CN102221470A - Performance parameter test system of silicon oil damper for vehicle - Google Patents
Performance parameter test system of silicon oil damper for vehicle Download PDFInfo
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- CN102221470A CN102221470A CN 201110081699 CN201110081699A CN102221470A CN 102221470 A CN102221470 A CN 102221470A CN 201110081699 CN201110081699 CN 201110081699 CN 201110081699 A CN201110081699 A CN 201110081699A CN 102221470 A CN102221470 A CN 102221470A
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- 238000012360 testing method Methods 0.000 title claims abstract description 29
- 239000003921 oil Substances 0.000 title claims description 24
- XUIMIQQOPSSXEZ-UHFFFAOYSA-N Silicon Chemical compound [Si] XUIMIQQOPSSXEZ-UHFFFAOYSA-N 0.000 title description 10
- 229910052710 silicon Inorganic materials 0.000 title description 10
- 239000010703 silicon Substances 0.000 title description 10
- 230000005284 excitation Effects 0.000 claims abstract description 28
- 230000008878 coupling Effects 0.000 claims abstract description 19
- 238000010168 coupling process Methods 0.000 claims abstract description 19
- 238000005859 coupling reaction Methods 0.000 claims abstract description 19
- 239000006096 absorbing agent Substances 0.000 claims abstract description 10
- 230000035939 shock Effects 0.000 claims abstract description 10
- 229920002545 silicone oil Polymers 0.000 claims abstract description 7
- 238000006243 chemical reaction Methods 0.000 claims abstract description 3
- 238000013016 damping Methods 0.000 claims description 11
- 239000010720 hydraulic oil Substances 0.000 claims description 11
- 238000005259 measurement Methods 0.000 claims description 9
- 230000009471 action Effects 0.000 claims description 3
- 230000000737 periodic effect Effects 0.000 claims description 3
- 238000000034 method Methods 0.000 description 6
- 230000010355 oscillation Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 4
- 241000196324 Embryophyta Species 0.000 description 3
- 238000004458 analytical method Methods 0.000 description 3
- 238000004364 calculation method Methods 0.000 description 2
- 238000002485 combustion reaction Methods 0.000 description 2
- 238000013461 design Methods 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 238000009826 distribution Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000002474 experimental method Methods 0.000 description 2
- 230000006870 function Effects 0.000 description 2
- 238000004519 manufacturing process Methods 0.000 description 2
- 230000008569 process Effects 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 238000004088 simulation Methods 0.000 description 2
- 240000007594 Oryza sativa Species 0.000 description 1
- 235000007164 Oryza sativa Nutrition 0.000 description 1
- 230000002159 abnormal effect Effects 0.000 description 1
- 230000003321 amplification Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 230000015556 catabolic process Effects 0.000 description 1
- 238000013500 data storage Methods 0.000 description 1
- 230000007812 deficiency Effects 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000009434 installation Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003199 nucleic acid amplification method Methods 0.000 description 1
- 230000000505 pernicious effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 235000009566 rice Nutrition 0.000 description 1
- 238000007789 sealing Methods 0.000 description 1
- 230000001629 suppression Effects 0.000 description 1
- 238000010998 test method Methods 0.000 description 1
- 230000001052 transient effect Effects 0.000 description 1
- 238000013519 translation Methods 0.000 description 1
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Abstract
本发明公开了一种车用硅油减振器性能参数测试系统。它包括顺次相连的变频器、变频电机、弹性联轴节、扭振激励装置、联轴节、第一测量齿盘、可调惯性飞轮、主轴、第二测量齿盘、减振器，扭振激励装置与液压泵站相连，第一测量齿盘上方设有第一磁电传感器，第二测量齿盘上方设有第二磁电传感器，第一、二磁电传感器分别与NI-PXI6250采集卡相连、NI-PXI6250采集卡与计算机相连。本发明可以模拟不同缸数的发动机，调整惯量盘惯量大小，实现转速较大范围的调节；测试系统可以连续测量变化迅速的瞬时速度，并对瞬时速度的微小变化有极高的分辨能力，响应速度快；测试系统节约了实车检测的成本，降低了实车测试的危险性，实现低成本下高效测量减振器内部性能参数的功能。
The invention discloses a performance parameter testing system of a silicone oil shock absorber for vehicles. It includes a frequency converter connected in sequence, a frequency conversion motor, an elastic coupling, a torsional vibration excitation device, a coupling, a first measuring toothed disc, an adjustable inertia flywheel, a main shaft, a second measuring toothed disc, a shock absorber, a torsional The vibration excitation device is connected with the hydraulic pump station. The first magnetoelectric sensor is installed above the first measuring toothed disc, and the second magnetoelectric sensor is installed above the second measuring toothed disc. The first and second magnetoelectric sensors are respectively connected with NI-PXI6250 The card is connected, and the NI-PXI6250 acquisition card is connected with the computer. The invention can simulate engines with different numbers of cylinders, adjust the inertia of the inertia plate, and realize the adjustment of the rotation speed in a large range; Fast speed; the test system saves the cost of real vehicle testing, reduces the risk of real vehicle testing, and realizes the function of efficiently measuring the internal performance parameters of the shock absorber at low cost.
Description
Technical field
The present invention relates to a kind of automobile-used silicon oil damper performance parameter test system, be particularly related to a kind of with variable-frequency motor, hydraulic power unit drives the torsional excitation device and simulates true engine luggine situation, carry out data with virtual instrument test ment and obtain, the automobile-used torsional vibration damper performance parameter test system that analyzes with computer-aided control.
Background technology
Twisting vibration is that rotating machinery shaft is a kind of special vibration mode, it is because axle system is not absolute rigid body in essence, there is elasticity, thereby in the rotary course that carries out with average velocity, can produce the fluctuating of the instantaneous velocity of different sizes, out of phase between each elastomeric element because of a variety of causes, form twisting back and forth along sense of rotation.
The harm of twisting vibration is very big, and the crankshaft torsion vibration that produces in the internal combustion engine process can make bent axle and relevant movable body thereof produce extra-stress on the one hand, simultaneously, also support equipment is had a negative impact.When the frequency of driving torque and I. C. engine crankshaft axle are that the natural torsion vibration frequency is when identical, also can produce " resonance " phenomenon, this will make twisting vibration obtain huge dynamic amplification, thereby increased suffered distorting stress in the axle system greatly, cause axle system that various accidents take place, or cause the working condition of other annexes unusual, when serious, pernicious engine-damaged accidents such as crankshaft breakdown can appear.
In order to reduce torsional oscillation, people are constantly excavating the method for vibration damping and the form of realization.Reduce the natural frequency that torsional oscillation can Adjustment System, by changing the natural frequency of torsional vibration system, thereby make the resonance speed of total system obtain changing.The intrinsic natural frequency of vibration of internal combustion engine shafting multimass system torsional oscillation depends on various piece inertia and flexible numerical value and distribution situation thereof in the system fully.The variation of the inertia values of any one parts or elasticity number in the system comprises the change of their distributing positions, can cause the variation of total system natural frequency.Therefore, the inertia of each parts and flexible numerical value and distribution situation thereof in the change system can change system frequency significantly, thereby effectively avoid judder.In addition can also be by reducing the energy of exciting, the modes such as energy consumption that increase damping are come vibration damping.
The main physical parameters of sign vibration damper performance is damping, inertia and rigidity.Its inertia calculates easily in design analysis to be determined, its damping is difficult to calculate and determines also control not too easily in the mill.Therefore, generally to adopt test method to determine the actual damping of vibration damper.Silicon oil damper is an engine torsional vibration damper commonly used, and its structure is very special, is made up of the annular casing of sealing and the annular inertia disk that is positioned at wherein, and both can relatively rotate.Be full of the silicone oil of certain viscosity in its airtight slit, rely on the inertia of inertia disk and the damping action of silicone oil just can have the function that consumes the torsional oscillation energy, reduces vibration.Owing to be difficult to detect the motion state of inertia disk, must adopt the just damping parameter of this vibration damper of energy measurement of special experimental technique.
The performance of silicon oil damper is subjected to the influence of several factors, is often revised repeatedly through test repeatedly by the theoretical formula result calculated, could be as the foundation of design vibration damper.Carry out bench test on the engine and could check effectiveness in vibration suppression and have only by vibration damper is installed in for main engine plants.Present domestic most of vibration damper factory has very strong productive capacity, but not research fully of performance to vibration damper, main engine plants carry out can't obtaining in the analog computation analysis performance parameter of vibration damper, computational accuracy is not high, cause a large amount of installation test of coupling needs of vibration damper and engine, so not only a large amount of wastes of manpower, material resources and financial resources, and cause accident to take place easily.
Summary of the invention
The objective of the invention is to overcome existing the deficiencies in the prior art, a kind of automobile-used silicon oil damper performance parameter test system is provided.
Automobile-used silicon oil damper performance parameter test system comprises that frequency converter, variable-frequency motor, elastic coupling, torsional excitation device, shaft coupling, first measure fluted disc, adjustable inertial flywheel, main shaft, second and measure fluted disc, vibration damper, first magnetoelectric transducer, second magnetoelectric transducer, NI-PXI6250 capture card, computing machine, hydraulic power unit; It is continuous in turn that frequency converter, variable-frequency motor, elastic coupling, torsional excitation device, shaft coupling, first are measured fluted disc, adjustable inertial flywheel, main shaft, second is measured fluted disc, vibration damper, hydraulic power unit links to each other with the torsional excitation device, above the first measurement fluted disc, be provided with first magnetoelectric transducer, above the second measurement fluted disc, be provided with second magnetoelectric transducer, first magnetoelectric transducer links to each other with the NI-PXI6250 capture card respectively with second magnetoelectric transducer, and the NI-PXI6250 capture card links to each other with computing machine; Hydraulic power unit comprises accumulator, tensimeter, motor, non-return valve, surplus valve, solenoid valve, oil inlet and outlet, hydraulic oil container; Hydraulic oil container is provided with accumulator, tensimeter, motor, non-return valve, surplus valve, solenoid valve, oil inlet and outlet; Hydraulic power unit provides oil pressure to the torsional excitation device, frequency converter and variable-frequency motor drive the torsional excitation device, the torsional excitation device is changed the line of production at oil pressure effect backspin and is given birth to periodic acting force, the duty of simulated engine, test macro main shaft two ends first are measured the magnetoelectric transducer output signal of the fluted disc and the second measurement fluted disc and are gathered by slave computer NI-PXI6250 analog input card, handle and calculate the damping capacity parameter of obtaining vibration damper by the host computer PC.
The pressure of the hydraulic power unit maximum of automobile-used silicon oil damper performance parameter test system is 25Mpa, and the frequency converter peak power is 7.5KW, and peak torque is 50 Ns of rice, and first measures fluted disc and second measures fluted disc 120 teeth are arranged respectively.
The beneficial effect that the present invention compared with prior art has:
1) belong to the test macro of domestic association area independent research, can under lower cost, carry out the mensuration of vibration damper internal performance parameter, saved cost and efficient that real vehicle detects greatly, and improved the security of experiment greatly,
2) can realize that different cylinders count the simulation of engine, and can adjust the inertia size of inertia dish according to the calculation requirement of inertia, variable-frequency motor scalable rotating speed interval range is big, and range of application and simulation context are bigger.
3) test macro adopts the high-frequency count method, the high-frequency impulse number in the time of storing single tooth through sensor, and response speed is exceedingly fast, but continuous coverage changes instantaneous velocity rapidly, and the subtle change of instantaneous velocity is had high resolution characteristic.Adopt the method, both satisfied the small Testing requirement that is difficult to of twisting vibration, also satisfied the continuous coverage under the less situation of anglec of rotation step-length.
4) this experimental system both can be used for the test of vibration damper performance parameter, can be used for engine and vibration damper matching test again, had realized functional diversities.
Description of drawings
Fig. 1 is automobile-used silicon oil damper performance parameter test system architecture synoptic diagram;
Fig. 2 is a hydraulic power unit structural representation of the present invention;
Fig. 3 is control and analytic system functional block diagram.
Among the figure: frequency converter 1, variable-frequency motor 2, elastic coupling 3, torsional excitation device 4, shaft coupling 5, first are measured fluted disc 6, adjustable inertial flywheel 7, main shaft 8, the second measurement fluted disc 9, vibration damper 10, first magnetoelectric transducer 11, second magnetoelectric transducer 12, NI-PXI6250 capture card 13, computing machine 14, hydraulic power unit 15, accumulator 16, tensimeter 17, motor 18, non-return valve 19, surplus valve 20, solenoid valve 21, oil inlet and outlet 22, hydraulic oil container 23.
Embodiment
Below in conjunction with accompanying drawing the present invention is described in further detail, but not as a limitation of the invention.
As shown in Figure 1, a kind of automobile-used silicon oil damper performance parameter test system, it comprises that frequency converter 1, variable-frequency motor 2, elastic coupling 3, torsional excitation device 4, shaft coupling 5, first measure fluted disc 6, adjustable inertial flywheel 7, main shaft 8, second and measure fluted disc 9, vibration damper 10, first magnetoelectric transducer 11, second magnetoelectric transducer 12, NI-PXI6250 capture card 13, computing machine 14, hydraulic power unit 15; It is continuous in turn that frequency converter 1, variable-frequency motor 2, elastic coupling 3, torsional excitation device 4, shaft coupling 5, first are measured fluted disc 6, adjustable inertial flywheel 7, main shaft 8, second is measured fluted disc 9, vibration damper 10, hydraulic power unit 15 links to each other with torsional excitation device 4, above the first measurement fluted disc 6, be provided with first magnetoelectric transducer 11, above the second measurement fluted disc 9, be provided with second magnetoelectric transducer 12, first magnetoelectric transducer 11 links to each other with NI-PXI6250 capture card 13 respectively with second magnetoelectric transducer 12, and NI-PXI6250 capture card 13 links to each other with computing machine 14.
As shown in Figure 2, hydraulic power unit 15 comprises accumulator 16, tensimeter 17, motor 18, non-return valve 19, surplus valve 20, solenoid valve 21, oil inlet and outlet 22, hydraulic oil container 23; Hydraulic oil container 23 is provided with accumulator 16, tensimeter 17, motor 18, non-return valve 19, surplus valve 20, solenoid valve 21, oil inlet and outlet 22; Hydraulic power unit 15 provides oil pressure to torsional excitation device 4, and frequency converter 1 and variable-frequency motor 2 drive torsional excitation device 4, and torsional excitation device 4 is changed the line of production at oil pressure effect backspin and given birth to periodic acting force, the duty of simulated engine.
As shown in Figure 3, before the signals collecting hardware and software are carried out the parameter setting, first magnetoelectric transducer 11 that fluted disc 6 and second is measured fluted disc 9 places is measured at test macro main shaft 8 two ends first, second magnetoelectric transducer, 12 output signals are gathered by slave computer NI-PXI6250 analog input card 13, carry out the initial position translation to obtaining acquired signal, abnormal point is handled, identical value can be carried out the analysis of frequency domain and time domain after handling, obtain the damping capacity parameter of vibration damper, software systems can realize the data storage playback, generate functions such as form.
The course of work of the present invention is:
The cam of torsional excitation device 4 inside links to each other with variable-frequency motor 2 by elastic coupling 3, variable-frequency motor 2 is subjected to the control of frequency converter 1, operating personnel are by adjusting frequency converter 1, needed moment of torsion and tach signal are passed to variable-frequency motor 2, thus the rotating speed and the moment of torsion of control of conversion motor 2 and torsional excitation device 4 inner cam.Acting as of elastic coupling 3 protected variable-frequency motor 2 in order to avoid the driving torque of torsional excitation device 4 outputs impacts variable-frequency motor.
NI-PXI6250 capture card 13 has 68 road acquisition channels, wherein comprise 2 road 5V dc voltage output ends, No. 2 counter passages, 2 tunnel DC voltage output of capture card 13 is to magnetoelectric transducer 11,12 power supplies, No. 2 counter passages adopt the high-frequency count method that data are carried out record.After the data of being gathered write computer version from the integrated circuit board buffer memory, can carry out transient speed, the fluctuation of speed, torsional oscillation amplitude, the analytical calculation of resistance of shock absorber performance parameter to data.
Claims (4)
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201110081699A CN102221470B (en) | 2011-04-01 | 2011-04-01 | Automotive silicone oil shock absorber performance parameter testing system |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201110081699A CN102221470B (en) | 2011-04-01 | 2011-04-01 | Automotive silicone oil shock absorber performance parameter testing system |
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| CN102221470A true CN102221470A (en) | 2011-10-19 |
| CN102221470B CN102221470B (en) | 2012-09-19 |
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Cited By (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103149036A (en) * | 2013-03-08 | 2013-06-12 | 山东理工大学 | Analysis method for external characteristic test in shock absorber |
| CN104849010A (en) * | 2015-05-28 | 2015-08-19 | 江阴众和电力仪表有限公司 | Jet fan vibration and loosening excitation test bench |
| CN105021412A (en) * | 2014-04-18 | 2015-11-04 | 上海汽车集团股份有限公司 | Automobile shock absorber performance test method and automobile shock absorber performance test system |
| CN103759940B (en) * | 2014-01-17 | 2016-03-30 | 雪龙集团股份有限公司 | A kind of cooling fan of engine silicon oil clutch damping test testing table and method |
| WO2019047968A1 (en) * | 2017-09-11 | 2019-03-14 | 东莞理工学院 | Testing module and system for use in hydraulic shock absorber damping valve experiments and experimentation method |
| CN110361172A (en) * | 2018-04-04 | 2019-10-22 | 中国船舶重工集团公司第七一一研究所 | A kind of experimental rig and pilot system for torsional vibration damper |
| CN111811815A (en) * | 2020-07-30 | 2020-10-23 | 重庆长安汽车股份有限公司 | System and method for testing natural frequency of torsional vibration reduction belt pulley |
| CN115235776A (en) * | 2022-06-30 | 2022-10-25 | 潍柴动力股份有限公司 | A method, device and system for monitoring torsional vibration of a leaf spring shock absorber shafting |
| CN115405656A (en) * | 2022-07-19 | 2022-11-29 | 中车工业研究院有限公司 | Vibration damping control system test method, device, equipment and program product |
Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3955400A (en) * | 1973-08-27 | 1976-05-11 | Caterpillar Tractor Co. | Viscous damper and method for determining the rotational position of a weight thereof |
| DE3320570C1 (en) * | 1983-06-07 | 1984-08-23 | Ludwig Dr.-Ing. 7500 Karlsruhe Pietzsch | Device for testing shock absorbers for vehicles when installed |
| EP0429785B1 (en) * | 1989-12-01 | 1993-11-24 | Firma Carl Freudenberg | Test bench for a torsional vibration absorber |
| CN2272576Y (en) * | 1995-11-23 | 1998-01-14 | 王蟾芬 | Test table for vibration damper of vehicle |
| CN101226106A (en) * | 2008-02-01 | 2008-07-23 | 武汉理工大学 | Test method and test bench for multiple performances of dual-mass flywheel torsional damper |
| CN201138294Y (en) * | 2007-12-25 | 2008-10-22 | 中国北车集团四方车辆研究所 | Hydraulic shock absorber test bench |
| CN201307067Y (en) * | 2008-11-21 | 2009-09-09 | 青岛四方车辆研究所有限公司 | Test platform for oil pressure vibration damper |
| CN201607329U (en) * | 2009-12-30 | 2010-10-13 | 宁波市北仑恒铁机电制造有限公司 | Novel test station of oil-pressure absorber |
| CN201707218U (en) * | 2010-07-05 | 2011-01-12 | 常州科兴铁路装备有限公司 | Oil hydraulic shock absorber test bed |
-
2011
- 2011-04-01 CN CN201110081699A patent/CN102221470B/en not_active Expired - Fee Related
Patent Citations (9)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3955400A (en) * | 1973-08-27 | 1976-05-11 | Caterpillar Tractor Co. | Viscous damper and method for determining the rotational position of a weight thereof |
| DE3320570C1 (en) * | 1983-06-07 | 1984-08-23 | Ludwig Dr.-Ing. 7500 Karlsruhe Pietzsch | Device for testing shock absorbers for vehicles when installed |
| EP0429785B1 (en) * | 1989-12-01 | 1993-11-24 | Firma Carl Freudenberg | Test bench for a torsional vibration absorber |
| CN2272576Y (en) * | 1995-11-23 | 1998-01-14 | 王蟾芬 | Test table for vibration damper of vehicle |
| CN201138294Y (en) * | 2007-12-25 | 2008-10-22 | 中国北车集团四方车辆研究所 | Hydraulic shock absorber test bench |
| CN101226106A (en) * | 2008-02-01 | 2008-07-23 | 武汉理工大学 | Test method and test bench for multiple performances of dual-mass flywheel torsional damper |
| CN201307067Y (en) * | 2008-11-21 | 2009-09-09 | 青岛四方车辆研究所有限公司 | Test platform for oil pressure vibration damper |
| CN201607329U (en) * | 2009-12-30 | 2010-10-13 | 宁波市北仑恒铁机电制造有限公司 | Novel test station of oil-pressure absorber |
| CN201707218U (en) * | 2010-07-05 | 2011-01-12 | 常州科兴铁路装备有限公司 | Oil hydraulic shock absorber test bed |
Non-Patent Citations (4)
| Title |
|---|
| 《内燃机工程》 20030228 刘兴华等 曲轴减振器特性参数检测系统开发研究 61-65页 1-4 第24卷, 第2期 * |
| 《内燃机工程》 20100630 耿瑞光等 内燃机轴系可控扭振模拟试验台的研制 105-108页 1-4 第31卷, 第3期 * |
| 《机械设计与研究》 20071031 张晓玲等 基于虚拟仪器的转子扭振特性测试系统研究 77-79，86页 1-4 第23卷, 第5期 * |
| 《机电技术》 20100430 陈小梅 基于磁流变原理的汽车减振器控制系统研究 20-23页 1-4 , 第4期 * |
Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103149036A (en) * | 2013-03-08 | 2013-06-12 | 山东理工大学 | Analysis method for external characteristic test in shock absorber |
| CN103149036B (en) * | 2013-03-08 | 2015-04-22 | 山东理工大学 | Analysis method for external characteristic test in shock absorber |
| CN103759940B (en) * | 2014-01-17 | 2016-03-30 | 雪龙集团股份有限公司 | A kind of cooling fan of engine silicon oil clutch damping test testing table and method |
| CN105021412A (en) * | 2014-04-18 | 2015-11-04 | 上海汽车集团股份有限公司 | Automobile shock absorber performance test method and automobile shock absorber performance test system |
| CN104849010A (en) * | 2015-05-28 | 2015-08-19 | 江阴众和电力仪表有限公司 | Jet fan vibration and loosening excitation test bench |
| CN104849010B (en) * | 2015-05-28 | 2018-03-16 | 江阴众和电力仪表有限公司 | A kind of jet blower vibration is with loosening exciter test platform |
| WO2019047968A1 (en) * | 2017-09-11 | 2019-03-14 | 东莞理工学院 | Testing module and system for use in hydraulic shock absorber damping valve experiments and experimentation method |
| CN110361172A (en) * | 2018-04-04 | 2019-10-22 | 中国船舶重工集团公司第七一一研究所 | A kind of experimental rig and pilot system for torsional vibration damper |
| CN111811815A (en) * | 2020-07-30 | 2020-10-23 | 重庆长安汽车股份有限公司 | System and method for testing natural frequency of torsional vibration reduction belt pulley |
| CN115235776A (en) * | 2022-06-30 | 2022-10-25 | 潍柴动力股份有限公司 | A method, device and system for monitoring torsional vibration of a leaf spring shock absorber shafting |
| CN115235776B (en) * | 2022-06-30 | 2023-08-18 | 潍柴动力股份有限公司 | Method, device and system for monitoring torsional vibration of leaf spring shock absorber shaft system |
| WO2024001209A1 (en) * | 2022-06-30 | 2024-01-04 | 潍柴动力股份有限公司 | Method, apparatus and system for monitoring torsional vibration of shaft system of leaf spring damper |
| CN115405656A (en) * | 2022-07-19 | 2022-11-29 | 中车工业研究院有限公司 | Vibration damping control system test method, device, equipment and program product |
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| CN102221470B (en) | 2012-09-19 |
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