CN201876344U - Resonant vibration table with adjustable supporting rigidity - Google Patents
Resonant vibration table with adjustable supporting rigidity Download PDFInfo
- Publication number
- CN201876344U CN201876344U CN2010201920323U CN201020192032U CN201876344U CN 201876344 U CN201876344 U CN 201876344U CN 2010201920323 U CN2010201920323 U CN 2010201920323U CN 201020192032 U CN201020192032 U CN 201020192032U CN 201876344 U CN201876344 U CN 201876344U
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- shaking table
- vibration table
- spring
- rigidity
- resonant
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Abstract
The utility model relates to a resonant vibration table with adjustable supporting rigidity, which is characterized in that the elastic supporting rigidity of a movement part of the vibration table can be adjusted according to the load quality and the working frequency of the vibration table so that the natural frequency of the movement part of the vibration table is consistent with the working frequency of the vibration table, and the vibration table is in a resonant working state. By utilizing a resonance effect, an excitation force is reduced to the minimum level under the same vibration condition.
Description
Affiliated technical field
The utility model relates to a kind of device that obtains mechanical vibration.Shaking table in particular for vibration test and test specimen vibration detection
Background technology
At present, the main effect in the flexible support members of direction of vibration between the moving component of shaking table and the pedestal is the equilibrium position that keeps moving component, and its rigidity is constant.If regard test specimen, moving component and support component as a quality-spring oscillator, this oscillator has a natural frequency, and this natural frequency is determined by the gross mass of test specimen and moving component and the rigidity of support component.For same frequency of operation and amplitude, if the natural frequency of oscillator is near frequency of operation, because resonance effects only needs less exciting force just can realize the vibration of given amplitude; Otherwise,, then need very big exciting force could realize same amplitude when the natural frequency of oscillator during away from frequency of operation.Because the rigidity of existing shaking table support component is fixed, and that is to say that the natural frequency of test specimen, moving component and support system is fixed.And frequency of operation sets according to testing requirements, often away from natural frequency.Therefore, the vibrator of shaking table must provide big exciting force could satisfy test condition.So, for large-scale shaking table, not only increase cost, also will add some air-cooled or water cooling equipments is the vibrator cooling, has caused the waste of the energy.
Summary of the invention
For the natural frequency that overcomes existing shaking table can not be with the deficiency of frequency of operation variation, the utility model provides a kind of shaking table, this shaking table changes the natural frequency of test specimen, moving component and support system by the rigidity of adjusting support component, makes its frequency of operation near shaking table.Under same test condition, reduce the power and the energy consumption of vibrator.
The technical problems to be solved in the utility model is the support stiffness according to the quality adjustment moving component of the frequency of operation of shaking table and test specimen.
The technical scheme that its technical matters that solves the utility model adopts is following several
Scheme 1: one or several laminated spring are installed between the pedestal of the work top of moving component and shaking table.Laminated spring one end and work top are fixedly connected or are hinged, and the other end seamlessly inserts a removable bearing.Mobile support saddle can slide along the guide rail on the pedestal, when bearing when the mesa supports end moves, the rigidity of leaf spring increases.And when mobile round about, the rigidity of leaf spring reduces.
Scheme 2: one or several volute spring are installed between the pedestal of the work top of moving component and shaking table.Spring one end and work top are fixedly connected, and the other end seamlessly screws in a screw rod.Screw rod can be around the rotation of the inner thread sleeve on the pedestal, and when screw rod screwed in the length increase of spring, the rigidity of spring increased.Otherwise the rigidity of spring reduces.
Scheme 3: one or several air springs are installed between the pedestal of the work top of moving component and shaking table.The piston rod of air spring is fixedly connected or hinged in work top, and air spring is fixedly mounted on the pedestal of shaking table.Two air chambers of air spring pass through the retaining valve air feed by source of the gas.When the pressure of air chamber increased, the rigidity of air spring increased, otherwise the rigidity of air spring reduces.
The beneficial effects of the utility model are, make the natural frequency of shaking table vibrational system equal or near the desired frequency of operation of test condition, thus, can be reached same vibration condition by the exciting force of minimum.
Description of drawings
Below in conjunction with drawings and Examples the utility model is further specified.
Fig. 1 is embodiment 1 of the present utility model.
The moving component of 1. shaking tables among the figure 2. supports leaf spring, 3. mobile support saddle, 4. mobile support saddle slide rail, 5. shaking table pedestal.
Fig. 2 is embodiment 2 of the present utility model.
The moving component of 1. shaking tables among the figure, 2. volute spring, 3. screw rod, 4. inner thread sleeve, 5. shaking table pedestal.
Fig. 3 is embodiment 3 of the present utility model.
The moving component of 1. shaking tables among the figure, 2. air spring piston rod, 3. air spring, 4. retaining valve, 5. shaking table pedestal, 6. source of the gas.
Embodiment
In the embodiment shown in fig. 1, the motion parts of shaking table (1) connects with mobile support saddle (3) by supporting leaf spring (2), and mobile support saddle can move along slide rail (4), and the mobile support saddle slide rail is fixed on the pedestal (5) of shaking table.Motion parts is by forming resiliency supported between laminated spring and the shaking table pedestal, and when the movable plate spring abutment shortened spring length, support stiffness increased, otherwise the support stiffness of motion parts reduces.
In embodiment illustrated in fig. 2, the motion parts of shaking table (1) connects with screw rod (3) by volute spring (2), and screw rod can be around the rotation of the inner thread sleeve (4) on the pedestal (5), and when screw rod screwed in the length increase of spring, the rigidity of spring increased.Otherwise the rigidity of spring reduces.
In the embodiment shown in fig. 3, the work top of moving component (1) connects with the piston rod (2) of air spring (3), air spring is fixedly mounted on the pedestal (5) of shaking table, and by retaining valve (4) air feed, air chamber pressure is controlled by source of the gas two air chambers of cylinder by source of the gas (6).When the pressure of air chamber increased, the rigidity of air spring increased, otherwise the rigidity of air spring reduces.
Claims (4)
1. resonant shaking table of adjustable supports rigidity is characterized in that additional flexible support component between the pedestal of shaking table motion parts and shaking table, and the rigidity of this flexible support members can be adjusted.
2. the resonant shaking table of adjustable supports rigidity according to claim 1, the jib-length that it is characterized in that supporting the laminated spring of shaking table motion parts can be adjusted.
3. the resonant shaking table of adjustable supports rigidity according to claim 1 is characterized in that the helical spring useful effect number of turns that supports the shaking table motion parts can adjust.
4. the resonant shaking table of adjustable supports rigidity according to claim 1, the air chamber pressure that it is characterized in that supporting the air spring of shaking table motion parts can be adjusted.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201920323U CN201876344U (en) | 2010-05-17 | 2010-05-17 | Resonant vibration table with adjustable supporting rigidity |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN2010201920323U CN201876344U (en) | 2010-05-17 | 2010-05-17 | Resonant vibration table with adjustable supporting rigidity |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN201876344U true CN201876344U (en) | 2011-06-22 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN2010201920323U Expired - Fee Related CN201876344U (en) | 2010-05-17 | 2010-05-17 | Resonant vibration table with adjustable supporting rigidity |
Country Status (1)
| Country | Link |
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| CN (1) | CN201876344U (en) |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013151653A2 (en) * | 2012-04-06 | 2013-10-10 | Siemens Energy, Inc. | Stator coil removal method |
| CN103528785A (en) * | 2013-11-04 | 2014-01-22 | 苏州东菱振动试验仪器有限公司 | Method and device for generating high accelerated speed |
| CN105606326A (en) * | 2016-03-17 | 2016-05-25 | 西安陆洲智能传感技术有限公司 | Single spring suspension actuating vibration table |
| CN106168528A (en) * | 2016-08-23 | 2016-11-30 | 吉林大学 | Nonlinear elasticity auxiliary vibration device and vibration and sway platform |
| CN107014578A (en) * | 2017-04-06 | 2017-08-04 | 内蒙古工业大学 | Analogue experiment installation and its experimental method that vehicle influences on bridge floor cast-in-place concrete |
| CN108548646A (en) * | 2018-03-28 | 2018-09-18 | 中国航发北京航空材料研究院 | The quantitative measuring method of damage development overall process in a kind of vibration fatigue test |
| CN108844703A (en) * | 2018-04-08 | 2018-11-20 | 北京强度环境研究所 | Support device and TT&C system |
| CN110848372A (en) * | 2019-12-13 | 2020-02-28 | 无锡钟山环境工程科技有限公司 | Stepless speed change adjustable vibration absorption device |
| CN112082502A (en) * | 2020-07-31 | 2020-12-15 | 中国电力科学研究院有限公司 | Insulator non-contact three-dimensional size detection system |
| CN113737633A (en) * | 2021-09-15 | 2021-12-03 | 湖南大学 | Low-frequency tuned mass damper |
-
2010
- 2010-05-17 CN CN2010201920323U patent/CN201876344U/en not_active Expired - Fee Related
Cited By (14)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| WO2013151653A2 (en) * | 2012-04-06 | 2013-10-10 | Siemens Energy, Inc. | Stator coil removal method |
| WO2013151653A3 (en) * | 2012-04-06 | 2014-10-16 | Siemens Energy, Inc. | Stator coil removal method |
| CN103528785A (en) * | 2013-11-04 | 2014-01-22 | 苏州东菱振动试验仪器有限公司 | Method and device for generating high accelerated speed |
| CN105606326A (en) * | 2016-03-17 | 2016-05-25 | 西安陆洲智能传感技术有限公司 | Single spring suspension actuating vibration table |
| CN106168528A (en) * | 2016-08-23 | 2016-11-30 | 吉林大学 | Nonlinear elasticity auxiliary vibration device and vibration and sway platform |
| CN107014578A (en) * | 2017-04-06 | 2017-08-04 | 内蒙古工业大学 | Analogue experiment installation and its experimental method that vehicle influences on bridge floor cast-in-place concrete |
| CN108548646A (en) * | 2018-03-28 | 2018-09-18 | 中国航发北京航空材料研究院 | The quantitative measuring method of damage development overall process in a kind of vibration fatigue test |
| CN108548646B (en) * | 2018-03-28 | 2020-06-19 | 中国航发北京航空材料研究院 | Quantitative test method for whole damage evolution process in vibration fatigue test |
| CN108844703A (en) * | 2018-04-08 | 2018-11-20 | 北京强度环境研究所 | Support device and TT&C system |
| CN110848372A (en) * | 2019-12-13 | 2020-02-28 | 无锡钟山环境工程科技有限公司 | Stepless speed change adjustable vibration absorption device |
| CN110848372B (en) * | 2019-12-13 | 2024-04-09 | 无锡钟山环境工程科技有限公司 | Vibration absorbing device with adjustable infinitely variable speed |
| CN112082502A (en) * | 2020-07-31 | 2020-12-15 | 中国电力科学研究院有限公司 | Insulator non-contact three-dimensional size detection system |
| CN112082502B (en) * | 2020-07-31 | 2023-02-28 | 中国电力科学研究院有限公司 | Insulator non-contact three-dimensional size detection system |
| CN113737633A (en) * | 2021-09-15 | 2021-12-03 | 湖南大学 | Low-frequency tuned mass damper |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| CF01 | Termination of patent right due to non-payment of annual fee |
Granted publication date: 20110622 Termination date: 20170517 |
|
| CF01 | Termination of patent right due to non-payment of annual fee |