CN109780130A - A kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression - Google Patents
A kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression Download PDFInfo
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- CN109780130A CN109780130A CN201910152269.4A CN201910152269A CN109780130A CN 109780130 A CN109780130 A CN 109780130A CN 201910152269 A CN201910152269 A CN 201910152269A CN 109780130 A CN109780130 A CN 109780130A
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- spring
- shock
- guide rail
- absorbing means
- energy trap
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Abstract
The invention discloses a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression, including two geometric linear springs, a support Hookean spring, mass block, guide rail, bracket and bottom plate composition；The shock-absorbing means is installed along adapter conical shell wall；It is moved along the rail by mass block and three Hookean spring movements is driven to realize purer cube stiffness characteristics, to constitute nonlinear energy trap device to achieve the effect that absorbing.The present invention has haved the function that vertical and horizontal vibration suppression by arranging nonlinear energy trap shock-absorbing means on satellite adapter conical shell wall and introducing Hookean spring along guide rail direction；The nonlinear energy trap apparatus structure is simple simultaneously, can easily be accommodated and installs, and has many advantages, such as that robustness is good, effectively wide-band vibration can inhibit and be not required to additional power source.
Description
Technical field
The invention belongs to rocket launching powered phase Satellite Vibration control technology fields, are related to a kind of for whole star vibration suppression
Nonlinear energy trap shock-absorbing means.
Background technique
In the powered phase of carrier rocket transmitting, environment locating for satellite is the most severe.In this stage, satellite can simultaneously by
The influence of a variety of load, and these load are distributed in wider frequency domain more.These oscillating loads frequently can lead to satellite
And sensing element failure thereon, and the most crucial position of carrier rocket is exactly satellite, satellite is damaged, and means that rocket is sent out
Penetrate the failure of task.Since nonlinear energy trap shock-absorbing means has the advantage of wideband absorbing, and there is quality and small in size etc.
Advantage, therefore the Satellite Vibration suppression technology based on nonlinear energy trap shock-absorbing means is just most important at carrier rocket transmitting
One of project.Usual nonlinear energy trap shock-absorbing means is adopted more since self gravitation effect will affect the feature of non-linear rigidity
Ensure that it, with non-linear rigidity, therefore can only solve the problems, such as oscillation crosswise with being horizontally arranged, but carrier rocket emits
Powered phase, satellite bears from longitudinal load more, and nonlinear energy trap shock-absorbing means can not very good solution master at present
The problem of dynamic section longitudinally shakes.
Summary of the invention
The object of the present invention is to provide a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression, solve existing
There is the problem of nonlinear energy trap shock-absorbing means present in technology can not inhibit powered phase satellite extensional vibration.
The technical scheme adopted by the invention is that a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression,
Including bottom plate, there are two rail brackets, rail brackets to be provided with groove, be provided with guide rail in groove, lead for opposite setting on bottom plate
Rail passes through described two rail brackets, and the both ends of guide rail are screwed on guide supporting, guide supporting screws bolts
It is fixed on rail brackets；Mass block is socketed on guide rail, mass block can be moved back and forth along guide rail；The both ends of mass block point
It is not connected with the overhead gage of geometric linear spring, the lower baffle plate of geometry spring is bolted in hinged groove, and hinged groove is set
It sets on spring support, spring support is bolted on bottom plate, and the present apparatus is integrally one using guide rail as the symmetrical of axis
Structure；Support Hookean spring is provided between mass block and rail brackets, support Hookean spring is socketed on guide rail, supports line
Property spring one end quality of connection block, the other end be fixed on guide supporting upper surface setting boss on, below with boss into
Row connection；Boss is connect with rail brackets with two screws.
Bottom plate is provided with elongated slot, and the elongated slot and spring support of bottom plate and the hole of rail brackets lower end are attached with bolt.
Guide rail surface is evenly arranged with multiple holes, adjusts and leads by selecting the hole of suitable guide rail to connect with guide supporting
The length of rail.
Geometric linear spring is fixed between overhead gage and lower baffle plate, the guiding axis of the pilot hole of overhead gage and lower baffle plate it
Between carry out clearance fit.
The two sides of nonlinear energy trap shock-absorbing means bottom plate are provided with boss, and the boss is along adapter conical shell wall balanced welding
It is connected on adapter conical shell wall.
Device inclination installation, the condition that the support Hookean spring of described device need to meet are as follows:
k1H=mg sin θ, k1=2kla/ l, la< 0, u < h
Wherein k1For the rigidity of support spring (9), h is the decrement of support spring (9), and m is mass block quality, and k is several
The rigidity of what spring (8), laFor the decrement of geometry spring (8), l is that the original of geometry spring (8) is long, and u is mass block deviation
The displacement of initial position, θ are the angle of satellite adapter conical shell bus and horizontal plane.
The beneficial effects of the present invention are:
1. the present invention using linear geometry spring and linear support spring cooperation by the way of, solve nonlinear energy because of
The problem of being influenced spring cube stiffness characteristics by self gravity factor, realizes purer cube stiffness characteristics.
2. the present invention not only reduces self gravity to along guide rail direction by being arranged along satellite adapter conical shell wall
The influence of cube rigidity, while can play and the effect inhibited jointly is vibrated to vertical and horizontal.
3. the present invention can be by adjusting separately the relative position of spring support and rail brackets come to geometry spring and branch
Support spring applies different precompressions to obtain different rigidity, so that device is more flexible adjustable.
4. the present invention is fixed on overhead gage and lower baffle plate in the seasonal geometric linear spring of design, the pilot hole of overhead gage
Clearance fit is carried out between the guiding axis of lower baffle plate, haveing an advantage that prevents geometry spring from bending during stretching.
5. the configuration of the present invention is simple, lighter weight are easily installed and adjust, the environment suitable for the vibration of whole star is subtracted
Vibration.
Detailed description of the invention
Fig. 1 is whole star nonlinear energy trap shock-absorbing means structural schematic diagram of the invention；
Fig. 2 is whole star nonlinear energy trap shock-absorbing means cross-sectional view；
Fig. 3 is the structural diagram of base plate of whole star nonlinear energy trap shock-absorbing means
Fig. 4 is scheme of installation of the whole star nonlinear energy trap shock-absorbing means in adapter；
In figure, 1. guide rails, 2. guide supportings, 3. rail brackets, 4. bottom plates, 5. hinged grooves, 6. bolts, 7. spring supports,
8. geometric linear spring, 9. support Hookean springs, 10. mass blocks, 11. spring supportings, 12. overhead gages, 13. lower baffle plates, 14. circles
Shape boss, 15. satellite conical shell adapters
Specific embodiment
The following describes the present invention in detail with reference to the accompanying drawings and specific embodiments.
A kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression, it is characterised in that: including bottom plate 4, bottom plate 4
There are two rail brackets 3, rail brackets 3 are provided with groove for upper opposite setting, and guide rail 1 is provided in groove, and guide rail 1 passes through described
Two rail brackets 3, the both ends of guide rail 1 are screwed on guide supporting 2, and guide supporting 2 is bolted to guide rail
On bracket 3；Mass block 10 is socketed on guide rail 1, mass block 10 can be moved back and forth along guide rail 1；The both ends of mass block 10 point
It is not connected with the overhead gage 12 of geometric linear spring 8, the lower baffle plate 13 of geometry spring 8 is fixed in hinged groove 5 by bolt 6,
Hinged groove 5 is arranged on spring support 7, and spring support 7 is bolted on bottom plate 4, and the present apparatus is integrally one to lead
Rail 1 is the symmetrical structure of axis；It is provided with support Hookean spring 9 between mass block 10 and rail brackets 3, supports Hookean spring 9
It is socketed on guide rail 1, supports one end quality of connection block 10 of Hookean spring 9, the other end is fixed on the setting of 3 upper surface of guide supporting
Boss 14 on, be attached below with boss 14；Boss 14 is connect with rail brackets 3 with two screws.
Bottom plate 4 is provided with elongated slot, and the elongated slot and spring support 7 of bottom plate 4 and the hole of 3 lower end of rail brackets are connected with bolt
It connects, facilitates the position of adjustment support to adjust the precompression of geometry spring 8 and support spring 9.
1 surface of guide rail is evenly arranged with multiple holes, is adjusted by selecting hole and the connection of guide supporting 2 of suitable guide rail 1
The length of whole guide rail 1.
Geometric linear spring 8 is fixed between overhead gage 12 and lower baffle plate 13, the pilot hole and lower baffle plate 13 of overhead gage 12
Guiding axis between carry out clearance fit, haveing an advantage that prevents geometry spring 8 from bending during stretching.
The two sides of nonlinear energy trap shock-absorbing means bottom plate 4 are provided with boss, and the boss is symmetrical along adapter conical shell wall
It is welded on adapter conical shell wall, only weight component has an impact a cube stiffness characteristics, not only reduces gravity, but also can be with
Have the function that absorb vertical and horizontal vibration.
Institute's device of the present invention is vertically-mounted, the condition that the support Hookean spring 9 need to meet are as follows:
k1H=mg sin θ, k1=2kla/ l, la< 0, u < h
Wherein k1For the rigidity of support spring 9, h is the decrement of support spring 9, and m is mass block quality, and k is geometry bullet
The rigidity of spring 8, laFor the decrement of geometry spring 8, l is that the original of geometry spring 8 is long, and u is that mass block deviates initial position
Displacement, θ are the angle of satellite adapter conical shell bus and horizontal plane.
Mass block 10 is attached on guide rail 1 and moves along guide rail 1, and initial position is equilbrium position, such as Fig. 1 institute
Show.It is moved downward when mass block 10 deviates initial position, mass block 10 drives the two geometric linear springs 8 in left and right to do stretching fortune
Dynamic, mass block 10 drives support spring 9 to do compression movement；It is moved upwards when mass block 10 deviates initial position, 10 band of mass block
Dynamic support spring 9 does extensional motion.
As shown in Figure 1, the decrement h of support spring 9 is used to support gravity caused by mass block, and support spring 9 is flat
Weighing apparatus position is just mass block initial position, that is, is met: k1H=mgsin θ, wherein wherein k1For the rigidity of support spring 9, h is
The decrement of support spring 9, m are mass block quality, and θ is the angle of adapter conical shell bus and horizontal plane.
As shown in Fig. 2, the right and left of mass block 10 respectively opens a slot, the overhead gage of geometry spring and the slot of mass block are used
It is bolted composition revolute pair.Lower baffle plate and hinged groove are also attached composition revolute pair with bolt.It is several in order to prevent
What spring 8 bends during stretching, carries out clearance fit between the pilot hole of overhead gage 12 and the guiding axis of lower block 13.
It, can be by adjusting as shown in figure 3, be provided with elongated slot at the hole cooperation of bottom plate and guide supporting 3 and spring supporting 11
Its position cooperated applies different precompressions to geometry spring 8.
When mass block is subjected to displacement u, the restoring force that geometry spring can be provided along guide rail direction relative to initial position are as follows:
F=2ku (l-l0)/l+ku3(l0/l3)+O(u3)
When considering that gravity factor and additional support spring 9 act on, generated restoring force are as follows:
F=u (k1+2kla/l)+ku3(l0/l3)+k1h-mgsinθ
Wherein l0Long for geometry spring original, l is compressed length, laFor reduction length and meet la=l-l0。
Purer cube rigidity in order to obtain needs that Monomial coefficient is allowed to be 0, i.e. k1=-2kla/l
, and la< 0.
Therefore, support spring and geometric linear spring need to meet condition: k1H=mg sin θ, k1=2kla/ l, la
< 0, u < h.
As shown in figure 4, bottom plate 4 is arranged symmetrically along the conical shell wall of adapter, the boss of insole board be welded in conical shell wall it
On.
A kind of nonlinear energy trap shock-absorbing means working principle for whole star vibration suppression provided by the invention is as follows:
Carrier rocket generates violent vibration in transmitting powered phase, and vibration is transmitted at satellite and the rocket faying face along rocket body, shape
At the displacement excitation source of satellite adapter, cause satellite adapter that high vibration occurs.Along with the vibration of satellite adapter,
The beginning of mass block 10 is moved up and down along guide rail 1.When mass block 10, which deviates equilbrium position, to be moved down, the overhead gage 12 of spring
Lower baffle plate 13 is driven to start to deflect down, the axis of overhead gage 12 is drawn out from the hole of lower baffle plate 13, and along with geometry spring 8
Stretching, meanwhile, mass block 10, which is moved down, produces compression to support spring 9, and mass block 10 starts after reaching certain position
It replys.When mass offset equilbrium position moves up, spring overhead gage 12 drives lower baffle plate 13 to start to upward deflect, overhead gage
Axis be drawn out from the hole of lower baffle plate 13, and along with the stretching of geometry spring 8, meanwhile, mass block 10 is moved down to branch
Support spring produces stretching.Mass block 10 moves back and forth in this way, which absorbs most of energy, and is consumed, and plays
The effect of absorbing.It is in tilted layout along adapter conical shell due to being, so the vibration of vertical direction had both can be absorbed in the device,
The vibration of horizontal direction can be absorbed again.
This structure considers that 10 gravity of mass block makes the rigidity of structure by the cooperation of geometry spring and support spring
Reach purer cube stiffness characteristics, realizes the requirement of nonlinear energy trap device.
The present invention using linear geometry spring and linear support spring cooperation by the way of, solve nonlinear energy because by
Self gravity factor influences the problem of spring cube stiffness characteristics, realizes purer cube stiffness characteristics.Along satellite adapter
Conical shell wall is arranged, and not only reduces self gravity to the influence along guide rail direction cube rigidity, while can be played to vertical
To the effect inhibited jointly with oscillation crosswise, the relative position for adjusting spring supporting and guide supporting is come to geometry spring and support
Spring applies different precompressions to obtain different rigidity, so that device is more flexible adjustable.Geometric linear spring is fixed on
On overhead gage and lower baffle plate, clearance fit is carried out between the pilot hole of overhead gage and the guiding axis of lower baffle plate, is had an advantage that
Prevent geometry spring from bending during stretching, in addition to this, the configuration of the present invention is simple, lighter weight, be easily installed and
Adjustment, the environment suitable for the vibration of whole star carry out vibration damping.
Claims (6)
1. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression, it is characterised in that: including bottom plate (4), bottom plate
(4) there are two rail brackets (3), rail brackets (3) to be provided with groove, guide rail (1), guide rail are provided in groove for opposite setting on
(1) described two rail brackets (3) are passed through, the both ends of guide rail (1) are screwed on guide supporting (2), guide supporting
(2) it is bolted on rail brackets (3)；It is socketed on guide rail (1) mass block (10), mass block (10) can be along guide rail
(1) it moves back and forth；The both ends of mass block (10) are connected with the overhead gage (12) of geometric linear spring (8) respectively, geometry spring (8)
Lower baffle plate (13) be fixed in hinged groove (5) by bolt (6), hinged groove (5) is arranged on spring support (7), spring branch
Frame (7) is bolted on bottom plate (4), and the present apparatus is integrally a symmetrical structure with guide rail (1) for axis；In mass block
(10) support Hookean spring (9) is provided between rail brackets (3), support Hookean spring (9) is socketed on guide rail (1), is propped up
One end quality of connection block (10) of Hookean spring (9) is supportted, the other end is fixed on the boss (14) of rail brackets (3) upper surface setting
On, it is attached below with boss (14)；Boss (14) is connect with rail brackets (3) with two screws.
2. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression according to claim 1, feature exist
In the bottom plate (4) is provided with elongated slot, the elongated slot and spring support (7) of bottom plate (4) and the hole bolt of rail brackets (3) lower end
It is attached.
3. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression according to claim 1, feature exist
In guide rail (1) surface is evenly arranged with multiple holes, is connected by the hole and guide supporting (2) that select suitable guide rail (1)
To adjust the length of guide rail (1).
4. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression according to claim 1, feature exist
In the geometric linear spring (8) is fixed between overhead gage (12) and lower baffle plate (13), and the pilot hole of overhead gage (12) is under
Clearance fit is carried out between the guiding axis of baffle (13).
5. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression according to claim 1, feature exist
In the two sides of the nonlinear energy trap shock-absorbing means bottom plate (4) are provided with boss, and the boss is symmetrical along adapter conical shell wall
It is welded on adapter conical shell wall.
6. a kind of nonlinear energy trap shock-absorbing means for whole star vibration suppression according to claim 3, feature exist
In: described device inclination installation；The condition that support Hookean spring (9) need to meet are as follows:
k1H=mgsin θ, k1=2kla/ l, la< 0, u < h
Wherein k1For the rigidity of support spring (9), h is the decrement of support spring (9), and m is mass block quality, and k is geometry spring
(8) rigidity, laFor the decrement of geometry spring (8), l is that the original of geometry spring (8) is long, and u is that mass block deviates initial bit
The displacement set, θ are the angle of satellite adapter conical shell bus and horizontal plane.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910152269.4A CN109780130B (en) | 2019-02-28 | 2019-02-28 | Nonlinear energy trap vibration absorption device for whole-satellite vibration suppression |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201910152269.4A CN109780130B (en) | 2019-02-28 | 2019-02-28 | Nonlinear energy trap vibration absorption device for whole-satellite vibration suppression |
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| Publication Number | Publication Date |
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| CN109780130A true CN109780130A (en) | 2019-05-21 |
| CN109780130B CN109780130B (en) | 2021-01-15 |
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| CN201910152269.4A Expired - Fee Related CN109780130B (en) | 2019-02-28 | 2019-02-28 | Nonlinear energy trap vibration absorption device for whole-satellite vibration suppression |
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Cited By (16)
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| CN110296182A (en) * | 2019-06-28 | 2019-10-01 | 西安理工大学 | A kind of tuning quality damper vibration damping system being incorporated to nonlinear energy trap |
| CN110566617A (en) * | 2019-09-17 | 2019-12-13 | 天津理工大学 | magnetism-rigidity-based non-smooth vibration absorber |
| CN110566616A (en) * | 2019-09-17 | 2019-12-13 | 天津理工大学 | passive variable-rigidity non-smooth vibration absorber |
| CN110886808A (en) * | 2019-12-04 | 2020-03-17 | 上海大学 | Amplitude limiting type nonlinear energy trap vibration damper |
| CN110939673A (en) * | 2019-12-04 | 2020-03-31 | 上海大学 | Nonlinear vibration damper of coupling segmental rigidity |
| CN111140616A (en) * | 2020-01-14 | 2020-05-12 | 天津理工大学 | Negative stiffness enhanced nonlinear vibration absorber |
| CN111219296A (en) * | 2020-04-14 | 2020-06-02 | 扬州大学 | Device suitable for restraining vortex-induced vibration of wind turbine tower |
| CN111306243A (en) * | 2020-04-01 | 2020-06-19 | 青岛理工大学 | Slideway type nonlinear energy trap vibration damper |
| CN111396498A (en) * | 2019-12-06 | 2020-07-10 | 浙江运达风电股份有限公司 | Nonlinear vibration damper for wind turbine tower |
| CN111424832A (en) * | 2020-03-23 | 2020-07-17 | 广州大学 | Tuned mass damper with adjustable nonlinear energy trap and inertial volume |
| CN111641351A (en) * | 2020-05-18 | 2020-09-08 | 扬州大学 | Vortex vibration piezoelectric power generation device with broadband energy collection function |
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| CN114086806A (en) * | 2021-10-11 | 2022-02-25 | 东南大学 | Two-dimensional eccentric rotation nonlinear energy trap device and vibration absorption and energy consumption method |
| CN114370478A (en) * | 2021-12-29 | 2022-04-19 | 同济大学 | Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity |
| CN114542854A (en) * | 2022-02-18 | 2022-05-27 | 中铁建港航局集团勘察设计院有限公司 | Damping device for engineering machinery supporting leg |
| CN115095624A (en) * | 2022-06-16 | 2022-09-23 | 哈尔滨工程大学 | Elastic device, control method, vibration absorber, vibration isolator and vibration energy collector |
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| CN110296182A (en) * | 2019-06-28 | 2019-10-01 | 西安理工大学 | A kind of tuning quality damper vibration damping system being incorporated to nonlinear energy trap |
| CN110566617A (en) * | 2019-09-17 | 2019-12-13 | 天津理工大学 | magnetism-rigidity-based non-smooth vibration absorber |
| CN110566616A (en) * | 2019-09-17 | 2019-12-13 | 天津理工大学 | passive variable-rigidity non-smooth vibration absorber |
| CN110886808B (en) * | 2019-12-04 | 2021-08-06 | 上海大学 | Amplitude limiting type nonlinear energy trap vibration damper |
| CN110886808A (en) * | 2019-12-04 | 2020-03-17 | 上海大学 | Amplitude limiting type nonlinear energy trap vibration damper |
| CN110939673A (en) * | 2019-12-04 | 2020-03-31 | 上海大学 | Nonlinear vibration damper of coupling segmental rigidity |
| CN110939673B (en) * | 2019-12-04 | 2021-10-08 | 上海大学 | Nonlinear vibration damper of coupling segmental rigidity |
| CN111396498B (en) * | 2019-12-06 | 2021-08-17 | 浙江运达风电股份有限公司 | Nonlinear vibration damper for wind turbine tower |
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| CN111140616A (en) * | 2020-01-14 | 2020-05-12 | 天津理工大学 | Negative stiffness enhanced nonlinear vibration absorber |
| CN111424832A (en) * | 2020-03-23 | 2020-07-17 | 广州大学 | Tuned mass damper with adjustable nonlinear energy trap and inertial volume |
| CN111424832B (en) * | 2020-03-23 | 2021-08-17 | 广州大学 | Tuned mass damper with adjustable nonlinear energy trap and inertial volume |
| CN111306243A (en) * | 2020-04-01 | 2020-06-19 | 青岛理工大学 | Slideway type nonlinear energy trap vibration damper |
| CN111219296A (en) * | 2020-04-14 | 2020-06-02 | 扬州大学 | Device suitable for restraining vortex-induced vibration of wind turbine tower |
| CN111219296B (en) * | 2020-04-14 | 2021-12-17 | 扬州大学 | Device suitable for restraining vortex-induced vibration of wind turbine tower |
| CN111641351A (en) * | 2020-05-18 | 2020-09-08 | 扬州大学 | Vortex vibration piezoelectric power generation device with broadband energy collection function |
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| CN114086806A (en) * | 2021-10-11 | 2022-02-25 | 东南大学 | Two-dimensional eccentric rotation nonlinear energy trap device and vibration absorption and energy consumption method |
| CN114370478A (en) * | 2021-12-29 | 2022-04-19 | 同济大学 | Inertial volume type nonlinear energy trap vibration damping system with adjustable nonlinear rigidity |
| CN114542854A (en) * | 2022-02-18 | 2022-05-27 | 中铁建港航局集团勘察设计院有限公司 | Damping device for engineering machinery supporting leg |
| CN115095624A (en) * | 2022-06-16 | 2022-09-23 | 哈尔滨工程大学 | Elastic device, control method, vibration absorber, vibration isolator and vibration energy collector |
| CN115095624B (en) * | 2022-06-16 | 2023-09-22 | 哈尔滨工程大学 | Elastic device, control method, vibration absorber, vibration isolator and vibration energy collector |
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| CN109780130B (en) | 2021-01-15 |
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