Section.
Technical scheme further includes：Rotary speed property parameter in the first step is engine under speed, certain shelves
One in rotating speed, certain grade of lower drive shaft rotating speed.
Technical scheme further includes：The measurement direction of acceleration transducer is perpendicular to the ground in the step 1.
Technical scheme further includes：Driving cycle is one in accelerating mode, coasting mode in the step 2
Kind.
Technical scheme further includes：When the vehicle bridge position under spring and spring upper frame position in the step 2
Acceleration transducer measured value frequency-domain transform after amplitude-frequency value in same frequency to occur amplitude in local maximum and spring at the same time big
The amplitude and during phase frequency value equal under the same frequency under spring, can recognize that and be recorded as covibration on spring, the same frequency
Resonant frequency f on springi。
Technical scheme further includes：Test road in the step 1 is high-grade highway flat segments.
The beneficial effects of the invention are as follows：This method is based on the operating mode measure leaf spring dynamic stiffness that resonates on spring, by spring
Acceleration transducer is placed in lower vehicle bridge position with spring upper frame position, and resonant frequency on spring is measured using vehicle driving-cycle, it
Afterwards again based under resonant frequency on spring and spring, the inverse problem of parameter leaf spring dynamic stiffness such as sprung mass, tire stiffness, experiment knot
Influential effect of the friction to dynamic stiffness is embodied in fruit, relatively loading, the method for unloading test measure rigidity are more accurate, also,
Leaf spring need not be dismantled, without bench test, can more efficiently measure leaf spring dynamic stiffness.
Brief description of the drawings
Fig. 1 is the assay method flow chart of the present invention.
Embodiment
Below in conjunction with attached drawing, by embodiment, the invention will be further described.
The vehicle sheet steel spring dynamic stiffness assay method of the present invention, vehicle bridge position is placed with spring upper frame position and is added under spring
Velocity sensor, resonant frequency on spring is measured by vehicle driving-cycle, based under resonant frequency on spring and spring, matter on spring
The inverse problem of parameter leaf spring dynamic stiffness such as amount, tire stiffness, can rapidly and accurately measure leaf spring dynamic stiffness when resonating on spring,
Design for leaf spring is instructed and verified.
The embodiment of the present invention one：
By taking truck front overhang uses Leaf Spring Suspension System as an example.
Wherein, unsprung mass m1=369.61kg, sprung mass m2=1675.39kg, both sides tire global stiffness kt=
960N/mm.Determination step is as follows：
Step 1：Arrange unidirectional acceleration transducer at get off bridge position and spring upper frame position of preceding suspension spring, and should plus
The measurement direction of velocity sensor is perpendicular to the ground, facilitates the use the change of vertical data to determine whether resonating.Choosing
Suburb high-grade highway flat segments are taken as test road, i.e. select the section without turn, slope to be tested as far as possible.In order to
The accuracy of determination data is improved, reduces external testing condition to the adverse effect of determination data, can be by the test road of selection
Condition control is less than 1% in road gradient, and unevenness is uniformly without mutation, and road surface is dried during test.
Step 2：Tested using accelerating mode, vehicle bridge measuring point and vehicle frame measuring point during 4 grades of rotating speed of transmission shaft about 960rpm
There is local peaking in amplitude-frequency value in direction perpendicular to the ground and vehicle frame measuring point is more than vehicle bridge measuring point, and phase frequency value is equal, this is on preceding suspension spring
Resonance state, at this time respective frequencies fi=2.870Hz is resonant frequency on spring.
Step 3：By resonant frequency f on springi=2.870Hz, unsprung mass m1=369.61kg, sprung mass m2=
1675.39kg, tire stiffness kt=960N/mm brings calculation formula into：
Reverse leaf spring dynamic stiffness k=776N/mm.
The embodiment of the present invention two, the suspension system of selection is identical with embodiment one, the difference is that being carried out to resonant frequency
Test of many times, which is averaged, to be calculated, to improve the accuracy of measurement result.As shown in Figure 1, specific determination step is as follows：
Step 1：Unidirectional acceleration transducer is arranged at get off bridge position and spring upper frame position of preceding suspension spring, chooses suburb
Certain high-grade highway flat segments is test road, and road gradient is less than 1%, and unevenness is uniformly without mutation, and road surface is dried during test.
Step 2：Rotating speed of transmission shaft during using 4 grades is tested as characterisitic parameter using accelerating mode, and 4 grades of transmission shafts turn
There is local peaking to vehicle bridge measuring point in amplitude-frequency value in direction perpendicular to the ground and vehicle frame measuring point is more than car with vehicle frame measuring point during speed about 960rpm
Bridge measuring point, phase frequency value is equal, to resonate on preceding suspension spring.
Step 3：Keep 4 grades of rotating speed of transmission shaft 960rpm operating modes of vehicle to carry out 10 groups at the uniform velocity to test, often wheel test Jun roads
The same direction on road, same section of section carry out, to ensure the accuracy of determination data.Based on resonant frequency f on frequency spectrum discerning spring1
=2.872Hz, f2=2.876Hz, f3=2.889Hz, f4=2.884Hz, f5=2.875Hz, f6=2.864Hz, f7=
2.867Hz f8=2.879Hz, f9=2.866Hz, f10=2.891Hz.
Step 4：Bring resonant frequency on 10 springs into calculation formula：
Calculate mean resonance frequency fe=2.876Hz.
Step 5：By mean resonance frequency fe=2.876Hz, unsprung mass m1=369.61kg, sprung mass m2=
1675.39kg, tire stiffness kt=960N/mm brings calculation formula into：
Reverse leaf spring dynamic stiffness k=786N/mm.
The above, is only presently preferred embodiments of the present invention, and limitation in any form is not done to the present invention, all at this
All any modification, equivalent and improvement etc. are done within the spirit and principle of invention, should be included in protection scope of the present invention
Within.
Claims (9)
1. a kind of vehicle sheet steel spring dynamic stiffness assay method, mainly includes the following steps that：
Step 1, vehicle bridge position by vehicle after the arrangement acceleration transducer of spring upper frame position with driving into test road under spring；
Step 2, carries out driving cycle test, and the acceleration signal that acceleration transducer is measured carries out frequency-domain transform, based on frequency
Covibration on spectrum discrimination spring, records resonant frequency f on springi；
Step 3, according to resonant frequency f on springi, unsprung mass m1, sprung mass m2With tire stiffness KtCalculating is tried to achieve and resonated on spring
When leaf spring dynamic stiffness k, calculation formula is,
<mrow>
<msup>
<mrow>
<mo>(</mo>
<mn>2</mn>
<msub>
<mi>&pi;f</mi>
<mi>i</mi>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>-</mo>
<mfrac>
<mn>1</mn>
<mn>2</mn>
</mfrac>
<mrow>
<mo>(</mo>
<mfrac>
<mrow>
<mi>k</mi>
<mo>+</mo>
<msub>
<mi>k</mi>
<mi>t</mi>
</msub>
</mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
</mfrac>
<mo>+</mo>
<mfrac>
<mi>k</mi>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mfrac>
<mo>)</mo>
</mrow>
<mo>+</mo>
<msqrt>
<mrow>
<mfrac>
<mn>1</mn>
<mn>4</mn>
</mfrac>
<msup>
<mrow>
<mo>(</mo>
<mfrac>
<mrow>
<mi>k</mi>
<mo>+</mo>
<msub>
<mi>k</mi>
<mi>t</mi>
</msub>
</mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
</mfrac>
<mo>+</mo>
<mfrac>
<mi>k</mi>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mfrac>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>-</mo>
<mfrac>
<mrow>
<msub>
<mi>kk</mi>
<mi>t</mi>
</msub>
</mrow>
<mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mrow>
</mfrac>
</mrow>
</msqrt>
<mo>=</mo>
<mn>0.</mn>
</mrow>
A kind of 2. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 1, it is characterised in that：In the step 3
Resonant frequency, which is averaged, on spring is calculated, and is denoted as mean resonance frequency fe, the meter of leaf spring dynamic stiffness k when resonating on spring
Calculating formula is,
<mrow>
<msup>
<mrow>
<mo>(</mo>
<mn>2</mn>
<msub>
<mi>&pi;f</mi>
<mi>e</mi>
</msub>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>-</mo>
<mfrac>
<mn>1</mn>
<mn>2</mn>
</mfrac>
<mrow>
<mo>(</mo>
<mfrac>
<mrow>
<mi>k</mi>
<mo>+</mo>
<msub>
<mi>k</mi>
<mi>t</mi>
</msub>
</mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
</mfrac>
<mo>+</mo>
<mfrac>
<mi>k</mi>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mfrac>
<mo>)</mo>
</mrow>
<mo>+</mo>
<msqrt>
<mrow>
<mfrac>
<mn>1</mn>
<mn>4</mn>
</mfrac>
<msup>
<mrow>
<mo>(</mo>
<mfrac>
<mrow>
<mi>k</mi>
<mo>+</mo>
<msub>
<mi>k</mi>
<mi>t</mi>
</msub>
</mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
</mfrac>
<mo>+</mo>
<mfrac>
<mi>k</mi>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mfrac>
<mo>)</mo>
</mrow>
<mn>2</mn>
</msup>
<mo>-</mo>
<mfrac>
<mrow>
<msub>
<mi>kk</mi>
<mi>t</mi>
</msub>
</mrow>
<mrow>
<msub>
<mi>m</mi>
<mn>1</mn>
</msub>
<msub>
<mi>m</mi>
<mn>2</mn>
</msub>
</mrow>
</mfrac>
</mrow>
</msqrt>
<mo>=</mo>
<mn>0.</mn>
</mrow>
A kind of 3. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 2, it is characterised in that：The mean resonance
Frequency feAcquisition methods be,
The first step, when vehicle is travelling working condition measurement, based on covibration on frequency spectrum discerning spring, records and turns when resonating on spring
Fast characterisitic parameter；
Second step, carries out N wheels based on rotary speed property parameter and at the uniform velocity tests, wherein N values 2-100, record is often taken turns on the spring of test
Resonant frequency is fi, wherein i=1,2,3 ..., N；
3rd step, is averaged resonant frequency on N number of spring, obtains mean resonance frequency
A kind of 4. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 3, it is characterised in that：In the second step
The test road at the uniform velocity tested is unidirectional same a road section.
A kind of 5. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 3, it is characterised in that：In the first step
Rotary speed property parameter be one in speed, certain grade of lower engine speed, certain grade of lower drive shaft rotating speed.
A kind of 6. vehicle sheet steel spring dynamic stiffness assay method as described in claim 1 to 5 is any, it is characterised in that：It is described
The measurement direction of acceleration transducer is perpendicular to the ground in step 1.
A kind of 7. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 6, it is characterised in that：In the step 2
Driving cycle is one kind in accelerating mode, coasting mode.
A kind of 8. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 1, it is characterised in that：In the step 2
Amplitude-frequency value is same after the acceleration transducer measured value frequency-domain transform at the vehicle bridge position under spring and spring upper frame position
When frequency amplitude occurs on local maximum and spring and is more than under spring amplitude and phase frequency value equal under the same frequency at the same time, it can know
Covibration, the same frequency resonant frequency f on spring Wei not be recorded as on springi。
A kind of 9. vehicle sheet steel spring dynamic stiffness assay method as claimed in claim 1, it is characterised in that：In the step 1
Test road be high-grade highway flat segments.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711156386.5A CN107941488B (en) | 2017-11-20 | 2017-11-20 | Method for measuring dynamic stiffness of vehicle leaf spring |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201711156386.5A CN107941488B (en) | 2017-11-20 | 2017-11-20 | Method for measuring dynamic stiffness of vehicle leaf spring |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN107941488A true CN107941488A (en) | 2018-04-20 |
| CN107941488B CN107941488B (en) | 2020-03-20 |
Family
ID=61929154
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN201711156386.5A Active CN107941488B (en) | 2017-11-20 | 2017-11-20 | Method for measuring dynamic stiffness of vehicle leaf spring |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN107941488B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112067271A (en) * | 2020-09-14 | 2020-12-11 | 东风汽车底盘系统有限公司 | Single-leaf spring fatigue test method and device |
| CN114646475A (en) * | 2022-03-16 | 2022-06-21 | 中国第一汽车股份有限公司 | Four-column ride comfort test data processing method and device and electronic equipment |
Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202133537U (en) * | 2011-06-09 | 2012-02-01 | 南京林业大学 | Dynamic stiffness testing device |
| CN102729760A (en) * | 2012-07-17 | 2012-10-17 | 山东理工大学 | Real-time optimal damping control algorithm of automobile semi-active suspension system |
| CN102980756A (en) * | 2012-11-20 | 2013-03-20 | 西南交通大学 | Method and system for testing dynamic stiffness |
| CN103121475A (en) * | 2013-03-08 | 2013-05-29 | 山东理工大学 | Design method for optimal damping ratio of suspension system of cab |
| CN104156547A (en) * | 2014-09-03 | 2014-11-19 | 山东理工大学 | Method for designing optimal damping characteristics of shock absorber of vehicle steel plate spring suspension system |
| CN104200028A (en) * | 2014-09-03 | 2014-12-10 | 山东理工大学 | Method for designing power of energy regenerative suspension generator based on vehicle parameters |
| CN104198197A (en) * | 2014-09-11 | 2014-12-10 | 重庆长安汽车股份有限公司 | Method and device for testing dynamic stiffness of car-body mounting points |
| CN104309437A (en) * | 2014-10-23 | 2015-01-28 | 山东理工大学 | Design method for real-time optimal control of nonlinear rigidity of vehicle air suspension |
| CN105564176A (en) * | 2016-03-12 | 2016-05-11 | 周长城 | Design method of few-leaf variable-section plate spring based on vehicle parameters |
| CN106908255A (en) * | 2017-01-20 | 2017-06-30 | 三明学院 | The analogy method of vehicle vibration performance is obtained based on the test of single shake table suspension |
| CN106951588A (en) * | 2017-02-16 | 2017-07-14 | 江苏大学 | A kind of vehicle ISD suspension research methods based on coupling effect |
-
2017
- 2017-11-20 CN CN201711156386.5A patent/CN107941488B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN202133537U (en) * | 2011-06-09 | 2012-02-01 | 南京林业大学 | Dynamic stiffness testing device |
| CN102729760A (en) * | 2012-07-17 | 2012-10-17 | 山东理工大学 | Real-time optimal damping control algorithm of automobile semi-active suspension system |
| CN102980756A (en) * | 2012-11-20 | 2013-03-20 | 西南交通大学 | Method and system for testing dynamic stiffness |
| CN103121475A (en) * | 2013-03-08 | 2013-05-29 | 山东理工大学 | Design method for optimal damping ratio of suspension system of cab |
| CN104156547A (en) * | 2014-09-03 | 2014-11-19 | 山东理工大学 | Method for designing optimal damping characteristics of shock absorber of vehicle steel plate spring suspension system |
| CN104200028A (en) * | 2014-09-03 | 2014-12-10 | 山东理工大学 | Method for designing power of energy regenerative suspension generator based on vehicle parameters |
| CN104198197A (en) * | 2014-09-11 | 2014-12-10 | 重庆长安汽车股份有限公司 | Method and device for testing dynamic stiffness of car-body mounting points |
| CN104309437A (en) * | 2014-10-23 | 2015-01-28 | 山东理工大学 | Design method for real-time optimal control of nonlinear rigidity of vehicle air suspension |
| CN105564176A (en) * | 2016-03-12 | 2016-05-11 | 周长城 | Design method of few-leaf variable-section plate spring based on vehicle parameters |
| CN106908255A (en) * | 2017-01-20 | 2017-06-30 | 三明学院 | The analogy method of vehicle vibration performance is obtained based on the test of single shake table suspension |
| CN106951588A (en) * | 2017-02-16 | 2017-07-14 | 江苏大学 | A kind of vehicle ISD suspension research methods based on coupling effect |
Non-Patent Citations (2)
| Title |
|---|
| 刘守银 等: ""多片簧悬架簧上振动特性的研究"", 《农业装备与车辆工程》 * |
| 向师欣: ""自卸汽车前悬架变刚度钢板弹簧对平顺性影响的研究"", 《中国优秀硕士学位论文全文数据库 工程科技II辑》 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN112067271A (en) * | 2020-09-14 | 2020-12-11 | 东风汽车底盘系统有限公司 | Single-leaf spring fatigue test method and device |
| CN114646475A (en) * | 2022-03-16 | 2022-06-21 | 中国第一汽车股份有限公司 | Four-column ride comfort test data processing method and device and electronic equipment |
| CN114646475B (en) * | 2022-03-16 | 2024-05-03 | 中国第一汽车股份有限公司 | Four-column ride comfort test data processing method and device and electronic equipment |
Also Published As
| Publication number | Publication date |
|---|---|
| CN107941488B (en) | 2020-03-20 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| CN104120644B (en) | A kind of detection method of road-surface evenness based on Gravity accelerometer | |
| WO2015174323A1 (en) | Method for predicting rolling resistance of tire and device for predicting rolling resistance of tire | |
| WO2007060836A1 (en) | Tire wear test method | |
| JP2014530347A (en) | Defect diagnosis method and apparatus for component parts in automobile chassis system | |
| CN100485348C (en) | Forecast method for change of tyre radial force | |
| US10024763B2 (en) | Efficient high speed uniformity measurements using speed ramps | |
| CN110631786A (en) | Rapid evaluation method for bearing capacity of beam bridge based on parking vibration response | |
| US20120316800A1 (en) | System for predicting vehicle vibration or acoustic response | |
| CN107941488A (en) | A kind of vehicle sheet steel spring dynamic stiffness assay method | |
| Siegel et al. | Smartphone-based wheel imbalance detection | |
| CN105653759A (en) | Apparatus for estimating vehicle mass using tire air pressure and method thereof | |
| Prażnowski et al. | Classification of the road surface condition on the basis of vibrations of the sprung mass in a passenger car | |
| US7941255B2 (en) | Process and apparatus for detecting damper damage | |
| Kising et al. | Dynamic characteristics of large tyres | |
| CN101963519B (en) | Road test-simulated standard-state fuel consumption detection method based on bench test | |
| Jin et al. | Robust algorithm of indirect tyre pressure monitoring system based on tyre torsional resonance frequency analysis | |
| JP4431023B2 (en) | Tire vibration characteristics measurement method | |
| Ślaski et al. | The influence of damping changes on vertical dynamic loads of wheel–experimental investigations | |
| Koulocheris et al. | Dynamic analysis of the suspension system of a heavy vehicle through experimental and simulation procedure | |
| Ejsmont et al. | The influence of road surface unevenness on tyre rolling resistance | |
| Zaabar et al. | Investigation of the relationship between dynamic axle load, roughness and fuel consumption | |
| KR101829436B1 (en) | Test apparatus for measurement of dynamic spring rate of high speed rotating tire | |
| CN104266849B (en) | A kind of vehicle tyre damping test device and analysis method | |
| JP4255748B2 (en) | Evaluation method of circumferential torsional characteristics of tire | |
| Rothhämel et al. | On comfort in cycle carriers for child transport |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| PB01 | Publication | ||
| PB01 | Publication | ||
| SE01 | Entry into force of request for substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| GR01 | Patent grant | ||
| GR01 | Patent grant |