CN106872105A - Whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing - Google Patents
Whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing Download PDFInfo
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- CN106872105A CN106872105A CN201710284053.4A CN201710284053A CN106872105A CN 106872105 A CN106872105 A CN 106872105A CN 201710284053 A CN201710284053 A CN 201710284053A CN 106872105 A CN106872105 A CN 106872105A
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- 238000012360 testing method Methods 0.000 claims abstract description 61
- 230000001133 acceleration Effects 0.000 claims abstract description 47
- 230000005540 biological transmission Effects 0.000 claims abstract description 35
- 238000000034 method Methods 0.000 claims abstract description 11
- 239000000523 sample Substances 0.000 claims description 3
- 230000006641 stabilisation Effects 0.000 claims description 3
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- 239000011159 matrix material Substances 0.000 abstract description 2
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Classifications
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M1/00—Testing static or dynamic balance of machines or structures
- G01M1/14—Determining imbalance
- G01M1/16—Determining imbalance by oscillating or rotating the body to be tested
- G01M1/28—Determining imbalance by oscillating or rotating the body to be tested with special adaptations for determining imbalance of the body in situ, e.g. of vehicle wheels
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- 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
- G01M13/02—Gearings; Transmission mechanisms
- G01M13/028—Acoustic or vibration analysis
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- G—PHYSICS
- G01—MEASURING; TESTING
- G01M—TESTING STATIC OR DYNAMIC BALANCE OF MACHINES OR STRUCTURES; TESTING OF STRUCTURES OR APPARATUS, NOT OTHERWISE PROVIDED FOR
- G01M17/00—Testing of vehicles
- G01M17/007—Wheeled or endless-tracked vehicles
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- General Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Measurement Of Mechanical Vibrations Or Ultrasonic Waves (AREA)
Abstract
The invention discloses whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing, by speed changer, three separable assembleds of intermediate supports and drive axle are into transmission system totality, and in speed changer, unbalance dynamic face is set in intermediate supports and drive axle, by arranging unidirectional acceleration sensor on each unbalance dynamic face, in batches test mass is added in a certain unbalance dynamic face, and calculate one group influence coefficient of two other split on the split unbalance dynamic face, so as to construct transmission system general impacts coefficient matrix, and the remaining unbalancing value of transmission system is calculated by influence coefficient method.The method that the present invention is provided can test out the remaining unbalancing value and phase of power train under whole vehicle state, breach the limitation of aptitude test only on stand or on unbalance dynamic machine.
Description
Technical field
The invention belongs to car transmissions NVH technical field of measurement and test, and in particular to passed being tested based on influence coefficient method
Dynamic is the method for multiaspect residue unbalance dynamic.
Background technology
Consumer and automaker to 4 wheel driven and after the drive noise and vibration problem of transmission system generation increasingly pay close attention to.
Wherein, the power train parts such as including speed changer, power transmission shaft, drive axle, be 4 wheel driven and after the crucial power-transmission system driven,
Low-frequency noise and vibration problem that its unbalance dynamic is produced increasingly obtain the attention of consumer.
There is different size of remaining unbalancing value in the rotary shaft of speed changer, power transmission shaft and drive axle.Ordinary circumstance
Under, only power transmission shaft does unbalance dynamic test and corrects in the fabrication process.The residue of power transmission shaft, drive axle and speed changer is dynamic not
Balance phase can be overlapped mutually in vehicle assembling process so that the unbalance dynamic of power train may be larger and produces noise and vibration
Problem.Therefore, the unbalancing value of test whole vehicle state underdrive system has non-to the remaining unbalancing value for controlling transmission system
Often important meaning.
The power train residue unbalancing value of prior art is that power transmission shaft is placed on unbalance dynamic machine or stand to carry out
Dynamic balancing, not yet there is a kind of effective ways that the residue unbalance dynamic of power train multiaspect is tested under whole vehicle state.
The content of the invention
The invention discloses whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing so that the residue of power train
Unbalancing value can be with objective quantification, to solve the problems, such as that the uneven noise and vibration for producing of transmission system provides direction.
Whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing disclosed by the invention, comprises the following steps：
The first step, placement sensor：
Speed probe is being disposed about near power transmission shaft, the rotating speed for detecting power transmission shaft；
Respectively near power takeoff output shaft, intermediate supports, the bearing hole of drive axle input shaft, along vehicle Z-direction or Y-direction
The first unidirectional acceleration transducer, the second unidirectional acceleration transducer and the 3rd unidirectional acceleration transducer are arranged, for detecting
Vibratory response；
Second step, chooses test speed：
Under certain accelerator pedal stroke, vehicle is at the uniform velocity accelerated, measure the first unidirectional acceleration transducer, second unidirectional
The vibratory response of acceleration transducer and the 3rd unidirectional acceleration transducer, test is repeatedly averaged；Choose vibration amplitude and phase
The speed of position stabilization is follow-up test speed；
3rd step, tests transmission system original state vibratory response：
Make vehicle in selected vehicle speed cruise, the first unidirectional acceleration transducer of test, the second unidirectional acceleration transducer
With the vibratory response of the 3rd unidirectional acceleration transducerWithTest is repeatedly averaged；
4th step, test transmission system increases the vibratory response after test mass, and calculating influence coefficientIt is as follows：
4a) only add test mass in speed changer unbalance dynamic faceMake vehicle in selected vehicle speed cruise, obtain speed changer and move
The unbalancing value of plane of unbalance is to the influence coefficient of first, second and third unidirectional acceleration transducer vibratory response, the shadow
Sound coefficient is the difference for adding the vibratory response after test mass and the vibratory response of original state divided by test mass；
4b) only add test mass in intermediate supports unbalance dynamic faceMake vehicle in selected vehicle speed cruise, obtain middle branch
The unbalancing value of racking plane of unbalance to the influence coefficient of first, second and third unidirectional acceleration transducer vibratory response,
The influence coefficient is the difference for adding the vibratory response after test mass and the vibratory response of original state divided by test mass；
4c) only add test mass in drive axle unbalance dynamic face (11)Make vehicle in selected vehicle speed cruise, obtain and drive
Influence system of the unbalancing value in dynamic bridge unbalance dynamic face to first, second and third unidirectional acceleration transducer vibratory response
Number, the influence coefficient is the difference for adding the vibratory response after test mass and the vibratory response of original state divided by test mass；
5th step, calculates the remaining unbalancing value of drive shaft system：
The transmission system original state vibratory response obtained by the 3rd stepWithThe influence coefficient that 4th step is obtainedThe remaining unbalancing value of power train is calculated according to influence coefficient method.
Further,
Step 4a) in the unbalancing value in speed changer unbalance dynamic face (9) first, second and third unidirectional acceleration is passed
The influence coefficient of sensor vibratory responseWithRespectively：
Step 4b) in the unbalancing value in intermediate supports unbalance dynamic face (10) unidirectional to first, second and third accelerate
The influence coefficient of degree sensor vibration responseWithRespectively：
Step 4c) in drive axle unbalance dynamic face (11) unbalancing value to first, second and third unidirectional acceleration
The influence coefficient of sensor vibration responseWithRespectively：
Further, the 5th step, calculates the remaining unbalancing value of drive shaft system：
The transmission system original state vibratory response obtained by the 3rd stepWithThe influence coefficient that 4th step is obtainedThe remaining unbalancing value of power train is calculated according to below equation：
Further, in the second step, accelerator pedal stroke is 30%-40%, and vehicle is accelerated to by 70km/h is even
140km/h。
Advantageous Effects of the present invention are：
By speed changer, three separable assembleds of intermediate supports and drive axle into transmission system totality, and in speed changer, middle branch
Unbalance dynamic face is set in support and drive axle, by arranging unidirectional acceleration sensor on each unbalance dynamic face, is existed in batches
Test mass is added in a certain unbalance dynamic face, and calculates one group influence coefficient of two other split on the split unbalance dynamic face, from
And transmission system general impacts coefficient matrix is constructed, and the remaining unbalance dynamic of transmission system is calculated by influence coefficient method
Amount.The method that this patent is provided can test out the remaining unbalancing value and phase of power train under whole vehicle state, breach
The limitation of aptitude test only on stand or on unbalance dynamic machine.
Brief description of the drawings
Fig. 1 is the unidirectional acceleration sensor arrangement schematic diagram of this power train；
Fig. 2 is that this power train adds test mass in speed changer unbalance dynamic face；
Fig. 3 is that this power train adds test mass in intermediate supports unbalance dynamic face；
Fig. 4 is that this power train adds test mass in drive axle unbalance dynamic face；
Wherein, the unidirectional acceleration transducers of 1- first, the unidirectional acceleration transducers of 2- second, the unidirectional acceleration of 3- the 3rd is passed
Sensor, 4- speed probes, 5- power takeoffs, 6- power transmission shafts, 7- intermediate supports, 8- drive axles, 9- speed changers unbalance dynamic face,
10- intermediate supports unbalance dynamic face, 11- drive axles unbalance dynamic face, 12- test mass.
Specific embodiment
In order to test obtains the remaining unbalancing value of power train, the transmission with power transmission shaft as two-part under whole vehicle state
As a example by system, illustrate：
Test condition：Test request is carried out in two drives or 4 wheel driven rotating hub, or smooth pitch and straight road surface.Do on road surface
It is dry without ponding, road surface is without debris such as accumulated snow, dust, sandstone and other fragments being scattered.Wind speed is not more than 5m/s.Vehicle shape
State is intact.
The first step, placement sensor：
As shown in Figure 1；
Photoelectric sensor 4 is being arranged within 1cm near power transmission shaft 6；
Respectively within 1cm near the output shaft of power takeoff 5, intermediate supports 7, the bearing hole of the input shaft of drive axle 8, along whole
Car Z-direction or Y-direction arrange the first unidirectional acceleration transducer 1, the second unidirectional acceleration transducer 2 and the 3rd unidirectional acceleration sensing
Device 3, for detecting vibratory response；
Second step, chooses test speed：
Under 30%-40% accelerator pedal strokes, vehicle is accelerated into 140km/h by 70km/h is even, measure first unidirectional
The vibratory response of acceleration transducer 1, the second unidirectional acceleration transducer 2 and the 3rd unidirectional acceleration transducer 3, test is multiple
It is averaged；The speed for choosing vibration amplitude and phase stabilization is follow-up test speed；
3rd step, tests transmission system original state vibratory response：
Make vehicle in selected vehicle speed cruise, the first unidirectional acceleration transducer 1 of test, the second unidirectional acceleration transducer
2 and the 3rd unidirectional acceleration transducer 3 vibratory responseWithTest is repeatedly averaged；
4th step, test transmission system increases the vibratory response after test mass, and calculating influence coefficientIt is as follows：
4a) as shown in Fig. 2 only adding test mass 12 in speed changer unbalance dynamic face 9, its size isMake vehicle selected
Vehicle speed cruise, obtain speed changer unbalance dynamic face (9) unbalancing value to first, second and third unidirectional acceleration sensing
The influence coefficient of the vibratory response of device 1,2 and 3WithRespectively：
4b) as shown in figure 3, only adding test mass in intermediate supports unbalance dynamic face 10Vehicle is set to be patrolled in selected speed
Boat, obtain the unbalancing value in intermediate supports unbalance dynamic face 10 to first, second and third unidirectional acceleration transducer 1,2 and
The influence coefficient of 3 vibratory responsesWithRespectively：
4c) as shown in figure 4, only adding test mass in drive axle unbalance dynamic face 11Make vehicle in selected vehicle speed cruise,
The unbalancing value for obtaining drive axle unbalance dynamic face 11 vibrates to first, second and third unidirectional acceleration transducer 1,2 and 3
The influence coefficient of responseWithRespectively：
5th step, calculates the remaining unbalancing value of drive shaft system：
The transmission system original state vibratory response obtained by the 3rd stepWithThe influence coefficient that 4th step is obtainedThe remaining unbalancing value of power train is calculated according to influence coefficient method：
Table one is test record data of the first step to the 4th step：
Table 1
Table two is the transmission system residue unbalance dynamic size and phase being calculated according to the 5th step：
| Size (gcm) | Phase (deg) | |
| Speed changer unbalance dynamic face | 24.5 | 312 |
| Intermediate supports unbalance dynamic face | 29.0 | 178 |
| Drive axle unbalance dynamic face | 15.8 | 101 |
Table 2.
Claims (5)
1. whole vehicle state underdrive system multiaspect residue unbalance dynamic method of testing, it is characterised in that comprise the following steps：
The first step, placement sensor：
Speed probe (4) is being disposed about near power transmission shaft (6), the rotating speed for detecting power transmission shaft；
Respectively near power takeoff (5) output shaft, intermediate supports (7), the bearing hole of drive axle (8) input shaft, along vehicle Z-direction
Or Y-direction arranges the first unidirectional acceleration transducer (1), the second unidirectional acceleration transducer (2) and the 3rd unidirectional acceleration sensing
Device (3), for detecting vibratory response；
Second step, chooses test speed：
Under certain accelerator pedal stroke, vehicle is at the uniform velocity accelerated, measure the first unidirectional acceleration transducer (1), second unidirectional
Acceleration transducer (2) and the vibratory response of the 3rd unidirectional acceleration transducer (3), test are repeatedly averaged；Choose vibration width
The speed of value and phase stabilization is follow-up test speed；
3rd step, tests transmission system original state vibratory response：
Make vehicle in selected vehicle speed cruise, the first unidirectional acceleration transducer (1) of test, the second unidirectional acceleration transducer
(2) and the 3rd unidirectional acceleration transducer (3) vibratory responseWithTest is repeatedly averaged；
4th step, test transmission system increases the vibratory response after test mass, and calculating influence coefficientIt is as follows：
4a) only add test mass in speed changer unbalance dynamic face (9)Make vehicle in selected vehicle speed cruise, obtain speed changer and move
Influence of the unbalancing value of plane of unbalance (9) to first, second and third unidirectional acceleration transducer (1,2,3) vibratory response
Coefficient, the influence coefficient is the difference for adding the vibratory response after test mass and the vibratory response of original state divided by test mass；
4b) only add test mass in intermediate supports unbalance dynamic face (10)Make vehicle in selected vehicle speed cruise, obtain middle branch
The unbalancing value of racking plane of unbalance (10) is to first, second and third unidirectional acceleration transducer (1,2,3) vibratory response
Influence coefficient, the influence coefficient is the difference of the vibratory response for adding vibratory response and original state after test mass divided by examination
Weight；
4c) only add test mass in drive axle unbalance dynamic face (11)Make vehicle in selected vehicle speed cruise, obtain drive axle and move
Shadow of the unbalancing value of plane of unbalance (11) to first, second and third unidirectional acceleration transducer (1,2,3) vibratory response
Coefficient is rung, the influence coefficient is the difference for adding the vibratory response after test mass and the vibratory response of original state divided by test mass；
5th step, calculates the remaining unbalancing value of drive shaft system：
The transmission system original state vibratory response obtained by the 3rd stepWithThe influence coefficient that 4th step is obtainedRoot
The remaining unbalancing value of power train is calculated according to influence coefficient method.
2. whole vehicle state underdrive system multiaspect as claimed in claim 1 residue unbalance dynamic method of testing, it is characterised in that：
Step 4a) in speed changer unbalance dynamic face (9) unbalancing value to first, second and third unidirectional acceleration transducer
(1,2,3) the influence coefficient of vibratory responseWithRespectively：
Step 4b) in the unbalancing value in intermediate supports unbalance dynamic face (10) first, second and third unidirectional acceleration is passed
The influence coefficient of sensor (1,2,3) vibratory responseWithRespectively：
Step 4c) in drive axle unbalance dynamic face (11) unbalancing value to first, second and third unidirectional acceleration sensing
The influence coefficient of device (1,2,3) vibratory responseWithRespectively：
3. whole vehicle state underdrive system multiaspect as claimed in claim 1 or 2 residue unbalance dynamic method of testing, its feature exists
In：
5th step, calculates the remaining unbalancing value of drive shaft system：
The transmission system original state vibratory response obtained by the 3rd stepWithThe influence coefficient that 4th step is obtainedRoot
The remaining unbalancing value of power train is calculated according to below equation：
4. whole vehicle state underdrive system multiaspect as claimed in claim 3 residue unbalance dynamic method of testing, it is characterised in that：Institute
State in second step, accelerator pedal stroke is 30%-40%, vehicle is accelerated into 140km/h by 70km/h is even.
5. whole vehicle state underdrive system multiaspect as claimed in claim 1 or 2 residue unbalance dynamic method of testing, its feature exists
In：In the second step, accelerator pedal stroke is 30%-40%, and vehicle is accelerated into 140km/h by 70km/h is even.
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Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107918702A (en) * | 2017-11-10 | 2018-04-17 | 上海纳铁福传动系统有限公司 | The appraisal procedure of transmission shaft initial unbalance, |
| CN108760029A (en) * | 2018-03-16 | 2018-11-06 | 江铃汽车股份有限公司 | Interior noise sensitivity test method caused by transmission system imbalance |
| CN112683529A (en) * | 2020-12-04 | 2021-04-20 | 东风汽车股份有限公司 | Automobile transmission shaft bending endurance test device and method thereof |
| CN113432815A (en) * | 2021-01-26 | 2021-09-24 | 重庆大学 | Bridge deck response reconstruction method based on vibration response of measuring vehicle |
| CN114429000A (en) * | 2022-04-06 | 2022-05-03 | 江铃汽车股份有限公司 | Method, system and equipment for predicting dynamic unbalance finished automobile response of transmission system |
| CN114813116A (en) * | 2022-04-07 | 2022-07-29 | 中国第一汽车股份有限公司 | Dynamic balance sensitivity test analysis method for passenger car transmission system |
| CN117782432A (en) * | 2024-02-23 | 2024-03-29 | 润华汽车控股有限公司 | Dynamic balance comprehensive test system for automobile front axle assembly |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000088689A (en) * | 1998-09-09 | 2000-03-31 | Akashi Corp | Balancing machine and placement method for object, to be tested, in balancing machine |
| JP4014822B2 (en) * | 2001-05-22 | 2007-11-28 | 国際計測器株式会社 | Tire uniformity and dynamic balance test equipment |
| CN101464202A (en) * | 2009-01-05 | 2009-06-24 | 东南大学 | Dynamic balancing method for dual-rotor rotating machine with little speed difference |
| CN103728133A (en) * | 2014-01-24 | 2014-04-16 | 武汉理工大学 | Method for testing automotive transmission system resistance distribution |
| CN106124126A (en) * | 2016-07-07 | 2016-11-16 | 重庆长安汽车股份有限公司 | The method for testing and analyzing that the unbalance dynamic of whole vehicle state underdrive system separates |
-
2017
- 2017-04-26 CN CN201710284053.4A patent/CN106872105A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP2000088689A (en) * | 1998-09-09 | 2000-03-31 | Akashi Corp | Balancing machine and placement method for object, to be tested, in balancing machine |
| JP4014822B2 (en) * | 2001-05-22 | 2007-11-28 | 国際計測器株式会社 | Tire uniformity and dynamic balance test equipment |
| CN101464202A (en) * | 2009-01-05 | 2009-06-24 | 东南大学 | Dynamic balancing method for dual-rotor rotating machine with little speed difference |
| CN103728133A (en) * | 2014-01-24 | 2014-04-16 | 武汉理工大学 | Method for testing automotive transmission system resistance distribution |
| CN106124126A (en) * | 2016-07-07 | 2016-11-16 | 重庆长安汽车股份有限公司 | The method for testing and analyzing that the unbalance dynamic of whole vehicle state underdrive system separates |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107918702A (en) * | 2017-11-10 | 2018-04-17 | 上海纳铁福传动系统有限公司 | The appraisal procedure of transmission shaft initial unbalance, |
| CN107918702B (en) * | 2017-11-10 | 2021-04-06 | 上海纳铁福传动系统有限公司 | Method for evaluating initial unbalance amount of transmission shaft |
| CN108760029A (en) * | 2018-03-16 | 2018-11-06 | 江铃汽车股份有限公司 | Interior noise sensitivity test method caused by transmission system imbalance |
| CN112683529A (en) * | 2020-12-04 | 2021-04-20 | 东风汽车股份有限公司 | Automobile transmission shaft bending endurance test device and method thereof |
| CN112683529B (en) * | 2020-12-04 | 2023-03-31 | 东风汽车股份有限公司 | Automobile transmission shaft bending endurance test device and method thereof |
| CN113432815A (en) * | 2021-01-26 | 2021-09-24 | 重庆大学 | Bridge deck response reconstruction method based on vibration response of measuring vehicle |
| CN113432815B (en) * | 2021-01-26 | 2022-08-05 | 重庆大学 | Bridge deck response reconstruction method based on vibration response of measuring vehicle |
| CN114429000A (en) * | 2022-04-06 | 2022-05-03 | 江铃汽车股份有限公司 | Method, system and equipment for predicting dynamic unbalance finished automobile response of transmission system |
| CN114813116A (en) * | 2022-04-07 | 2022-07-29 | 中国第一汽车股份有限公司 | Dynamic balance sensitivity test analysis method for passenger car transmission system |
| CN114813116B (en) * | 2022-04-07 | 2024-06-11 | 中国第一汽车股份有限公司 | Dynamic balance sensitivity test analysis method for passenger car transmission system |
| CN117782432A (en) * | 2024-02-23 | 2024-03-29 | 润华汽车控股有限公司 | Dynamic balance comprehensive test system for automobile front axle assembly |
| CN117782432B (en) * | 2024-02-23 | 2024-05-24 | 润华汽车控股有限公司 | Dynamic balance comprehensive test system for automobile front axle assembly |
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