CN106153316B - A kind of Overload simulator resonance peak regulating mechanism - Google Patents
A kind of Overload simulator resonance peak regulating mechanism Download PDFInfo
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- CN106153316B CN106153316B CN201610448101.4A CN201610448101A CN106153316B CN 106153316 B CN106153316 B CN 106153316B CN 201610448101 A CN201610448101 A CN 201610448101A CN 106153316 B CN106153316 B CN 106153316B
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- connecting plate
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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
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- Investigating Strength Of Materials By Application Of Mechanical Stress (AREA)
Abstract
The invention discloses a kind of Overload simulator resonance peak regulating mechanism, the regulating mechanism makes resonance peak appear in the Overload simulator of particular range using the quality spring unit of flexible connected by adjusting the adjustment of its balance weight quality, connecting plate mechanical dimension；It is acted on by the locking of screw rod come fixed connecting plate, the resonance peak regulating mechanism is mainly made of machine assembly and mass-spring system two large divisions.
Description
Technical field
The invention belongs to load simulation fields, and in particular to a kind of Overload simulator resonance peak regulating mechanism.
Background technique
Passive type power (square) servo-control system is one of the capital equipment for carrying out aircraft ground HWIL simulation,
Engineering field is also referred to as load simulator or loading system.Its function is to reappear vehicle rudder in laboratory conditions
Suffered various load in the sky, so that the technical performance index of servo mechanism drive system is detected, by classical self destruction
All-real object tests the predictive research that is converted under laboratory condition, there is good controllability, without destructive, round-the-clock and
Advantage simple to operate, and this test can be repeated several times, thus the research environment of safety can be provided, shorten and develops
Period saves R & D Cost, improves reliability and success rate.For the development of course of new aircraft, using providing performance test data,
Reliable experimental data is provided for the popularization of new technology.
At this stage, widely applied load simulation system is mainly Based on Electro-hydraulic Loading Servo System, is based on electro-hydraulic servo technology
Loading system have the advantages that power is big, response block, anti-loading rigidity are big, basic theories is fairly perfect.
In modern mechanical processing, resilient connection hinders the raising of mechanical device performance, and flexible transmission system is easy to draw
Torsion resonance is played, so that system is unstable, mechanical device is endangered, reduces product quality.In order to preferably study load table resonance
Phenomenon devises the quality spring unit of flexible connected, by adjust the adjustment of its balance weight quality, connecting plate mechanical dimension from
And resonance peak is made to appear in particular range, it devises according to estrade stress size and adjusts the precession length of top device screw rod,
Installation locking nut, thus secures connecting plate and rack steadily.It is generated than only clipping connecting plate by balance block pressur plate
Frictional force fixedly connected part is more feasible reliable.Advantage is provided for industrial materials load test research in the future.
Summary of the invention
Aiming at the shortcomings in the prior art, the purpose of the present invention is the research to load table resonance phenomena, change this quality
The rigidity or quality of spring system can easily change the intrinsic frequency of subject servo mechanism, can accurately adjust resonance peak, make
It tests processing to industrial materials and provides reliable guide scheme in appearing in assigned frequency in a certain range.
To achieve the goals above, the technical solution adopted by the present invention is that:
A kind of Overload simulator resonance peak regulating mechanism, the regulating mechanism utilize the quality spring unit of flexible connected,
By adjusting the adjustment of its balance weight quality, connecting plate mechanical dimension, resonance peak is made to appear in the Overload simulator of particular range；
It is acted on by the locking of screw rod come fixed connecting plate, the resonance peak regulating mechanism is mainly by machine assembly and mass-spring system
Two large divisions's composition.
The composition of the machine assembly is by rack plate, balance weight clamping plate, half T-shape clamping plate and shockproof long bolt composition；
The mass-spring system is made of connector and balance weight.
The connecting plate of the mass-spring system is flexible connection, for generating vibration frequency, by changing connector
The quality of length and/or small mass block, to change the resonance frequency of system.
It is preferred that small mass block is 25Kg, even under the premise of meeting connecting plate maximum tension stress intensity no more than 300MPa
Fishplate bar is with a thickness of 20mm, width 50mm.
It is made of two large divisions: 1. machine assembly；2. mass-spring system.It is explained with reference to the accompanying drawing.In Fig. 1
In, the composition of machine assembly is by rack plate (crossbeam of load table), balance weight clamping plate, half T-type clamping plate, shockproof long bolt group
At.Mass-spring system is made of connector and balance weight.By change connector length or (and) quality of balance weight, i.e.,
The resonance frequency of system can effectively be changed.In Fig. 3, the rigidity of small mass block connecting plate and a series of given connecting plates
Thickness h, width b are anti-to release the effective of connecting plate under the premise of meeting connecting plate maximum tension stress intensity no more than 300Mpa
Length x；By Combination Design, when small mass block is 25Kg, connect plate thickness 20mm, when width 50mm, connecting plate other
Mechanical parameter such as table 1.
Table 1
Beneficial effect
For the simulation test research more easily to load table resonance phenomena.Top is adjusted according to estrade stress size
The precession length of part device screw rod, installation locking nut.Frictional force than only clipping connecting plate by balance block pressur plate and generating is solid
It is more feasible reliable to determine connector.
When estrade is by torque, the precession length of top device screw rod is adjusted on demand, installation locking nut is fixed
Connecting plate avoids the landing of connecting plate.
Change mass block quality, connecting plate length, can to the resonance peak that changes in a certain range of test requirements document and
Resonance frequency carries out analog study and analysis, makes it in appearing in assigned frequency in a certain range.
As a subsystem of Overload simulator, device space has been saved, it can be with the ingenious combination of total system.
Therefore, present invention mainly solves the adjustings of the resonance peak of load table.Resonance peak can be accurately adjusted, makes it in a segment limit
Assigned frequency is inside appeared in, processing is tested to industrial materials, reliable guide scheme, while the research to load table resonance peak is provided
It lays a solid foundation.
Detailed description of the invention
Fig. 1 is Overload simulator resonance peak adjusted design sectional view.
Fig. 2 is Overload simulator resonance peak adjusted design left view.
Fig. 3 is Overload simulator resonance peak adjusted design scale diagrams.
Fig. 4 is Overload simulator resonance peak adjusted design perspective view.
Fig. 5 is Overload simulator resonance peak adjusted design parameter schematic diagram.
Wherein, 1- bolt M8X50,2- balance weight clamping plate, half T-type clamping plate of 3-, the small balance weight connecting plate of 4-, the small balance of 5-
Block, 6- bolt M16X130,7- hex nut M12,8- bolt M8X60,9- hex nut M8,10- bolt M12X90, hexagonal spiral shell
Female M12,12- spindle central, 13- connecting plate, 14- balance weight.
Specific embodiment
Embodiment 1
The present invention will now be described in detail with reference to the accompanying drawings and examples.
Preparation before testing: test direction book is formulated, the determination including test objective, resonance frequency, resonance peak, from
And quality, test physical quantity and the biography of the table look-up length, small balance weight 5 of determining the small balance weight connecting plate 4 of mass-spring system
Sensor distribution method, test procedure etc., the material requesteds such as small balance weight, small balance weight connecting plate needed for preparing.
According to tabling look-up as a result, first being clamped small balance weight connecting plate 4 with balance weight clamping plate 2, as shown in Figure 1, small balance
Block connecting plate 4 is sufficiently thick to occur bending and deformation, and connected the two with bolt 8, locked using hex nut 9.Recycle spiral shell
Balance weight clamping plate 2 is connected and fixed by bolt 1 with estrade.
According to tabling look-up as a result, small balance weight 5 is first mounted in small 4 two sides of balance weight connecting plate, recycling bolt 10 will be small
Balance weight 5 is connect with small balance weight connecting plate 4, is locked using hex nut 11.
After installing this two experimental rigs, bolt 6 is screwed down to the position of needs, is added with the locking of hex nut 7
With fixation.After ready, progress self-test first determines whether Overload simulator can work normally.
It is as follows using the control system of Overload simulator after Overload simulator can work normally when system completion self-test
The precession length of top device bolt 6 is adjusted when estrade is by torque in Fig. 4 on demand, installs hex nut 7, and fixation is small
Balance weight connecting plate 4 avoids the landing of small balance weight 5.Such as Fig. 5, change the quality of small balance weight 5, small balance weight connecting plate 4
Length can carry out analog study and analysis to the resonance peak and resonance frequency changed in a certain range of test requirements document, make
It is in appearing in assigned frequency in a certain range.
Finally, it should be noted that obviously, above-described embodiment is only intended to clearly illustrate the application example, and simultaneously
The non-restriction to embodiment.For those of ordinary skill in the art, it can also do on the basis of the above description
Other various forms of variations or variation out.There is no necessity and possibility to exhaust all the enbodiments.And thus drawn
Shen go out obvious changes or variations still in the protection scope of the application type among.
Claims (3)
1. a kind of Overload simulator resonance peak regulating mechanism, it is characterised in that: the resonance peak regulating mechanism by machine assembly and
Mass-spring system two parts composition；The machine assembly is by rack plate, balance weight clamping plate, half T-shape clamping plate and shockproof long spiral shell
Bar composition；The mass-spring system is made of connecting plate and balance weight；The resonance peak regulating mechanism utilizes flexible connection
Mass-spring system makes the humorous of Overload simulator by adjusting balance weight quality, the connecting plate mechanical dimension of mass-spring system
Vibration peak occurs；Machine assembly and the two-part position connection relationship of mass-spring system are as follows: worn among the rack plate of machine assembly
The connecting plate in hole, mass-spring system is passed through from the hole, and half T-shape clamping plate is mounted on the top of rack plate, balance weight clamping plate peace
Mounted in the lower surface of rack plate, half T-shape clamping plate and balance weight clamping plate clamp the connecting plate of mass-spring system, and pass through spiral shell
The locking effect of bar carrys out fixed connecting plate, passes through half T-shape clamping plate and rack plate using shockproof long bolt, then with nut check,
The connecting plate of mass-spring system is fixedly clamped, and pass through half T-shape clamping plate and rack plate by changing shockproof long bolt
Length changes the length of connecting plate.
2. Overload simulator resonance peak regulating mechanism according to claim 1, it is characterised in that: the mass-spring system
Connecting plate is flexible connection, for generating vibration frequency, by changing the length of connecting plate and/or the quality of balance weight, to change
The resonance frequency of change system.
3. Overload simulator resonance peak regulating mechanism according to claim 2, it is characterised in that: drawn meeting connecting plate maximum
Under the premise of stress intensity is no more than 300MPa, the quality of balance weight is 25Kg, connecting plate with a thickness of 20mm, the width of connecting plate
Degree is 50mm.
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| Application Number | Priority Date | Filing Date | Title |
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| CN201610448101.4A CN106153316B (en) | 2016-06-20 | 2016-06-20 | A kind of Overload simulator resonance peak regulating mechanism |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201610448101.4A CN106153316B (en) | 2016-06-20 | 2016-06-20 | A kind of Overload simulator resonance peak regulating mechanism |
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| CN106153316A CN106153316A (en) | 2016-11-23 |
| CN106153316B true CN106153316B (en) | 2019-03-26 |
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Citations (4)
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| CN103615496A (en) * | 2013-12-05 | 2014-03-05 | 哈尔滨工程大学 | Cantilever beam type vibration absorber with adjustable frequency |
| CN103674351A (en) * | 2012-09-06 | 2014-03-26 | 日本电波工业株式会社 | External force detection device and external force detection sensor |
| CN104634419A (en) * | 2015-02-03 | 2015-05-20 | 深圳计为自动化技术有限公司 | Mass block and vibrating device of vibrating material switch and resonant frequency debugging method |
| CN104713721A (en) * | 2015-04-10 | 2015-06-17 | 株洲时代新材料科技股份有限公司 | Dynamic performance test platform of vibration isolator system and test method thereof |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE102011053325B4 (en) * | 2011-09-07 | 2022-09-29 | Dr. Ing. H.C. F. Porsche Aktiengesellschaft | Test bench for the dynamic testing of an individual chassis component or a complete axle system of a motor vehicle, as well as methods for testing the same |
| CN103454054B (en) * | 2013-08-07 | 2016-01-13 | 中国科学院力学研究所 | The vertical vibration experimental device of a kind of power controlled loading, variable layout |
| CN205175642U (en) * | 2015-12-03 | 2016-04-20 | 株洲时代新材料科技股份有限公司 | Bilayer and individual layer vibration isolation system vibration test bench with adjustable |
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Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103674351A (en) * | 2012-09-06 | 2014-03-26 | 日本电波工业株式会社 | External force detection device and external force detection sensor |
| CN103615496A (en) * | 2013-12-05 | 2014-03-05 | 哈尔滨工程大学 | Cantilever beam type vibration absorber with adjustable frequency |
| CN104634419A (en) * | 2015-02-03 | 2015-05-20 | 深圳计为自动化技术有限公司 | Mass block and vibrating device of vibrating material switch and resonant frequency debugging method |
| CN104713721A (en) * | 2015-04-10 | 2015-06-17 | 株洲时代新材料科技股份有限公司 | Dynamic performance test platform of vibration isolator system and test method thereof |
Non-Patent Citations (1)
| Title |
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| 基于电液式负载模拟器的谐振特性研究;陈策等;《液压与气动》;20131231(第10期);全文 |
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