CN103033358B - Automobile transmission shaft fatigue test method - Google Patents

Automobile transmission shaft fatigue test method Download PDF

Info

Publication number
CN103033358B
CN103033358B CN201210537897.2A CN201210537897A CN103033358B CN 103033358 B CN103033358 B CN 103033358B CN 201210537897 A CN201210537897 A CN 201210537897A CN 103033358 B CN103033358 B CN 103033358B
Authority
CN
China
Prior art keywords
hydraulic servo
servo actuator
signal
transmission shaft
response
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.)
Expired - Fee Related
Application number
CN201210537897.2A
Other languages
Chinese (zh)
Other versions
CN103033358A (en
Inventor
袁冬梅
邹喜红
征小梅
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chongqing University of Technology
Original Assignee
Chongqing University of Technology
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Chongqing University of Technology filed Critical Chongqing University of Technology
Priority to CN201210537897.2A priority Critical patent/CN103033358B/en
Publication of CN103033358A publication Critical patent/CN103033358A/en
Application granted granted Critical
Publication of CN103033358B publication Critical patent/CN103033358B/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Abstract

The invention discloses an automobile transmission shaft fatigue test method. The automobile transmission shaft fatigue test method comprises the following steps: (1) collecting input torque of a transmission shaft and vibration acceleration of an output end on a testing ground to obtain an expected response signal; (2) installing the transmission shaft and calculating a frequency response function of a test system; (3) calculating initial driving signals of a straight line hydraulic servo actuator and a torsion hydraulic servo actuator; (4) calculating a weighted error of a time-domain response and a frequency-domain response, calculating a drive signal correction which corresponds to the weighted error, conducting imitation iteration, and recording a final drive signal when response weighted errors of all sensors are less than or equal to 5%; (5) carrying out a transmission shaft fatigue test based on input of the final drive signal. A weighted multiple parameter control method of time-domain errors and frequency-domain errors is applied. Movement condition and stress distribution condition, when a real car is driven, of the transmission shaft of an automobile are imitated. Fatigue life of the transmission shaft of the automobile is examined accurately and efficiently.

Description

A kind of truck drive shaft fatigue test method
Technical field
The present invention relates to a kind of truck drive shaft method for testing performance, relate in particular to a kind of truck drive shaft fatigue test method.
Background technology
Truck drive shaft is being undertaken the effect of transmission variator (or transfer gear) to main reducing gear moment of torsion, on vehicle performance impact greatly, particularly automobile is in the time of starting, acceleration and braking, and transmission shaft will bear very high pulling torque, is one of crucial assembly in automotive transmission.Truck drive shaft generally hollow carbon steel pipes antitorque by height, bending resistance is made, and the two ends of central siphon are welded with universal joint, because extruding and the technique such as welding are difficult to control, therefore must verify by testing the rigidity of truck drive shaft, intensity and fatigue lifetime.Existing truck drive shaft fatigue test method is normally determined torque and is determined rotating speed and carry out on transmission test bench, or the amplitude torsional fatigue test such as carry out, when but transmission shaft moves on real vehicle, not only bear the torque of dynamic change, and transmission shaft two ends upper-lower position is in continuous variation, therefore, existing test unit and test method are difficult to the accurately practical operation situation of simulation transmission shaft.
Summary of the invention
For above shortcomings in prior art, the invention provides a kind of truck drive shaft fatigue test method.This test method goes out motion and the stressing conditions of truck drive shaft in the time that real vehicle travels at lab simulation, automobile rotation axis is carried out to the examination of precise and high efficiency fatigue lifetime.
In order to solve the problems of the technologies described above, the present invention has adopted following technical scheme:
A kind of truck drive shaft fatigue test method, adopted in the method a kind of truck drive shaft fatigue test system, this pilot system comprises straight line hydraulic servo actuator, hold-down support, acceleration transducer, torsion hydraulic servo actuator, torque sensor and computer control system; Described straight line hydraulic servo actuator vertically arranges, and a brace table is set on the piston rod of straight line hydraulic servo actuator, and brace table is provided with a support slide unit for this brace table horizontal slip relatively; Described hold-down support is vertically fixed on and supports on slide unit, and described acceleration transducer is arranged on hold-down support; Described torque sensor is connected with torsion hydraulic servo actuator, and described straight line hydraulic servo actuator and torsion hydraulic servo actuator are by computer control system control, and the signal that acceleration transducer and torque sensor gather is inputted computer control system;
The method comprises the steps:
(1), strain-type torque sensor is installed on transmission output shaft, in the mounting disc of main reducing gear input end, acceleration transducer is installed, gather the vibration acceleration of transmission shaft input torque and output terminal at testing field, obtaining Expected Response signal is y d(t), be 1 × 2 matrix;
(2), transmission shaft is arranged on truck drive shaft fatigue test system, one end of transmission shaft is connected on hold-down support by universal joint, the other end of transmission shaft is connected with torsion hydraulic servo actuator with shaft coupling by universal joint; By computer control system, straight line hydraulic servo actuator and torsion hydraulic servo actuator are applied to sine sweep signal x n(t), collect the response signal y of acceleration transducer and torque sensor r(t), calculate the frequency response function H (f) of this pilot system by formula (1);
H ( f ) = S xy ( f ) S xx ( f ) - - - ( 1 )
In formula: S xx(f)-sine sweep signal x n(t) autopower spectral density;
S xy(f)-sine sweep signal x n(t) with sensor response signal y r(t) cross-spectral density between;
Frequency response function between H (f)-acceleration transducer and torque sensor and straight line hydraulic servo actuator and torsion hydraulic servo actuator is 2 × 2 matrixes;
(3), to expect response signal y d(t) be simulated target, the initial driving signal according to formula (2) and (3) calculated line hydraulic servo actuator and torsion hydraulic servo actuator:
X 0(f)=H -1(f)Y d(f)????(2)
x 0(t)=IFFT[X 0(f)]????(3)
In formula: H -1(f) inverse matrix of-H (f);
Y d(f)-Expected Response signal y d(t) Fourier transform;
X 0(t)-straight line hydraulic servo actuator and torsion hydraulic servo actuator initially drive signal;
X 0(f)-x 0(t) Fourier transform;
(4), with initial drive straight line hydraulic servo actuator with reverse hydraulic servo actuator, gather the response signal y of acceleration transducer and torque sensor simultaneously 0(t), calculate time domain response and frequency domain response weighted error with formula (4), (5), (6) and (7), use driving signal correction amount corresponding to formula (8) and (9) error of calculation:
Δ t(t)=y d(t)-y 0(t)????(4)
Δ f(f)=Y d(f)-Y 0(f)????(5)
Δ(t)=0.7×Δ t(t)+0.3×Δ f(t)????(7)
X e(f)=H -1(f)Δ(f)????(8)
x e(t)=IFFT[X e(f)]????(9)
In formula: Δ t(t)-time domain response error signal;
Y 0(f)-sensor response signal y 0(t) Fourier transform;
Δ f(f)-frequency domain response error signal;
Δ f(t)-frequency domain response error signal Δ f(f) inverse Fourier transform;
Δ (t)-time domain response and frequency domain response weighted error;
The Fourier transform of Δ (f)-Δ (t);
X e(t) the corresponding signal that drives of-error;
X e(f)-x e(t) Fourier transform;
Revising and driving signal is x 1(t)=x 0(t)+α x e(t);
In formula, α is attenuation coefficient, and initial value gets 0.5 conventionally, suitably increases or reduces, but must meet: 0 < α≤1 according to iteration convergence situation;
Drive signal x to revise 1(t), as driving, the process above that constantly repeats in this step is carried out iteration, and with formula (10) error of calculation value Δ in real time n, in the time of each sensor response error≤5%, the final signal that drives of record;
&Delta; n = ( 0.7 &times; &Sigma; t ( y d ( t ) - y n ( t ) ) 2 &Sigma; t y d 2 ( t ) + 0.3 &times; &Sigma; f ( Y d ( f ) - Y n ( f ) ) 2 &Sigma; f Y d 2 ( f ) ) &times; 100 % - - - ( 10 )
In formula: Δ n-the n time iteration error value;
Y n(t) response signal of-the n time iteration collection;
Y n(f)-y n(t) Fourier transform;
(5), finally to drive signal to carry out transmission shaft torture test as inputting.
Compared with prior art, a kind of truck drive shaft fatigue test method tool of the present invention has the following advantages:
1, the present invention in conjunction with truck drive shaft the stressed and motion conditions on real vehicle, load by reversing hydraulic servo actuator and straight line hydraulic servo actuator, by multi parameters control method, precise and high efficiency cause that at the indoor dynamic torque that has reproduced truck drive shaft and suspension displacement variator and the upper and lower relative position of drive axle change and vibration, for truck drive shaft torture test provides a set of new method.
2, use straight line hydraulic servo actuator to apply transmission shaft bob dynamic loading, use torsion hydraulic servo actuator to apply the input torque of transmission shaft, well reflected the load initial conditions of transmission shaft on real vehicle.
3, the multi parameters control method of application time domain error and error of frequency domain weighting, goes out motion and the stressing conditions of truck drive shaft in the time that real vehicle travels at lab simulation, automobile rotation axis is carried out to the examination of precise and high efficiency fatigue lifetime.
Brief description of the drawings
Fig. 1 is the front view of truck drive shaft fatigue test system.
In accompanying drawing: 1-mounting foundation; 2-straight line hydraulic servo actuator; 3-support slide unit; 4-hold-down support; 5-acceleration transducer; 6-transmission shaft; 7-shaft coupling; 8-bearing seat; 9-torque sensor; 10-torsion hydraulic servo actuator; 11-support platform; 12-support platform column; 13-brace table.
Embodiment
Below in conjunction with the drawings and specific embodiments, the invention will be further described.
A kind of truck drive shaft fatigue test method, has adopted a kind of truck drive shaft fatigue test system in the method.As shown in Figure 1, this truck drive shaft fatigue test system comprises mounting foundation 1, straight line hydraulic servo actuator 2, hold-down support 4, acceleration transducer 5, shaft coupling 7, bearing seat 8, torque sensor 9, reverses hydraulic servo actuator 10, support platform 11, support platform column 12 and computer control system.Straight line hydraulic servo actuator 2 is vertically arranged in mounting foundation 1, and straight line hydraulic servo actuator 2 is used for simulating transmission shaft bob.One brace table 13 is set on the piston rod of straight line hydraulic servo actuator 2, brace table 13 is provided with a support slide unit 3 for these brace table 13 horizontal slips relatively, this support slide unit 3 is used for supporting hold-down support 4, simultaneously brace table 13 along continuous straight runs slips relatively, the variation of distance when compensating transmission shaft two ends bob.Hold-down support 4 is vertically fixed on and supports on slide unit 3, and acceleration transducer 5 is arranged on hold-down support 4.Support platform 11 is horizontally set in mounting foundation 1 by three support platform columns 12, bearing seat 8, torque sensor 9 and torsion hydraulic servo actuator 10 are arranged in support platform 11, the power output shaft of reversing hydraulic servo actuator 10 is supported on bearing seat 8, torque sensor 9 is arranged in the power output shaft of reversing hydraulic servo actuator 10, and the end of reversing the power output shaft of hydraulic servo actuator 10 connects shaft coupling 7.Acceleration transducer 5 and torque sensor 9 are used for measuring and the simulation moment of torsion of transmission shaft and the up-down vibration at two ends.Straight line hydraulic servo actuator 2 and torsion hydraulic servo actuator 10 are by computer control system control, and the signal that acceleration transducer 5 and torque sensor 9 gather is inputted computer control system.
The ultimate principle of this truck drive shaft fatigue test system is: with straight line hydraulic servo actuator 2 with reverse hydraulic servo actuator 10 and apply respectively sine sweep signal, gathering acceleration transducer 5 and torque sensor 9 exports, calculate the frequency response function of this pilot system, the transmission shaft two ends bob and the transmission shaft torque that while travelling according to real vehicle, gather, the input signal of calculated line hydraulic servo actuator 2 and torsion hydraulic servo actuator 10, and constantly carry out iteration, the transmission shaft two ends bob and the transmission shaft torque that when simulating real vehicle travel on acceleration transducer 5 and torque sensor 9, gather, motion and the stressing conditions of transmission shaft are well reappeared on this device, under real load condition, carry out torture test.
This one truck drive shaft fatigue test method comprises the steps:
(1), strain-type torque sensor is installed on transmission output shaft, in the mounting disc of main reducing gear input end, acceleration transducer is installed, gather the vibration acceleration of transmission shaft input torque and output terminal at testing field, obtaining Expected Response signal is y d(t), be 1 × 2 matrix.
(2), transmission shaft 6 is arranged on truck drive shaft fatigue test system, one end of transmission shaft 6 is connected on hold-down support 4 by universal joint, the other end of transmission shaft 6 is connected with shaft coupling 7 by universal joint.By computer control system, straight line hydraulic servo actuator 2 and torsion hydraulic servo actuator 10 are applied to sine sweep signal x n(t), collect the response signal y of acceleration transducer and torque sensor r(t), calculate the frequency response function H (f) of this pilot system by formula (1);
H ( f ) = S xy ( f ) S xx ( f ) - - - ( 1 )
In formula: S xx(f)-sine sweep signal x n(t) autopower spectral density;
S xy(f)-sine sweep signal x n(t) with sensor response signal y r(t) cross-spectral density between;
Frequency response function between H (f)-acceleration transducer and torque sensor and straight line hydraulic servo actuator and torsion hydraulic servo actuator is 2 × 2 matrixes.
(3), to expect response signal y d(t) be simulated target, the initial driving signal according to formula (2) and (3) calculated line hydraulic servo actuator and torsion hydraulic servo actuator:
X 0(f)=H -1(f)Y d(f)????(2)
x 0(t)=IFFT[X 0(f)]????(3)
In formula: H -1(f) inverse matrix of-H (f);
Y d(f)-Expected Response signal y d(t) Fourier transform;
X 0(t)-straight line hydraulic servo actuator and torsion hydraulic servo actuator initially drive signal;
X 0(f)-x 0(t) Fourier transform.
(4), with initial drive straight line hydraulic servo actuator with reverse hydraulic servo actuator, gather the response signal y of acceleration transducer and torque sensor simultaneously 0(t), calculate time domain response and frequency domain response weighted error with formula (4), (5), (6) and (7), use driving signal correction amount corresponding to formula (8) and (9) error of calculation:
Δ t(t)=y d(t)-y 0(t)????(4)
Δ f(f)=Y d(f)-Y 0(f)????(5)
Δ(t)=0.7×Δ t(t)+0.3×Δ f(t)????(7)
X e(f)=H -1(f)Δ(f)????(8)
x e(t)=IFFT[X e(f)]????(9)
In formula: Δ t(t)-time domain response error signal;
Y 0(f)-sensor response signal y 0(t) Fourier transform;
Δ f(f)-frequency domain response error signal;
Δ f(t)-frequency domain response error signal Δ f(f) inverse Fourier transform;
Δ (t)-time domain response and frequency domain response weighted error;
The Fourier transform of Δ (f)-Δ (t);
X e(t) the corresponding signal that drives of-error;
X e(f)-x e(t) Fourier transform;
Revising and driving signal is x 1(t)=x 0(t)+α x e(t);
In formula, α is attenuation coefficient, and initial value gets 0.5 conventionally, suitably increases or reduces, but must meet: 0 < α≤1 according to iteration convergence situation;
Drive signal x to revise 1(t), as driving, the process above that constantly repeats in this step is carried out iteration, and with formula (10) error of calculation value Δ in real time n, in the time of each sensor response error≤5%, the final signal that drives of record;
&Delta; n = ( 0.7 &times; &Sigma; t ( y d ( t ) - y n ( t ) ) 2 &Sigma; t y d 2 ( t ) + 0.3 &times; &Sigma; f ( Y d ( f ) - Y n ( f ) ) 2 &Sigma; f Y d 2 ( f ) ) &times; 100 % - - - ( 10 )
In formula: Δ n-the n time iteration error value;
Y n(t) response signal of-the n time iteration collection;
Y n(f)-y n(t) Fourier transform.
(5), finally to drive signal to carry out transmission shaft torture test as inputting.
Finally explanation is, above embodiment is only unrestricted in order to technical scheme of the present invention to be described, although the present invention is had been described in detail with reference to preferred embodiment, those of ordinary skill in the art is to be understood that, can modify or be equal to replacement technical scheme of the present invention, and not departing from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of claim scope of the present invention.

Claims (1)

1. a truck drive shaft fatigue test method, it is characterized in that, adopted in the method a kind of truck drive shaft fatigue test system, this pilot system comprises straight line hydraulic servo actuator, hold-down support, acceleration transducer, torsion hydraulic servo actuator, torque sensor and computer control system; Described straight line hydraulic servo actuator vertically arranges, and a brace table is set on the piston rod of straight line hydraulic servo actuator, and brace table is provided with a support slide unit for this brace table horizontal slip relatively; Described hold-down support is vertically fixed on and supports on slide unit, and described acceleration transducer is arranged on hold-down support; Described torque sensor is connected with torsion hydraulic servo actuator, and described straight line hydraulic servo actuator and torsion hydraulic servo actuator are by computer control system control, and the signal that acceleration transducer and torque sensor gather is inputted computer control system;
The method comprises the steps:
(1), strain-type torque sensor is installed on transmission output shaft, in the mounting disc of main reducing gear input end, acceleration transducer is installed, gather the vibration acceleration of transmission shaft input torque and output terminal at testing field, obtaining Expected Response signal is y d(t), be 1 × 2 matrix;
(2), transmission shaft is arranged on truck drive shaft fatigue test system, one end of transmission shaft is connected on hold-down support by universal joint, the other end of transmission shaft is connected with torsion hydraulic servo actuator with shaft coupling by universal joint; By computer control system, straight line hydraulic servo actuator and torsion hydraulic servo actuator are applied to sine sweep signal x n(t), collect the response signal y of acceleration transducer and torque sensor r(t), calculate the frequency response function H (f) of this pilot system by formula (1);
H ( f ) = S xy ( f ) S xx ( f ) - - - ( 1 )
In formula: S xx(f)-sine sweep signal x n(t) autopower spectral density;
S xy(f)-sine sweep signal x n(t) with sensor response signal y r(t) cross-spectral density between;
Frequency response function between H (f)-acceleration transducer and torque sensor and straight line hydraulic servo actuator and torsion hydraulic servo actuator is 2 × 2 matrixes;
(3), to expect response signal y d(t) be simulated target, the initial driving signal according to formula (2) and (3) calculated line hydraulic servo actuator and torsion hydraulic servo actuator:
X 0(f)=H -1(f)Y d(f)????(2)
x 0(t)=IFFT[X 0(f)]????(3)
In formula: H -1(f) inverse matrix of-H (f);
Y d(f)-Expected Response signal y d(t) Fourier transform;
X 0(t)-straight line hydraulic servo actuator and torsion hydraulic servo actuator initially drive signal;
X 0(f)-x 0(t) Fourier transform;
(4), with initial drive straight line hydraulic servo actuator with reverse hydraulic servo actuator, gather the response signal y of acceleration transducer and torque sensor simultaneously 0(t), calculate time domain response and frequency domain response weighted error with formula (4), (5), (6) and (7), use driving signal correction amount corresponding to formula (8) and (9) error of calculation:
Δ t(t)=y d(t)-y 0(t)????(4)
Δ f(f)=Y d(f)-Y 0(f)????(5)
Δ(t)=0.7×Δ t(t)+0.3×Δ f(t)????(7)
X e(f)=H -1(f)Δ(f)????(8)
x e(t)=IFFT[X e(f)]????(9)
In formula: Δ t(t)-time domain response error signal;
Y 0(f)-sensor response signal y 0(t) Fourier transform;
Δ f(f)-frequency domain response error signal;
Δ f(t)-frequency domain response error signal Δ f(f) inverse Fourier transform;
Δ (t)-time domain response and frequency domain response weighted error;
The Fourier transform of Δ (f)-Δ (t);
X e(t) the corresponding signal that drives of-error;
X e(f)-x e(t) Fourier transform;
Revising and driving signal is x 1(t)=x 0(t)+α x e(t);
In formula, α is attenuation coefficient, and initial value gets 0.5 conventionally, suitably increases or reduces, but must meet: 0 < α≤1 according to iteration convergence situation;
Drive signal x to revise 1(t), as driving, the process above that constantly repeats in this step is carried out iteration, and with formula (10) error of calculation value Δ in real time n, in the time of each sensor response error≤5%, the final signal that drives of record;
&Delta; n = ( 0.7 &times; &Sigma; t ( y d ( t ) - y n ( t ) ) 2 &Sigma; t y d 2 ( t ) + 0.3 &times; &Sigma; f ( Y d ( f ) - Y n ( f ) ) 2 &Sigma; f Y d 2 ( f ) ) &times; 100 % - - - ( 10 )
In formula: Δ n-the n time iteration error value;
Y n(t) response signal of-the n time iteration collection;
Y n(f)-y n(t) Fourier transform;
(5), finally to drive signal to carry out transmission shaft torture test as inputting.
CN201210537897.2A 2012-12-13 2012-12-13 Automobile transmission shaft fatigue test method Expired - Fee Related CN103033358B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201210537897.2A CN103033358B (en) 2012-12-13 2012-12-13 Automobile transmission shaft fatigue test method

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201210537897.2A CN103033358B (en) 2012-12-13 2012-12-13 Automobile transmission shaft fatigue test method

Publications (2)

Publication Number Publication Date
CN103033358A CN103033358A (en) 2013-04-10
CN103033358B true CN103033358B (en) 2014-12-10

Family

ID=48020484

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201210537897.2A Expired - Fee Related CN103033358B (en) 2012-12-13 2012-12-13 Automobile transmission shaft fatigue test method

Country Status (1)

Country Link
CN (1) CN103033358B (en)

Families Citing this family (10)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN104122095B (en) * 2013-04-28 2017-02-22 重庆长安汽车股份有限公司 Automobile internally-arranged handle endurance test tool
CN105223002A (en) * 2014-05-27 2016-01-06 上海北阅机械设备有限公司 A kind of constant velocity driving shaft loop cycle life test method
JP6214480B2 (en) * 2014-06-26 2017-10-18 三菱電機株式会社 Frequency response measuring device
CN104677625B (en) * 2015-03-25 2018-07-06 奇瑞汽车股份有限公司 A kind of unilateral random spectrum load test tooling of rear axle torsional fatigue and its test method
CN106610337A (en) * 2016-08-24 2017-05-03 襄阳达安汽车检测中心 Device for testing torsional fatigue of semi-shaft and transmission shaft of automobile
CN107389478B (en) * 2017-06-22 2019-11-12 上海工程技术大学 A kind of prediction technique of the material fatigue life based on wavelet packet analysis
CN107742013A (en) * 2017-09-28 2018-02-27 北京新能源汽车股份有限公司 Electric automobile drive shaft Life Calculating Methods and device
CN108051172B (en) * 2017-12-27 2019-06-04 湖南响箭重工科技有限公司 A kind of test method of swing arm leg fatigue test device
CN108414221B (en) * 2018-03-02 2019-09-06 重庆理工大学 A kind of fluid torque-converter end cap torsional fatigue strength test method
CN108469339B (en) * 2018-03-08 2019-10-25 武汉理工大学 Integrated form damper pulley characteristic test apparatus

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2762092Y (en) * 2004-10-27 2006-03-01 中国第一汽车集团公司 Vibration testing device of automobile driving shaft bending and torsion
DE202008016747U1 (en) * 2008-12-18 2009-05-07 Schaeffler Kg Device for measuring at least one measured variable on at least one shaft-joint arrangement
CN201464190U (en) * 2009-07-07 2010-05-12 重庆理工大学 Motorcycle frame fatigue test apparatus
CN102032967A (en) * 2011-01-24 2011-04-27 吉林大学 Torque calibration test bed for loader transmission shaft
CN202420839U (en) * 2012-01-17 2012-09-05 十堰晨鹏机电科技有限公司 Static torsional and torsional fatigue test bed for automobile transmission shaft

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2006064403A (en) * 2004-08-24 2006-03-09 Toshiba Consumer Marketing Corp Torque sensor

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN2762092Y (en) * 2004-10-27 2006-03-01 中国第一汽车集团公司 Vibration testing device of automobile driving shaft bending and torsion
DE202008016747U1 (en) * 2008-12-18 2009-05-07 Schaeffler Kg Device for measuring at least one measured variable on at least one shaft-joint arrangement
CN201464190U (en) * 2009-07-07 2010-05-12 重庆理工大学 Motorcycle frame fatigue test apparatus
CN102032967A (en) * 2011-01-24 2011-04-27 吉林大学 Torque calibration test bed for loader transmission shaft
CN202420839U (en) * 2012-01-17 2012-09-05 十堰晨鹏机电科技有限公司 Static torsional and torsional fatigue test bed for automobile transmission shaft

Non-Patent Citations (5)

* Cited by examiner, † Cited by third party
Title
JP特开2006-64403A 2006.03.09 *
三维空间多节万向传动轴扭振的分析计算;王鸿恩 等;《机械工程学报》;20000630;第36卷(第6期);第37-41页 *
基于道路模拟的摩托车平顺性研究;邹喜红;《中国博士学位论文全文数据库 工程科技Ⅱ辑》;20120315(第3期);C035-3 *
王鸿恩 等.三维空间多节万向传动轴扭振的分析计算.《机械工程学报》.2000,第36卷(第6期),第37-41页. *
邹喜红.基于道路模拟的摩托车平顺性研究.《中国博士学位论文全文数据库 工程科技Ⅱ辑》.2012,(第3期),C035-3. *

Also Published As

Publication number Publication date
CN103033358A (en) 2013-04-10

Similar Documents

Publication Publication Date Title
US5572440A (en) Motor vehicle vibrating system and method of controlling same
CN103792098B (en) Automobile electric booster steering system is comprehensive performance test bed
US4658656A (en) Multiple axis test machine reproducing road excited vehicle vibration
CN1330954C (en) Automobile electric power-assisted steering system simulation testing arrangement
US7146859B2 (en) Method for simulation of the life of a vehicle
Riley et al. Design, analysis and testing of a formula SAE car chassis
CN202886097U (en) Mobile rigidity test equipment
CN103149037B (en) Multi-degree-of-freedom suspension kinematics and elastokinematics attribute testing platform
CN103134692B (en) Simulation test board line frame for electric car power-driven system
CN1969177B (en) Control methodology for a multi-axial wheel fatigue system
CN100516813C (en) Multifunction shockabsorber for automobile and quarter cantilever operation-condition-simulating testing table
US8966987B2 (en) Road simulation test stand
JP5204223B2 (en) Horizontal position control for tire tread wear test equipment.
JP2010530059A (en) Method and system for tire evaluation and adjustment using load system and vehicle model
CN104535335B (en) A kind of Multi-axial Loading axle assembly long duration test stand
CN103471856B (en) Automobile front subframe assembly assay device and method
JP4082101B2 (en) Chassis dynamo device and vehicle test method
CN101476985B (en) Hardware-in-loop semi-physical vehicle transmission-integrated simulation experiment bench
CN101216376B (en) Four-column type rail vehicle bogie rigidity detection system
CN202582909U (en) Automobile steering system parameter measurement test bench
CN204328336U (en) Detecting robot of pipe
US5452605A (en) Dynamometer for simulating the inertial and road load forces encountered by motor vehicles
US5154076A (en) Dynamometer for simulating the inertial and road load forces encountered by motor vehicles
CN101592552B (en) Method for predicting multiaxial fatigue of automobile rear suspension
CN102607842B (en) Multi-operating condition extreme load testing system and method for wheel loader transmission system

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant
CF01 Termination of patent right due to non-payment of annual fee
CF01 Termination of patent right due to non-payment of annual fee

Granted publication date: 20141210

Termination date: 20161213