CN106812859A - Double-spring magneto-rheological vibration damper - Google Patents
Double-spring magneto-rheological vibration damper Download PDFInfo
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- CN106812859A CN106812859A CN201710197688.0A CN201710197688A CN106812859A CN 106812859 A CN106812859 A CN 106812859A CN 201710197688 A CN201710197688 A CN 201710197688A CN 106812859 A CN106812859 A CN 106812859A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/53—Means for adjusting damping characteristics by varying fluid viscosity, e.g. electromagnetically
- F16F9/535—Magnetorheological [MR] fluid dampers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fluid-Damping Devices (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The present invention relates to Double-spring magneto-rheological vibration damper.Including two rigidity different spring, the coaxial inner cylinder body and outer cylinder body being set on piston rod, magnetic flow liquid is respectively equipped with inner cylinder body and outer cylinder body；Upper cover of piston rod in inner cylinder body is provided with interior magnet exciting coil and forms inner carrier；Outer magnet exciting coil is arranged with inner cylinder body periphery in outer cylinder body and forms outer piston；The periphery of outer cylinder body is connected to by vibration damping thing placing piece；Two springs of different-stiffness in the range of effective vibration damping, realize that the outer cylinder body is static with respect to inner cylinder body or occurs compared with thin tail sheep according to by vibration damping object and vibration source feature.Of the invention pair of rod structure, will not be formed it is under-voltage or work in-cylinder pressure it is unstable the problems such as；Processing technology of the invention is good；Installed using screw and connected, it is easy to I＆ M.
Description
Technical field
The invention belongs to vibration control technology field, can be used for the vibration isolation of object and vibration damping, the present invention relates to a kind of magnetic current
Become shock absorber.
Background technology
Magnetic flow liquid is the functional material that a kind of rheological behavior changes with changes of magnetic field, and its essential characteristic is：Without outer
Plus during magnetic fields, magnetic flow liquid is presented the Newtonian fluid state for flowing freely；In the case where being acted on by externally-applied magnetic field, magnetic flow liquid
Class solid-state can be transformed into by the good liquid of flow regime within the Millisecond time, its viscosity increases many numbers in very short time
Magnitude, shows viscoplastic fluid characteristic, and shows certain anti-shearing surrender ability, and shear yield stress is with additional magnetic
The increase of field intensity and increase.After magnetic field is removed, magnetic flow liquid is again by class Solid State Transformation into liquid, and this transformation is continuous, fast
It is fast, reversible, controllable.
It is one of vibration control technology study hotspot of rising in recent years with Control Method for MR Damper structural vibration, it is
One kind damping controllable devices, its internal resisting medium is magnetic flow liquid.The resistance of shock absorber of traditional form is immutable or hinders
Buddhist nun's variable range is smaller, and the damping of magneto-rheological vibration damper can carry out controllable variations on a large scale, and structure and control are all simpler
Single, so magneto-rheological vibration damper is with its safe and reliable and simple structure characteristic, the shock absorber for replacing traditional form is one new
Development trend.
Scientific instrument and equipment constantly develop towards high-grade, precision and advanced direction, either are still used to detect for the equipment processed
Instrument, their requirements to objective environment all more and more highers, wherein the requirement to the control of micro-vibration reached it is unprecedented
Height.Therefore, when this kind of instrument and equipment is designed and is used, harshness is proposed to micro-vibration control technology and is wanted
Ask.Refer to the mechanical oscillation or disturbance of low-level or low amplitude value on micro-vibration ordinary meaning, its vibration frequency range is arrived in 1Hz
Between 1kHz, in the sensitive equipments such as aircraft, the predominant oscillatory frequencies scope of micro-vibration is 0.1Hz to 300Hz.Typically by height
Regard High-frequency Interference as in the micro-vibration of 30Hz, the micro-vibration less than 30Hz regards low-frequency disturbance as.
At present, the magneto-rheological vibration damper that invention is used is divided into single rod magneto-rheological vibration damper and double rod magneto-rheological vibration dampings
Device, is mainly used in the large scale equipments such as automobile, steamer, building and large-amplitude vibration occasion, such magneto-rheological vibration damper
Size is big, and damp channel sectional area is big, and output damping force is big, is not suitable for small quality, small size by vibration damping object and micro- shakes
Rotating ring border.It is double go out pole magnetorheological damper piston rod stretched out from magnetic flow liquid cylinder body two ends, simple structure, without using compensation
Air bag, but the axial space that the motion of piston rod takes during due to work is larger, and magnetic current variable resistance is reduced to a certain extent
Buddhist nun's device impulse stroke.It is this kind of it is double go out double rod magneto-rheological vibration dampers for constituting together of pole magnetorheological damper and flexible member leading to
Minification is crossed to adapt to during micro-vibration environment, because micro-vibration vibration frequency is low, vibration amplitude is small, adds damp channel section
Product is small, and magneto-rheological vibration damper cannot provide enough damping forces and reach the purpose being controlled to micro-vibration.It is additionally, since this kind of
Double rod magneto-rheological vibration damper models are that damping element and flexible member are in parallel, and without variation rigidity characteristic, intrinsic frequency can not
To be changed, when micro-vibration control is carried out, the scope of application is limited by vibration source frequency.The present invention uses dual spring knot
Structure, when MR damper works, the deformation of spring can provide the elastic force of linear change, and two different-stiffness
The cooperation of spring can realize variation rigidity, reach the purpose of the intrinsic frequency for changing Double-spring magneto-rheological vibration damper, Ke Yishi
Now good effectiveness in vibration suppression, is particularly suitable for the control of micro-vibration.
The content of the invention
In order to solve the problems, such as that existing magneto-rheological vibration damper effectiveness in vibration suppression difference and magneto-rheological vibration damper during vibration damping exist
The problems such as can not changing without its power output under magnetic field or stationary magnetic field strength conditions, it is magnetorheological that the present invention provides a kind of Double-spring
Shock absorber.
Technical solution of the invention is as follows：
Double-spring magneto-rheological vibration damper include the different spring of two rigidity, it is coaxial be set on piston rod 12 it is closed interior
Magnetic flow liquid is respectively equipped with cylinder body 5 and closed outer cylinder body 6, inner cylinder body 5 and outer cylinder body 6；
The different spring of described two rigidity is small rigid spring 2 and big rigid spring 8；
Interior magnet exciting coil 15 is arranged with piston rod 12 in the inner cylinder body 5, inner carrier is formed；It is interior in the outer cylinder body 6
Outer magnet exciting coil 14 is arranged with cylinder body 5, outer piston is formed；Between the interior magnet exciting coil 15 and the inwall of the inner cylinder body 5
Annular throttling passage is formed, outer annular throttling passage is formed between the outer magnet exciting coil 14 and the inwall of the outer cylinder body 6；
The axial two ends of the inner cylinder body 5 are located at outside the axial two ends of the outer cylinder body 6；
The periphery of the outer cylinder body 6 is connected to by the axial connection end of vibration damping thing placing piece 10, described by vibration damping thing placing piece
The 10 axial other end is workbench, and the workbench is located at axial one end of outer cylinder body 6；
One end of the piston rod 12 is connected to piston joint element for bar 1, the piston joint element for bar 1 and corresponding outer cylinder body 6
Small rigid spring 2 is arranged with piston rod 12 between axial end face；The axial other end of the outer cylinder body 6 is connected to greatly
One end of rigid spring 8, the big rigid spring 8 is set on the axial overhanging end of corresponding inner cylinder body 5, big rigid spring 8
The other end be connected to inner cylinder body 5 axial overhanging end end face；
The spring of described two different-stiffness in the range of effective vibration damping, is realized described according to by vibration damping object and vibration source feature
The relatively described inner cylinder body 5 of outer cylinder body 6 is static or occurs compared with thin tail sheep.
The technical scheme for further limiting is as follows：
The first vibration damping scheme：Connector based on the piston joint element for bar 1；Inner casing in by vibration damping thing placing piece 10
One end of exntension tubs 11 is connected on the axial overhanging end of body 5, the other end of exntension tubs 11 is circular baffle plate 9；It is described big firm
Degree spring 8 is set on exntension tubs 11, and one end of big rigid spring 8 is connected to the second sealing of the axial end face of outer cylinder body 6
End cap 7, the other end of big rigid spring 8 is connected to baffle plate 9；The correspondence of small rigid spring 2 is located at by vibration damping thing placing piece 10
Installation end side；One end of small rigid spring 2 is connected to piston joint element for bar 1, and the other end is connected to the axially another of outer cylinder body 6
First end cover 4 of end face.
Second vibration damping scheme：It is connected to prolong on the axial overhanging end of the inner cylinder body 5 outside by vibration damping thing placing piece 10
One end of cylinder 11 is stretched, the other end of exntension tubs 11 is circular baffle plate 9；The big rigid spring 8 is set on exntension tubs 11, greatly
One end of rigid spring 8 is connected to the first end cover 4 of the axial end face of outer cylinder body 6, and the other end of big rigid spring 8 connects
Then baffle plate 9；Piston joint element for bar 1 and small rigid spring 2 correspondence on piston rod 12 is located at by vibration damping thing placing piece 10；It is small
One end of rigid spring 2 is connected to piston joint element for bar 1, and it is second close that the other end is connected to the axial other end of outer cylinder body 6
End-blocking lid 7.
Described is cylindrical tube shape by vibration damping thing placing piece 10, and its axial blind end is workbench, the axial other end
Connection end is fixedly connected the excircle of the outer cylinder body 6.
The radial width of the annular throttling passage and the outer annular throttling passage is 0.5-5mm.
Rigidity more than one times of the rigidity of the big rigid spring 8 more than small rigid spring 2.
To be slidingly sealed between the axial direction of the inner cylinder body 5 and outer cylinder body 6, the piston rod 10 and the inner cylinder body 5
It is to be slidingly sealed between axial direction.
The interior magnet exciting coil 15 and outer magnet exciting coil 14 are single-stage coil or multi-pole coils.
The interior magnet exciting coil 15 is by the fixed cover of inner splint 13 of ring-type on piston rod 12；The outer magnet exciting coil
14 are located on the excircle of the inner cylinder body 5 by the fixed cover of external splint 14 of ring-type.
The material of the inner splint 13 and external splint 14 is soft magnetic materials.
Advantageous Effects of the invention embody in the following areas：
1st, the present invention is overall in cylinder, processes economical good；Installed using screw and connected, it is easy to I＆ M.
2nd, the problems such as present invention is due to that using double rod structures, will not form under-voltage or unstable work in-cylinder pressure.
3rd, the present invention can realize variation rigidity, the mutative damp vibration-damping function of magneto-rheological vibration damper, by adjusting size of current
The rheological behavior of magnetic flow liquid can be changed, so as to change the damping of magneto-rheological vibration damper, output damping force size can be carried out
Stepless continuous are controlled, and output damping force excursion is big, it is easy to accomplish intelligentized control method.Due to using double-spring structure,
When MR damper works, the deformation of spring can provide the elastic force of linear change, and two springs of different-stiffness
Cooperation can realize variation rigidity.If the coefficient of elasticity of small rigid spring 2 is k1, the coefficient of elasticity of big rigid spring 8 is k2, then
Equivalent stiffness before change is k1, the equivalent stiffness after change can be similar to two springs series connection, equivalent stiffness is k1*k2/(k1+
k2), system stiffness can produce larger change.When the rigidity of big rigid spring is 2kN/m, the rigidity bullet of small rigid spring
When the rigidity of spring is 0.5kN/m, Single spring structure is compared to, system stiffness can produce the change of 1.6kN/m, be in load
5kg, in the case that the amplitude range of vibration source is ± 2mm interior, using the exciting form of frequency sweep, a certain size is passed through in magnet exciting coil
Electric current, when excited frequency is 20-50Hz, the present invention can reach good effectiveness in vibration suppression, by negative on vibration damping thing placing piece
The amplitude of load is ± 0.2mm or so.Therefore, the present invention can realize good effectiveness in vibration suppression in frequency domain wider, special
The control of micro-vibration is not applied to.
Brief description of the drawings
Fig. 1 is schematic perspective view of the present invention.
Fig. 2 is schematic structural view of the invention.
Fig. 3 is stereochemical structure sectional view of the present invention.
Fig. 4 is stereochemical structure sectional view of the present invention.
Fig. 5 is inner cylinder body and outer cylinder body confined state schematic diagram in Fig. 3 and Fig. 4.
Fig. 6 is working state schematic representation of the present invention.
Fig. 7 is present invention another kind working state schematic representation.
Fig. 8 is that big rigid spring and small rigid spring change second structural representation being located at.
Fig. 9 is the working state schematic representation of Fig. 8.
Sequence number in upper figure：1- pistons joint element for bar, the big rigid springs of 2-, the end covers of 4- first, 5- inner cylinder bodies, 6- outer shells
Body, the end covers of 7- second, the small rigid springs of 8-, 9- spring stops, 10- are by vibration damping thing placing piece, 11- exntension tubs, 12- pistons
Magnet exciting coil, 16- external splints in the outer magnet exciting coil of bar, 13- inner splints, 14-, 15-.
Specific embodiment
Below in conjunction with the accompanying drawings, the present invention is further described by embodiment.
Embodiment 1
Referring to Fig. 1 and Fig. 2, Double-spring magneto-rheological vibration damper includes the different spring of two rigidity, is coaxially set in piston rod
Magnetic flow liquid is respectively equipped with closed inner cylinder body 5 and closed outer cylinder body 6 on 12, inner cylinder body 5 and outer cylinder body 6.
Two different springs of rigidity are small rigid spring 2 and big rigid spring 8, and the rigidity of big rigid spring 8 is small firm
One times of degree spring 2.
Referring to Fig. 2, interior magnet exciting coil 15 is provided with by inner splint 13 on the piston rod 12 in inner cylinder body 5, forms interior living
Plug；Outer magnet exciting coil 14 is provided with by external splint 14 on inner cylinder body 5 in outer cylinder body 6, outer piston is formed.Interior magnet exciting coil 15
Single-stage coil is with outer magnet exciting coil 14, the material of inner splint 13 and external splint 14 is soft magnetic materials.Interior magnet exciting coil 15
Annular throttling passage is formed and the inwall of inner cylinder body 5 between, outer shroud is formed between outer magnet exciting coil 14 and the inwall of outer cylinder body 6
Shape throttling passage.The radial width of annular throttling passage and outer annular throttling passage is 2mm.The axial two ends position of inner cylinder body 5
Outside the axial two ends of outer cylinder body 6.Referring to Fig. 5, to be slidingly sealed between the axial direction of inner cylinder body 5 and outer cylinder body 6, piston rod 10
It is to be slidingly sealed and the axial direction of the inner cylinder body 5 between.
The periphery of outer cylinder body 6 is connected to
Cylindrical tube shape, its axial other end is workbench, and workbench is positioned at axial one end of outer cylinder body 6.
Referring to Fig. 3, the periphery of outer cylinder body 6 is connected to by the installation end of vibration damping thing placing piece 10, by vibration damping thing placing piece 10
Working end be located at the outer cylinder body 6 axial one end.
Referring to Fig. 3 and Fig. 4, one end of piston rod 12 is connected to piston joint element for bar 1, connects based on piston joint element for bar 1
Fitting；Small rigid spring is arranged with piston rod 12 between piston joint element for bar 1 and the axial end face of corresponding outer cylinder body 6
2；One end of small rigid spring 2 is connected to piston joint element for bar 1, and the other end is connected to the of the axial other end of outer cylinder body 6
One end cover 4.The one of exntension tubs 11 are connected on the axial overhanging end of the inner cylinder body 5 in by vibration damping thing placing piece 10
End, the other end of exntension tubs 11 is circular baffle plate 9；Big rigid spring 8 is set on exntension tubs 11, and the one of big rigid spring 8
End is connected to the second end cover 7 of the axial end face of outer cylinder body 6, and the other end of big rigid spring 8 is connected to baffle plate 9.
In the present embodiment, dynamic sealing uses U-shaped circle, static seal to use O-ring.
The operation principle of the present embodiment is described as follows：
Referring to Fig. 6, piston joint element for bar 1 is arranged on the basis of vibration source, is arranged on by vibration damping thing placing piece 10 by vibration damping object.
When the magnetic fields that interior magnet exciting coil 15 and outer magnet exciting coil 14 are produced are in magnetic flow liquid, annular throttling passage and outer annular
Magnetic flow liquid in throttling passage can occur magnetic rheology effect.
If the exciting force that the Double-spring magneto-rheological vibration damper of the present embodiment is subject to isf, the interior sealing end at the two ends of inner cylinder body 5
Force of sliding friction between lid 3 and piston rod 12 isf It is interior dynamic, the shear stress of magnetic flow liquid is in annular throttling passagef Interior magnetic, outward
First end cover 4 and the stiction between the second end cover 7 and the outer wall of inner cylinder 5 at the two ends of cylinder body 6 bef It is outer quiet, slip rubs
Wiping power isf It is outer dynamic, the shear stress of magnetic flow liquid is in outer annular throttling passagef Outer magnetic, the coefficient of elasticity of small rigid spring 2 is k1,
The deflection of small rigid spring 2 is x1, the coefficient of elasticity of big rigid spring 8 is k2, the deflection of big rigid spring 8 is x2。
1）When vibration source vibration is smaller,f≥f Interior magnetic+f It is interior dynamic, piston rod 12 moved with respect to inner cylinder 5, the deformation of small rigid spring 2
The power of generation is：f 1=k1*x1.Whenf 1≤f It is outer quiet+f Outer magneticWhen, only small rigid spring 2 is compressed, and small rigid spring 2 is not enough to gram
The frictional force and magnetorheological damping of the outer working cylinder of clothes are pushed dynamic outer cylinder body 6 and are moved, and now the equivalent stiffness of system is k1.Work as piston
When joint element for bar 1 vibrates together as vibration source is basic, interior magnet exciting coil 15 can be driven to move together, now annular throttling passage
Motion need to overcome the shear stress of magnetic flow liquid, consume partial vibration energy so that inner tube structure does not vibrate or shakes
Dynamic amplitude very little.
2）When vibration source excitation is larger, small rigid spring 2 is compressed, whenf 1≥f It is outer quiet+f Outer magneticWhen, small rigid spring 2 overcomes
The frictional force and magnetorheological damping of outer working cylinder are pushed dynamic outer cylinder body 6 and are moved, continue to compress big rigid spring 8, now system
Equivalent stiffness is k1*k2/(k1+k2).Because the rigidity of big rigid spring 8 is big, its deformation very little, so the motion bit of outer cylinder body 6
Also very little is moved, while the shear stress of the frictional force of outer working cylinder and magnetic flow liquid further consumes partial vibration energy, double bullets
Spring formula magneto-rheological vibration damper plays vibration damping purpose.
The Double-spring magneto-rheological vibration damper of the present embodiment has adjustable damping force, achievable passive control and half actively control
Processed the advantages of.When in a certain size vibration source amplitude range, the vibration amplitude by vibration damping object is zero or very little, it is possible to achieve
Good effectiveness in vibration suppression, is particularly well-suited to the control of micro-vibration.Damping force is produced using magnetic flow liquid so that the variable resistance of shock absorber
Buddhist nun's ability is strong, and damping size can be designed according to demand, applied widely.Double-spring magneto-rheological vibration damper of the invention is whole
Body is flat structure, for the shock absorber of existing use slim-lined construction design, with anti-beat ability higher, and can
To cause the first-order flexure modal frequency of shock absorber higher, the shadow of the oscillation crosswise to damping property of shock absorber is efficiently reduced
Ring, improve the effectiveness in vibration suppression of vibration reduction platform.
The Double-spring magneto-rheological vibration damper of the present embodiment, can be applied to camera head, micro Process platform, can also be applied to
The establishment of the micro-vibration control platform of aircraft, spacecraft etc..
Embodiment 2
Referring to Fig. 7, the present embodiment is that the Double-spring magneto-rheological vibration damper of embodiment 1 has been carried out into 180 ° to turn.
Piston joint element for bar 1 is arranged on the basis of vibration source, and vibration source basis is above, and placement is suspended by vibration damping object.
The Double-spring magneto-rheological vibration damper of the present embodiment can be applied to the establishment of the vibration reduction platform that need to enter vibration damping using sus-pension.Its
Similar to embodiment 1, its medium and small rigid spring 2 and big rigid spring 8 are extension spring to operation principle.The present embodiment can also reach
The purpose of vibration damping.
Embodiment 3
Referring to Fig. 8, the one of exntension tubs 11 are connected on the axial overhanging end of the inner cylinder body 5 outside by vibration damping thing placing piece 10
End, the other end of exntension tubs 11 is circular baffle plate 9.Big rigid spring 8 is sleeved on exntension tubs 11, and the one of big rigid spring 8
End is connected to the first end cover 4 of the axial end face of outer cylinder body 6, and the other end of big rigid spring 8 is connected to baffle plate 9.It is living
Piston joint element for bar 1 and small rigid spring 2 correspondence on stopper rod 12 is located at by vibration damping thing placing piece 10；Small rigid spring 2
One end is connected to piston joint element for bar 1, and the other end is connected to the second end cover 7 of the axial other end of outer cylinder body 6.It is small firm
Degree spring 2 and big rigid spring 8 are drawing-pressing spring.
Other structures are with embodiment 1.
Referring to Fig. 9, baffle plate 9 is arranged on the basis of vibration source, is arranged on by vibration damping thing placing piece 10 by vibration damping object.This reality
Apply an operation principle as follows：During work, the exciting force of vibration source directly can act on outer cylinder body 6 by big rigid spring 8, but by
Partial vibration energy is consumed in the frictional force of outer working cylinder and the shear stress of magnetic flow liquid, the amplitude of outer cylinder body 6 reduces；Together
When, outer cylinder body 6 is acted on by small rigid spring 2, and small rigid spring 2 can drive piston rod 12 to move by piston joint element for bar 1,
Because the frictional force of inner cylinder body 5 and the shear stress of magnetic flow liquid further consume partial vibration energy, so outer cylinder body 6 shakes
Width further reduces.The present embodiment can also reach the purpose of vibration damping.
Disclosed herein is only the preferred embodiments of the present invention, and this specification is chosen and specifically describes these embodiments, is
It is not limitation of the invention to preferably explain principle of the invention and practical application.Any those skilled in the art
The modifications and variations done in the range of specification, all should fall in the range of the present invention is protected.
Claims (10)
1. Double-spring magneto-rheological vibration damper, it is characterised in that：Including the different spring of two rigidity, coaxially it is set in piston rod
On closed inner cylinder body and closed outer cylinder body, be respectively equipped with magnetic flow liquid in inner cylinder body and outer cylinder body；
The different spring of described two rigidity is small rigid spring and big rigid spring；
Upper cover of piston rod in the inner cylinder body is provided with interior magnet exciting coil, forms inner carrier；On inner cylinder body in the outer cylinder body
Outer magnet exciting coil is arranged with, outer piston is formed；Annular section is formed between the interior magnet exciting coil and the inwall of the inner cylinder body
Circulation road, forms outer annular throttling passage between the outer magnet exciting coil and the inwall of the outer cylinder body；The axle of the inner cylinder body
It is located at outside the axial two ends of the outer cylinder body to two ends；
The periphery of the outer cylinder body is connected to by the axial connection end of vibration damping thing placing piece, the axle by vibration damping thing placing piece
It is workbench to the other end, the workbench is located at axial one end of outer cylinder body；
One end of the piston rod is connected to piston joint element for bar, the piston joint element for bar and axial the one of corresponding outer cylinder body
Upper cover of piston rod between end face is provided with small rigid spring；The axial other end of the outer cylinder body is connected to big rigid spring
One end, the big rigid spring is set on the axial overhanging end of corresponding inner cylinder body, and the other end of big rigid spring is connected to
The end face of the axial overhanging end of inner cylinder body；
The spring of described two different-stiffness in the range of effective vibration damping, is realized described according to by vibration damping object and vibration source feature
The relatively described inner cylinder body of outer cylinder body is static or occurs compared with thin tail sheep.
2. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The piston joint element for bar is base
Plinth connector；One end of exntension tubs, exntension tubs are connected on the axial overhanging end of the inner cylinder body in by vibration damping thing placing piece
The other end be circular baffle plate；The big rigid spring is set on exntension tubs, and one end of big rigid spring is connected to outer shell
Second end cover of the axial end face of body, the other end of big rigid spring is connected to baffle plate；
The small rigid spring correspondence is located at by the installation end side of vibration damping thing placing piece；One end of small rigid spring is connected to live
Stopper rod connector, the other end is connected to the first end cover of the axial other end of outer cylinder body.
3. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：Outside by vibration damping thing placing piece
Inner cylinder body axial overhanging end on be connected to one end of exntension tubs, the other end of exntension tubs is circular baffle plate；It is described big firm
Degree spring is set on exntension tubs, and one end of big rigid spring is connected to the first end cover of the axial end face of outer cylinder body,
The other end of big rigid spring is connected to baffle plate；
Piston joint element for bar on piston rod is corresponding with small rigid spring positioned at by vibration damping thing placing piece；The one of small rigid spring
End is connected to piston joint element for bar, and the other end is connected to the second end cover of the axial other end of outer cylinder body.
4. the Double-spring magneto-rheological vibration damper according to claim 1 or 2 or 3, it is characterised in that：It is described to be put by vibration damping thing
Part is put for cylindrical tube shape, its axial blind end is workbench, and the connection end of the axial other end is fixedly connected the outer shell
The excircle of body.
5. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The annular throttling passage and
The radial width of the outer annular throttling passage is 0.5-5mm.
6. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The rigidity of the big rigid spring
More than more than one times of the rigidity of small rigid spring.
7. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The inner cylinder body and outer cylinder body
It is to be slidingly sealed to be slidingly sealed between axial direction, between the axial direction of the piston rod and the inner cylinder body.
8. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The interior magnet exciting coil and encourage outward
Magnetic coil is single-stage coil or multi-pole coils.
9. Double-spring magneto-rheological vibration damper according to claim 1, it is characterised in that：The interior magnet exciting coil passes through ring
The inner splint fixed cover of shape is on piston rod；The outer magnet exciting coil is located at the inner casing by the external splint fixed cover of ring-type
On the excircle of body.
10. Double-spring magneto-rheological vibration damper according to claim 9, it is characterised in that：The inner splint and external splint
Material be soft magnetic materials.
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| CN201710197688.0A CN106812859B (en) | 2017-03-29 | 2017-03-29 | Double-spring magneto-rheological vibration damper |
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| CN201710197688.0A CN106812859B (en) | 2017-03-29 | 2017-03-29 | Double-spring magneto-rheological vibration damper |
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| CN106812859B CN106812859B (en) | 2018-11-23 |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
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| CN113216437A (en) * | 2021-06-02 | 2021-08-06 | 郑州大学 | Novel assembled building shock attenuation device |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN107956837A (en) * | 2017-11-15 | 2018-04-24 | 深圳市科比特航空科技有限公司 | Unmanned machine head damping device |
| CN107956837B (en) * | 2017-11-15 | 2024-03-19 | 深圳市科比特航空科技有限公司 | Unmanned aerial vehicle cloud platform damping device |
| CN109899437A (en) * | 2017-12-07 | 2019-06-18 | 陕西汽车集团有限责任公司 | Vibration energy regeneration type magneto-rheological vibration damper |
| CN109899437B (en) * | 2017-12-07 | 2024-03-05 | 陕西汽车集团股份有限公司 | Vibration energy recovery type magneto-rheological damper |
| CN112188379A (en) * | 2020-09-29 | 2021-01-05 | 杭州黎铙电器有限公司 | Sound detection device utilizing magnetorheological fluid |
| CN113216437A (en) * | 2021-06-02 | 2021-08-06 | 郑州大学 | Novel assembled building shock attenuation device |
| CN113216437B (en) * | 2021-06-02 | 2022-05-17 | 郑州大学 | Assembled building damping device |
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