CN104747649A - Magneto-rheological damper - Google Patents
Magneto-rheological damper Download PDFInfo
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- CN104747649A CN104747649A CN201510186272.XA CN201510186272A CN104747649A CN 104747649 A CN104747649 A CN 104747649A CN 201510186272 A CN201510186272 A CN 201510186272A CN 104747649 A CN104747649 A CN 104747649A
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- damper
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- end cap
- cylinder
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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
- F16F9/3207—Constructional features
- F16F9/3235—Constructional features of cylinders
- F16F9/3242—Constructional features of cylinders of cylinder ends, e.g. caps
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- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Vibration Prevention Devices (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention discloses a magneto-rheological damper. The magneto-rheological damper comprises a damping cylinder and a compensating cylinder which are connected vertically. The damping cylinder comprises an outer cylinder, wherein an inner cylinder is arranged in the outer cylinder, the outer wall of the inner cylinder is alternatively sleeved with magnet yoke rings and a permanent magnet ring; a magnet exciting coil winds in an annular groove formed by adjacent magnet yoke rings and the permanent magnet ring between them; the magnet yoke rings and the magnet exciting coil are externally and alternatively sleeved with flux sleeve rings and magnet isolating sleeve rings; an annular damping channel is formed among the flux sleeve rings, the magnet isolating sleeve rings, and the inner wall of the outer cylinder; the upper and lower end openings of the outer cylinder are equipped with upper and lower end covers, and the inner cylinder is provided with a damping piston for dividing a damping cavity inside into upper and lower cavities; the upper and lower cavities are interconnected with the damping channel. The compensating cylinder comprises a cylinder body, wherein the upper end opening of the cylinder body is connected with the lower end cover, and the lower end opening of the cylinder body is equipped with the end cover; a compensating cavity forms in the cylinder body, and the cylinder body is provided with a floating piston for dividing the compensating cavity into fluid and gas cavities; the fluid cavity is interconnected with the lower cavity. The magneto-rheological damper solves the contradiction of adjustable damping force and adjustable multiple of the existing magneto-rheological damper, and is especially applicable to half-active control of an impact vibrating system.
Description
Technical field
The present invention relates to a kind of MR damper for Structural Vibration Semi-active Control Technology, belong to Design of MR dampers field.
Background technique
MR damper is a kind of with intellectual material---magnetic flow liquid is working medium, the adjustable oscillation damping and energy dissipating device of damping force is realized by adding the viscosity of loaded magnetic field change magnetic flow liquid, mainly controllability is good, structure is simple, energy consumption is low for its outstanding feature, be the ideal component of implementation structure Semi-active Vibration Control, be widely used in every field at present.But in different applications, the operating conditions of MR damper also exists huge difference.Such as in the application such as civil engineering, medical treatment, the piston movement speed of MR damper is low, magnetic flow liquid is generally in low flow velocity state, the residence time long enough thus in induction channels, does not need to consider that the rheological response time of magnetic flow liquid is on the impact of damping force controllability.But for impact vibration system, as in the isolation mounting of the applications such as some engineering machinery, armament systems, Aero-Space, what MR damper suffered is high speed or impact load, the flow velocity of magnetic flow liquid is high, residence time in induction channels is extremely short, magnetic flow liquid even has little time that rheological effect fully occurs and is just rushed out induction channels, thus MR damper show as controllability decline even not controlled.Therefore, be applied to the requirement that the MR damper demand fulfillment of impact vibration system is more strict, harsh.
Existing MR damper as shown in Figure 1, it comprises cylinder body 11, slide in cylinder body 11 and be provided with piston 12, piston 12 one end is connected with piston rod 13, piston rod 13 stretches out from cylinder body 11 one end open, wherein: piston 12 comprises iron core 121, iron core 121 sidewall is arranged with at least one ring shape wire casing 122 (Figure 1 shows that the situation being designed with a ring shape wire casing 122), field coil 14 is wound with in each annular wire casing 122, field coil 14 is connected with automatical control system (not shown) through wire 16, field coil 14 and there is gap between iron core 121 and cylinder body 11 inwall, slit-shaped circularizes damp channel 15.At present, when existing MR damper is applied to the semi-active control of impact vibration system, there is following problem in it:
The first, adjustable multiple and damping-force adjustable contradiction.
Shown in Fig. 1, the damping force of typical MR damper can approximate representation be:
Formula 1) in, L
gthe total length of damp channel, L
g=L
p+ L
mr, L
mrthe total length of magnetic field induction part in damp channel, L
pthe total length without magnetic field induction part, R
mbe the mean radius of damp channel, h is the thickness of damp channel, A
pthe end face useful area of piston,
r
pthe radius of piston end surface, r
pthe radius of piston rod, in general, r
p< < R
p, so
v
dbe the speed of piston, η is the null field viscosity of magnetic flow liquid, τ
bit is the shear yield strength adding magnetic flow liquid after loaded magnetic field.
In formula 1) in, the first fraction is null field damping force, and be the non-adjustable part in damping force, the second fraction is damping-force adjustable, is the adjustable part in damping force.The ratio of damping-force adjustable and null field damping force is adjustable multiple.Damping-force adjustable and adjustable multiple weigh the performance of MR damper from different angles, are all the important evaluation indexes of MR damper.
By formula 1) adjustable multiple can be obtained be:
As can be seen from formula 2), outside damping-force adjustable is relevant to the performance of magnetic flow liquid with adjustable multiple, they are also by the impact of structural design.Wherein, raising induction channels length accounts for the ratio of whole damp channel length is from axis to improve the effective way of adjustable multiple.
The thickness h of damp channel is determined after needing to consider null field damping force and magnetic field, and general h gets 0.5mm ~ 3mm, increases h and is conducive to improving adjustable multiple, but is unfavorable for increasing damping-force adjustable.
For the typical MR damper shown in Fig. 1, R
m≈ R
p≈ R
c(R
ccylinder body radius), so can following formula be obtained:
From formula 1), 3), piston (or cylinder body) radius is larger, and the damping-force adjustable of MR damper is larger, but adjustable multiple is less.
As can be seen here, when structure based design regulates the adjustable multiple of MR damper typical shown in Fig. 1, damping-force adjustable, be conflicting between adjustable multiple and damping-force adjustable, unified adjustment cannot be implemented.
The second, the residence time of magnetic flow liquid in induction channels is too short, and the piston velocity limit that damping force is controlled and controllable damping force are difficult to the requirement simultaneously meeting high impact-resistant load.
The residence time t of magnetic flow liquid in induction channels
dcan following formula 4 be used) calculate:
Formula 4) in, l
mrthe length of one section of induction channels, u
mthe mean velocity of magnetic flow liquid in induction channels, mean velocity u
mcan by following formula 5) obtain:
For MR damper typical shown in Fig. 1, R
m≈ R
p,
so can obtain
The response time of magnetic flow liquid to magnetic field is generally 1ms ~ 2ms, if magnetic flow liquid is less than 2ms from entering to the time leaving one section of induction channels, then mean that magnetic flow liquid can not play rheological effect fully, there will be controllable damping force and decline, or even uncontrollable phenomenon.From formula 6), under the condition that other structural parameter are determined, the length increasing induction channels is the most direct method extending residence time, but the length of each section of induction channels is subject to the magnetic flux of magnetic circuit and magnetomotive restriction, can not blindly increase.And the multi-section type piston structure that prior art adopts usually can only increase the size of damping force, the residence time of magnetic flow liquid in each section of induction channels can not be extended.From formula 6) also, residence time and piston (or cylinder body) radius are inversely proportional to.This just means the mentality of designing based on typical MR damper, increase the radius of piston (or cylinder body), although can damping-force adjustable be increased, but be unfavorable for extending residence time, the controlled piston velocity limit of damping force is limited, and reduce the radius of piston (or cylinder body), be conducive to extending residence time, but may be difficult to provide enough damping-force adjustables.
In a word, for existing MR damper, piston (or cylinder body) radius produce affect in, damping-force adjustable and residence time are also contradiction, and ensure that sufficiently long residence time and enough large controllable damping force are the keys that MR damper is applied to impact vibration system simultaneously.
3rd, failure safety mechanism disappearance or imperfection.
Existing MR damper disappearance failure safety mechanism, or failure safety mechanism imperfection.Failure safety mechanism refers to when automatical control system breaks down, and MR damper still can provide certain damping force with the form of Normal hydraulic damper, guarantees that whole system is run safely.When MR damper is used for the semi-active control of structural vibration, in order to reach good control effects, its null field damping force be often less than original system be equipped with the damping force of damper, therefore the automatical control system of MR damper can bring bad consequence to the operation of system after breaking down.Visible, failure safety mechanism is particularly important for the application of MR damper in impact vibration system.If the MR damper in the isolation mounting of such as engineering machinery can not provide enough damping forces to be consumed by vibrational energy after automatical control system loses efficacy, the vibration of structure during equipment work, can be caused, thus reduce operating accuracy and the motion speed of equipment.
4th, anti-settling measure disappearance or imperfection.
Although magnetic flow liquid can add additive to the sedimentation suppressing ferromagnetic particle too early in preparation process, the density difference of ferromagnetic particle and base fluid is comparatively large, sedimentation still can occur after static a period of time and even harden.The as easy as rolling off a log blocking of bottom valve of existing double barreled MR damper, and because liquid does not form backflow bottom the cylinder barrel of single-cylinder type MR damper, the ferromagnetic particle of sedimentation not easily disperses again, even constantly can be tamped by piston.For impact vibration system, if magnetorheological fluid sedimentation hardens valve opening or damp channel blocking, then MR damper just can be approximately rigid device, and paroxysmal impulsive load can bring destructiveness to whole system, or even catastrophic consequence.
5th, piston axial dimension is large, limits the effective travel of piston.
In order to increase the damping-force adjustable of vibration damper, prior art adopts multi-section type piston structure usually.But for concrete equipment, the axial installing space of MR damper is often limited, and the piston of lengthening then means the effective travel will sacrificing damper, and this has been absorbed in again the contradiction of damping-force adjustable and effective travel.
As can be seen here, designing a kind of MR damper structure that can be used for impact vibration system semi-active control, is current urgent problem.
Summary of the invention
There are the problems referred to above to solve existing MR damper and be difficult to the present situation applied in impact vibration system, the invention provides a kind of MR damper that may be used for impact vibration system semi-active control, this MR damper of double barreled can improve damping-force adjustable and adjustable multiple simultaneously, and significantly can improve the controlled piston velocity limit of damping force, certain damping force still can be provided to ensure that impact vibration system is with the mode safe operation of passive damping when automatical control system breaks down, there is good anti-magnetic flow liquid settlement measurement, leave standstill even if long-time and also can normally work, damping piston does not obviously lengthen, do not affect the effective travel of MR damper.
To achieve these goals, present invention employs following technological scheme:
A kind of MR damper, it is characterized in that: it comprises damped cylinder, compensating cylinder is connected with bottom damped cylinder, wherein: damped cylinder comprises magnetic conduction urceolus, non-magnetic inner core is provided with in urceolus, inner tank theca is alternately arranged with magnet yoke ring, permanent-magnetic clamp, field coil is wound with in the circular groove that two neighbouring magnet yoke rings and the permanent-magnetic clamp between it are formed, magnet yoke ring and field coil are alternately arranged with the magnetic conduction collar outward, magnetic shield ring, the magnetic conduction collar, magnetic shield ring respectively with magnet yoke ring, the corresponding setting of field coil, the magnetic conduction collar and form annular damper passage between magnetic shield ring and outer tube inner wall, on urceolus, lower end mouth is separately installed with, lower end cap, on, lower end cap makes inner core fix and forms damping chamber in inner core and make the thickness of annular damper passage keep evenly, be provided with on damping chamber is divided in inner core, the damping piston of lower chambers, damping piston is connected with the piston rod stretching out upper end cap, on, lower chambers is respectively via the guiding gutter on upper end cap, guiding gutter on lower end cap and with annular damper channel connection, compensating cylinder comprises magnetic conduction cylindrical shell, cylindrical shell upper end-hole connects with lower end cap, and cylindrical shell lower end mouth installs end cap, compensates chamber to make to be formed in cylindrical shell, be provided with magnetic conduction floating piston compensation chamber being divided into liquid chamber, air chamber in cylindrical shell, the linked hole of liquid chamber on lower end cap is communicated with lower chambers.
Preferably, the top of described inner tank theca and bottom are described magnet yoke ring, and the height of the top and nethermost described magnet yoke ring is between 0.5 times ~ 1 times of magnet yoke ring height described in all the other.
Preferably, the height of the described magnetic conduction collar is greater than the height of described magnet yoke ring.
The upper and lower end of the described magnetic conduction collar, described magnetic shield ring is all processed with for the ledge structure of locating and assemble, wherein: ledge structure makes the described magnetic conduction collar be greater than not towards the side height of described annular damper passage towards the side height of described annular damper passage.
In actual design, described permanent-magnetic clamp axial charging, the polarity of two neighbouring described permanent-magnetic clamps is contrary; The current direction that two neighbouring described field coils pass into or direction of winding are on the contrary, contrary with the pole orientation making two neighbouring described field coils produce.
Preferably, described floating piston is provided with disk shaped recess towards the side of described lower end cap, is provided with permanent magnetism cake in groove.Described permanent magnetism cake axial charging.Described lower end cap is provided with towards the side of described floating piston the anti-bothrium of disc communicated with described linked hole.
Compare with existing MR damper, tool of the present invention has the following advantages:
1, MR damper of the present invention can increase damping-force adjustable and adjustable multiple simultaneously.
2, MR damper of the present invention is while increase damping-force adjustable and adjustable multiple, can extend the residence time of magnetic flow liquid in induction channels, thus increases the controlled piston velocity limit of damping force.
3, MR damper of the present invention has good Fail safe ability.
4, MR damper of the present invention can prevent magnetorheological fluid sedimentation from hardening effectively.
5, MR damper of the present invention has good reliability.
6, the consumption of MR damper of the present invention magnetic flow liquid used is few.
7, the effective travel of MR damper of the present invention is unaffected.
8, MR damper of the present invention is except can be used as traditional MR damper and using, and is specially adapted to the semi-active control of impact vibration system.
Accompanying drawing explanation
Fig. 1 is the structural representation of existing typical MR damper.
Fig. 2 is the structural representation of MR damper of the present invention.
Fig. 3 is the stereochemical structure enlarged diagram of upper end cap.
Embodiment
As shown in Figure 2, MR damper of the present invention comprises damped cylinder 20, the bottom of damped cylinder 20 is connected with compensating cylinder 30, wherein: damped cylinder 20 adopts single rod double barreled structure, damped cylinder 20 comprises the urceolus 21 of magnetic conduction, urceolus 21 adopts intensity good and the carbon steel of magnetic conduction or alloyed steel tubing are made, and the certain wall thickness required for the formation of flux loop, its wall thickness must consider magnetic flux, structural strength factor decides, non-magnetic inner core 22 is provided with in urceolus 21, inner core 22 adopts stainless steel or the good non-magnetic tubing of other intensity to make, and require that wall is thin, its wall thickness must consider that structural strength decides, inner core 22 outer wall is alternately arranged with magnet yoke ring 24, permanent-magnetic clamp 23, magnet yoke ring 24 is made for electrical pure iron material, two neighbouring magnet yoke rings 24 and the permanent-magnetic clamp between it 23 form circular groove, field coil 25 is wound with in circular groove, field coil 25 is connected with outside automatical control system via wire (not shown), and (laying of wire belongs to well known technology, therefore here do not describe in detail), magnet yoke ring 24 with field coil 25 periphery are alternately arranged with the magnetic conduction collar 26, magnetic shield ring 27, the magnetic conduction collar 26, magnetic shield ring 27 respectively with magnet yoke ring 24, the corresponding setting of field coil 25, as Fig. 2, for slight interference amount coordinates between the magnetic conduction collar 26 with magnet yoke ring 24, field coil 25 and the magnetic conduction collar 26, gap can be had between magnetic shield ring 27, the magnetic conduction collar 26 and form annular damper passage 53 between magnetic shield ring 27 periphery and urceolus 21 inwall, the thickness of annular damper passage 53 can between 0.5mm ~ 3mm, the magnetic conduction collar 26 is made for intensity good and the carbon steel of magnetic conduction or alloy steel material, magnetic shield ring 27 adopts copper, stainless steel or other non-magnetic metallic material are made, inner core 22 outer wall upper, lower end can be respectively equipped with the upper press ring 71 for compressing the parts that inner core 22 outer wall is installed, lower pressure ring 72, upper press ring 71 and lower pressure ring 72 adopt the non-magnetic metallic material such as stainless steel or copper to make, on, lower pressure ring 71, the angle, outer end of 72 can cut out and be beneficial to flow of fluid, reduce the larger chamfering (not marking in figure) along journey damping, urceolus 21 upper, lower end mouth is separately installed with upper end cap 28, lower end cap 29, on, lower end cap 28, 29 make inner core 22 fixing and form damping chamber in inner core 22 and annular damper passage 53 thickness keeps consistency, uniformity, damping piston 42 is installed in inner core 22, damping piston 42 slides along inner core 22 inwall, damping piston 42 can be provided with Decompression valves or one-way valve according to actual needs, on damping chamber is divided into by damping piston 42, lower chambers 51, 52, damping piston 42 is provided with the piston rod 41 stretching out upper end cap 28, namely piston rod 41 stretches out outside via the through hole 281 that upper end cap 28 is offered, damping piston 42 and piston rod 41 can be magnetic conduction or non-magnet material is made, upper chamber 51 is communicated with annular damper passage 53 via the guiding gutter 282 on upper end cap 28, lower chambers 52 is communicated with annular damper passage 53 via the guiding gutter 292 on lower end cap 29, guiding gutter 282, 292 reflux for guiding liquid to be formed between damping chamber and annular damper passage 53.The Volume Changes that compensating cylinder 30 causes at damping cavity indoor moving for compensating piston bar 41 and magnetic flow liquid expand with heat and contract with cold the Volume Changes caused.Compensating cylinder 30 comprises the cylindrical shell 31 of magnetic conduction, the upper end-hole of cylindrical shell 31 connects with lower end cap 29, the lower end mouth of cylindrical shell 31 is provided with end cap 32, compensate chamber to make to be formed in cylindrical shell 31, be provided with the floating piston 33 of magnetic conduction in cylindrical shell 31, floating piston 33 slides along cylindrical shell 31 inwall, compensation chamber is divided into liquid chamber 61, air chamber 62 by floating piston 33, liquid chamber 61 is positioned at top, and air chamber 62 is positioned at below, and the liquid chamber 61 being in top is communicated with lower chambers 52 via the linked hole 291 that lower end cap 29 is offered.
In actual design; upper end cap 28 can offer several guiding gutters 282; similarly; lower end cap 29 also can offer some guiding gutters 292; upper end cap 28, lower end cap 29 are designed with the step cutting pattern structure making to fix between inner core 22 and upper end cap 28, lower end cap 29, to guarantee the uniformity of annular damper passage 53 thickness.Fig. 3 shows the structure of upper end cap 28, upper end cap 28 is designed with ledge structure 283 and with the symmetrical guiding gutter 282 in axle center.Except anti-bothrium 293, the structure of lower end cap 29 is identical with upper end cap 28, therefore does not provide the structural drawing of lower end cap 29, please refer to upper end cap 28 and understands.
In the present invention, the effect of the magnetic conduction collar 26 and magnetic shield ring 27 has four: the first, and the magnetic conduction collar 26 for increasing the ratio of sensing part in annular damper passage 53, thus can increase adjustable multiple; The second, the magnetic conduction collar 26 and magnetic shield ring 27, for the protection of field coil 25 washing away and extruding from highly pressurised liquid, improve the reliability of MR damper of the present invention; 3rd, the outer profile size ratio of precision field coil 25 outer profile size precision of the magnetic conduction collar 26 and magnetic shield ring 27 wants high, therefore effectively can ensure that the damping force of different MR damper keeps good conformity; 4th, magnetic shield ring 27 avoids the magnetic line of force directly to form loop through self, but forces the magnetic line of force to pass annular damper passage 53 to form loop.
As Fig. 2, in actual design, preferably, the top of inner core 22 outer wall and bottom sheathed be magnet yoke ring 24, such design is to reach better magnetic conduction effect, and the height of the top and nethermost magnet yoke ring 24 is between 0.5 times ~ 1 times of all the other magnet yoke rings 24 height.
As Fig. 2, preferably, the height of the magnetic conduction collar 26 is greater than the height of magnet yoke ring 24, and namely magnet yoke ring 24 can cover by the magnetic conduction collar 26 completely, with the single hop induction channels that can be more grown.
As Fig. 2, the upper and lower end of the magnetic conduction collar 26, magnetic shield ring 27 can all be processed with for the ledge structure of locating and assemble, wherein: ledge structure makes the magnetic conduction collar 26 be greater than not towards the side height of annular damper passage 53 towards the side height of annular damper passage 53, like this, magnetic shield ring 27 is just less than not towards the side height of annular damper passage 53 towards the side height of annular damper passage 53, and such structural design is the ratio in order to increase sensing part in annular damper passage 53 as much as possible.
In actual design, permanent-magnetic clamp 23 is axial charging, and the polarity of two neighbouring permanent-magnetic clamps 23 is contrary.
In actual design, the current direction that two neighbouring field coils 25 pass into or direction of winding are on the contrary, contrary with the pole orientation making two neighbouring field coils 25 produce.
As Fig. 2, preferably, floating piston 33 is provided with disk shaped recess 34 towards the side of lower end cap 29, is provided with permanent magnetism cake 35 in groove 34, the effect of permanent magnetism cake 35 forms magnetic field in liquid chamber 61, after leaving standstill, sedimentation occurs harden to prevent the magnetic flow liquid in liquid chamber 61.
In actual design, permanent magnetism cake 35 is axial charging.
As Fig. 2, in actual design, preferably, lower end cap 29 is provided with the anti-bothrium 293 of the disc communicated with linked hole 291 towards the side of floating piston 33, and the effect of anti-bothrium 293 prevents the permanent magnetism cake 35 on floating piston 33 be directly adsorbed on lower end cap 29 and cause piston rod 41 to be difficult to push.
In the present invention, lower end cap 29 can be permeability magnetic material and makes, and upper end cap 28, end cap 32 can be magnetic conduction or non-magnet material is made.Lower end cap 29, cylindrical shell 31, floating piston 33 can adopt the carbon steel of magnetic conduction or alloy steel material to make, the magnetic flow liquid be so both conducive in liquid chamber 61 forms flux loop, prevent magnetorheological fluid sedimentation from hardening, the effect of shielding magnetic field can be played again, prevent permanent magnetism cake 35 magnetic line of force unstable in location free procedure from leaking to the normal work that damping chamber affects MR damper of the present invention, and prevent the magnetic line of force from leaking to the work of compensated cavity outdoor and interference other electronic equipment outside.
Each " highly " mentioned in the invention described above is in fig. 2 from the height viewed from vertical direction, can be described as axial height.
As Fig. 2, the working principle of MR damper of the present invention is:
When damping piston 42 is descending, piston rod 41 enters damping chamber, so the magnetic flow liquid in lower chambers 52 is pushed down.The guiding gutter 292 of major part magnetic flow liquid on lower end cap 29 enters in annular damper passage 53, and the guiding gutter 282 then on upper end cap 28 enters in upper chamber 51.In the present invention, piston rod 41 enters the Volume Changes that causes of damping cavity indoor and is moved downward (descending) to compensate by floating piston 33, then the linked hole 291 of another fraction magnetic flow liquid on lower end cap 29 enter compensated cavity liquid chamber 61 in realize compensation.
When damping piston 42 is up, compared with time descending with damping piston 42, the flow direction of magnetic flow liquid is contrary.Particularly, piston rod 41 moves upward, so the magnetic flow liquid in upper chamber 51 is pushed upwardly, the guiding gutter 282 on upper end cap 28 enters in annular damper passage 53, and the guiding gutter 292 then on lower end cap 29 enters in lower chambers 52.Simultaneously, due to piston rod 41 the Volume Changes that causes of damping cavity indoor by floating piston 33 move upward (up) compensate, so the linked hole 291 of the magnetic flow liquid in the liquid chamber 61 of compensated cavity on lower end cap 29 enters lower chambers 52 in realize compensation.
In use, no matter damping piston 42 is up or descending, the permanent-magnetic clamp 23 between magnet yoke ring 24 is all that annular damper passage 53 provides the foundation magnetic field, even if field coil 25 not loading current, MR damper of the present invention also can show as medium damping force.
When field coil 25 loads forward current, its magnetic field produced is identical with the magnetic direction that permanent-magnetic clamp 23 provides and superpose (Downward addition), so compared with during not loading current, the magnetic field at the magnetic flow liquid place in annular damper passage 53 is reinforced, magnetic flow liquid can magnetize further, and therefore MR damper of the present invention shows as increase damping force.If the forward current that field coil 25 passes into reaches forward lowest high-current value, then now MR damper of the present invention shows as maximum damping force.
On the contrary, when field coil 25 loads back current, the magnetic direction that its magnetic field produced and permanent-magnetic clamp 23 provide superposes (oppositely superposing) mutually on the contrary, so compared with during not loading current, the magnetic field at the magnetic flow liquid place in annular damper passage 53 is weakened, and therefore MR damper of the present invention shows as reduction damping force.If the back current that field coil 25 passes into reaches reverse lowest high-current value, then now MR damper of the present invention shows as minimum damping force.
In the present invention, define when the pole orientation that the field coil 25 of loading current produces is identical with the pole orientation that permanent-magnetic clamp 23 produces, the electric current that field coil 25 loads is forward current, on the contrary, when the pole orientation that the field coil 25 of loading current produces is contrary with the pole orientation that permanent-magnetic clamp 23 produces, the electric current that field coil 25 loads is back current.And, definition is when the magnetic field that the field coil 25 loading back current produces and the magnetic field that permanent-magnetic clamp 23 produces just in time cancel each other, the electric current that field coil 25 loads is reverse maximum current, and maximum (or specified) electric current that the value of the forward maximum current that field coil 25 loads can be born by field coil 25 wire used decides.
In the present invention, the introducing of permanent-magnetic clamp 23 makes MR damper of the present invention also can obtain medium damping force when not loading current, and by permanent-magnetic clamp 23 and field coil 25 produce magnetic field forward and reversely superpose the bidirectional modulation that can realize damping force (damping force increase, reduce), the magnetic field simultaneously produced due to permanent-magnetic clamp 23 can make the magnetic flow liquid in annular damper passage 53 be in sense state all the time, even if therefore permanent-magnetic clamp 23 also ensures MR damper of the present invention and leaves standstill for a long time and also there will not be magnetorheological fluid sedimentation to harden and the phenomenon that blocked by annular damper passage 53.
Further, compared with existing MR damper, tool of the present invention has the following advantages:
1, MR damper of the present invention can increase damping-force adjustable and adjustable multiple simultaneously.
MR damper of the present invention except axially except magnet yoke ring 24 sheathed concentrating flux sleeve ring 26 increase sensing part proportion in annular damper passage 53 (namely induction channels length accounts for the ratio of whole damp channel length), then come to increase outside damping-force adjustable and adjustable multiple simultaneously, also annular damper passage 53 and damping piston 42 are separated, the radius of annular damper passage 53 is no longer relied on or is no longer approximately equal to the radius of damping piston 42, but make the radius of annular damper passage 53 be greater than the radius of damping piston 42, therefore as can be seen from formula 2), so just can carry out the adjustable multiple of further increase by increasing the radius of damp channel 53 with the ratio of the radius of damping piston 42, and compared with typical MR damper, under the condition that damping piston 42 is identical with the radius of piston 12, the present invention can realize larger adjustable multiple, the present invention that Here it is breaks through the structural design thinking of existing MR damper, the theoretical foundation of adjustable multiple is increased from radial direction.
Thus, the present invention is based on structural design when adjustable multiple and damping-force adjustable are regulated, no longer conflicting between adjustable multiple and damping-force adjustable, but unified adjustment can be implemented.
In addition, present invention employs multi-section type magnetic structure scheme, have almost with the annular damper passage 53 of inner core 22 equal length, thus also increase effectively damping-force adjustable.
2, MR damper of the present invention is while increase damping-force adjustable and adjustable multiple, can extend the residence time of magnetic flow liquid in induction channels, thus increases the controlled piston velocity limit of damping force.
In the present invention, the height of the magnetic conduction collar 26 is greater than the height of magnet yoke ring 24, and therefore compared with existing MR damper, the present invention has longer single hop induction channels, so extend the residence time of magnetic flow liquid in induction channels in the axial direction.By formula 4), 5) can obtain:
Due to R
m> R
p, formula 7) value be obviously greater than formula 6) value, the present invention that Here it is extends the theoretical foundation of the residence time of magnetic flow liquid in induction channels from radial direction.
And can find out, the present invention is based on and to increase in annular damper passage 53 sensing part total length and proportion to while increasing damping-force adjustable and adjustable multiple, the adjustable multiple of further increase is carried out with the ratio of the radius of damping piston 42 by being separated with damping piston 42 by damp channel 53 and increasing the radius of damp channel 53, and achieve the prolongation of the residence time of magnetic flow liquid in induction channels, then achieve the increase of the controlled piston velocity limit of damping force.
3, MR damper of the present invention has good Fail safe ability.
The present invention introduces the permanent-magnetic clamp 23 identical with field coil 25 quantity in magnetic Circuit Design scheme, the electromagnetic field produced by the electric current controlling to pass in field coil 25 is superposed forward or backwards with the magnetic field that permanent-magnetic clamp 23 produces, and achieves the double-direction control to damping-force adjustable.The advantage introducing permanent-magnetic clamp 23 is, the inefficacy even if the automatical control system of MR damper of the present invention breaks down, permanent-magnetic clamp 23 also can provide certain magnetic field to make the magnetic flow liquid in annular damper passage 53 that stream change occur, MR damper of the present invention is made to provide damping force in the mode of passive damping device, ensure that the safe operation of whole system, this is most important for impact vibration system.
4, MR damper of the present invention can prevent magnetorheological fluid sedimentation from hardening effectively.
First, the permanent magnetism cake 35 that floating piston 33 is provided with can ensure that the magnetic flow liquid in liquid chamber 61 sedimentation can not occur, secondly, most magnetic lines of force of permanent-magnetic clamp 23 sheathed on inner core 22 can through magnet yoke ring 24, the magnetic conduction collar 26, annular damper passage 53, urceolus 21 and form closed flux loop, therefore it can ensure that the magnetic flow liquid in annular damper passage 53 can not sedimentation occur and be blocked by damp channel 53, simultaneously, the magnetic line of force that permanent-magnetic clamp 23 has an only a few can leak in the damping chamber in inner core 22 and form low-intensity magnetic field, thus the magnetic flow liquid generation sedimentation in damping chamber can be suppressed, even if there is slight sedimentation also not easily to harden, therefore in damping chamber, the magnetic flow liquid of slight sedimentation enters annular damper passage 53 Inner eycle via guiding gutter 282 or 292, the high magnetic fields of annular damper passage 53 thus can it be made to disperse again the magnetic flow liquid entered induction rapidly.It should be noted that effectively preventing magnetorheological fluid sedimentation from hardening is key MR damper of the present invention being applied to impact vibration system.
5, MR damper of the present invention has good reliability.
The field coil of existing typical MR damper generally adopts epoxy resin to encapsulate, and under the washing away and extrude of highly pressurised liquid, the easy strain cracking of epoxy resin layer, short circuit or open circuit very easily appear in field coil.And the present invention is arranged with concentrating flux sleeve ring 26 and magnetic shield ring 27 outside magnet yoke ring 24 and field coil 25; while increase damping-force adjustable and adjustable multiple; serve the good protection effect to field coil 25; make field coil 25 washing away from highly pressurised liquid, effectively improve the reliability of MR damper of the present invention.
6, the consumption of MR damper of the present invention magnetic flow liquid used is few.
The preparation cost of magnetic flow liquid is higher, if magnetic flow liquid consumption too much significantly will certainly increase the cost of MR damper.The present invention only need inject magnetic flow liquid consumption tradition little damper needed for suitable with inner core 22 bore, can realize the tradition large damper suitable with urceolus 21 bore and to be all beyond one's reach damping-force adjustable and adjustable multiple.
7, the effective travel of MR damper of the present invention is unaffected.
Magnetic circuit is not arranged on damping piston 42 by the present invention, but multi-section type magnetic structure has been arranged between inside and outside cylinder 22,21, compared with Normal hydraulic damper, the axial length of damping piston 42 of the present invention, without any increase, therefore ensure that the effective travel of MR damper of the present invention.
8, MR damper of the present invention is except can be used as traditional MR damper and using, and is specially adapted to the semi-active control of impact vibration system.Impact vibration system refers to have periodically or acyclic vibration source, and the vibration system that vibration velocity reaches higher value at short notice or alters a great deal, impact vibration system is well known system, therefore no longer describes in detail it.
The above know-why being preferred embodiment of the present invention and using; for a person skilled in the art; when not deviating from the spirit and scope of the present invention; any based on apparent changes such as the equivalent transformation on technical solution of the present invention basis, simple replacements, all belong within scope.
Claims (8)
1. a MR damper, it is characterized in that: it comprises damped cylinder, compensating cylinder is connected with bottom damped cylinder, wherein: damped cylinder comprises magnetic conduction urceolus, non-magnetic inner core is provided with in urceolus, inner tank theca is alternately arranged with magnet yoke ring, permanent-magnetic clamp, field coil is wound with in the circular groove that two neighbouring magnet yoke rings and the permanent-magnetic clamp between it are formed, magnet yoke ring and field coil are alternately arranged with the magnetic conduction collar outward, magnetic shield ring, the magnetic conduction collar, magnetic shield ring respectively with magnet yoke ring, the corresponding setting of field coil, the magnetic conduction collar and form annular damper passage between magnetic shield ring and outer tube inner wall, on urceolus, lower end mouth is separately installed with, lower end cap, on, lower end cap makes inner core fix and forms damping chamber in inner core and make the thickness of annular damper passage keep evenly, be provided with on damping chamber is divided in inner core, the damping piston of lower chambers, damping piston is connected with the piston rod stretching out upper end cap, on, lower chambers is respectively via the guiding gutter on upper end cap, guiding gutter on lower end cap and with annular damper channel connection, compensating cylinder comprises magnetic conduction cylindrical shell, cylindrical shell upper end-hole connects with lower end cap, and cylindrical shell lower end mouth installs end cap, compensates chamber to make to be formed in cylindrical shell, be provided with magnetic conduction floating piston compensation chamber being divided into liquid chamber, air chamber in cylindrical shell, the linked hole of liquid chamber on lower end cap is communicated with lower chambers.
2. MR damper as claimed in claim 1, is characterized in that:
The top of described inner tank theca and bottom are described magnet yoke ring, and the height of the top and nethermost described magnet yoke ring is between 0.5 times ~ 1 times of magnet yoke ring height described in all the other.
3. MR damper as claimed in claim 1 or 2, is characterized in that:
The height of the described magnetic conduction collar is greater than the height of described magnet yoke ring.
4. MR damper as claimed in claim 3, is characterized in that:
The upper and lower end of the described magnetic conduction collar, described magnetic shield ring is all processed with for the ledge structure of locating and assemble, wherein: ledge structure makes the described magnetic conduction collar be greater than not towards the side height of described annular damper passage towards the side height of described annular damper passage.
5. MR damper as claimed in claim 1, is characterized in that:
Described permanent-magnetic clamp axial charging, the polarity of two neighbouring described permanent-magnetic clamps is contrary;
The current direction that two neighbouring described field coils pass into or direction of winding are on the contrary, contrary with the pole orientation making two neighbouring described field coils produce.
6. MR damper as claimed in claim 1, is characterized in that:
Described floating piston is provided with disk shaped recess towards the side of described lower end cap, is provided with permanent magnetism cake in groove.
7. MR damper as claimed in claim 6, is characterized in that:
Described permanent magnetism cake axial charging.
8. MR damper as claimed in claim 6, is characterized in that:
Described lower end cap is provided with towards the side of described floating piston the anti-bothrium of disc communicated with described linked hole.
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Cited By (13)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963985A (en) * | 2015-07-08 | 2015-10-07 | 华东交通大学 | Magneto-rheological damper of integrated energy recovery device |
| CN105840718A (en) * | 2016-05-16 | 2016-08-10 | 中国人民解放军装甲兵工程学院 | Rapid optimal design method for magnetorheological damper |
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Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5632361A (en) * | 1994-09-16 | 1997-05-27 | Fichtel & Sachs Ag | Vibration damper, in particular for motor vehicles |
| US6279701B1 (en) * | 1999-09-13 | 2001-08-28 | Delphi Technologies, Inc. | Magnetorheological fluid damper with multiple annular flow gaps |
| US6419057B1 (en) * | 2001-01-12 | 2002-07-16 | Delphi Technologies, Inc. | Power-off damping in MR damper |
| CN1587738A (en) * | 2004-07-09 | 2005-03-02 | 北京工业大学 | Inverse type magnetic flow damper |
| EP1908985A1 (en) * | 2006-10-02 | 2008-04-09 | Delphi Technologies, Inc. | Twin-tube magnetorheological damper |
| CN101446117B (en) * | 2008-12-30 | 2010-10-27 | 河海大学 | High-energy consumption self-decoupling magnetorheological damper |
| CN103148159A (en) * | 2013-03-18 | 2013-06-12 | 中国人民解放军装甲兵工程学院 | Composite actuator and control method thereof |
| CN103511546A (en) * | 2013-10-22 | 2014-01-15 | 袁显举 | Automobile magneto-rheological absorber based on multistage circumferential flow mode |
| CN104100671A (en) * | 2014-07-04 | 2014-10-15 | 中国人民解放军装甲兵工程学院 | Magnetorheological damper having parallel normally-open holes and methods for calculating zero-field damping coefficient, on-field damping coefficient and damping force of magnetorheological damper |
| CN204253720U (en) * | 2014-11-20 | 2015-04-08 | 石家庄铁道大学 | External many circular holes damp channel MR damper |
| CN204553671U (en) * | 2015-04-20 | 2015-08-12 | 中国人民解放军装甲兵工程学院 | Double barreled MR damper |
-
2015
- 2015-04-20 CN CN201510186272.XA patent/CN104747649B/en active Active
Patent Citations (11)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5632361A (en) * | 1994-09-16 | 1997-05-27 | Fichtel & Sachs Ag | Vibration damper, in particular for motor vehicles |
| US6279701B1 (en) * | 1999-09-13 | 2001-08-28 | Delphi Technologies, Inc. | Magnetorheological fluid damper with multiple annular flow gaps |
| US6419057B1 (en) * | 2001-01-12 | 2002-07-16 | Delphi Technologies, Inc. | Power-off damping in MR damper |
| CN1587738A (en) * | 2004-07-09 | 2005-03-02 | 北京工业大学 | Inverse type magnetic flow damper |
| EP1908985A1 (en) * | 2006-10-02 | 2008-04-09 | Delphi Technologies, Inc. | Twin-tube magnetorheological damper |
| CN101446117B (en) * | 2008-12-30 | 2010-10-27 | 河海大学 | High-energy consumption self-decoupling magnetorheological damper |
| CN103148159A (en) * | 2013-03-18 | 2013-06-12 | 中国人民解放军装甲兵工程学院 | Composite actuator and control method thereof |
| CN103511546A (en) * | 2013-10-22 | 2014-01-15 | 袁显举 | Automobile magneto-rheological absorber based on multistage circumferential flow mode |
| CN104100671A (en) * | 2014-07-04 | 2014-10-15 | 中国人民解放军装甲兵工程学院 | Magnetorheological damper having parallel normally-open holes and methods for calculating zero-field damping coefficient, on-field damping coefficient and damping force of magnetorheological damper |
| CN204253720U (en) * | 2014-11-20 | 2015-04-08 | 石家庄铁道大学 | External many circular holes damp channel MR damper |
| CN204553671U (en) * | 2015-04-20 | 2015-08-12 | 中国人民解放军装甲兵工程学院 | Double barreled MR damper |
Cited By (21)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN104963985A (en) * | 2015-07-08 | 2015-10-07 | 华东交通大学 | Magneto-rheological damper of integrated energy recovery device |
| CN104963985B (en) * | 2015-07-08 | 2016-11-23 | 华东交通大学 | A kind of MR damper of integrated energy retracting device |
| CN105840718A (en) * | 2016-05-16 | 2016-08-10 | 中国人民解放军装甲兵工程学院 | Rapid optimal design method for magnetorheological damper |
| CN105840718B (en) * | 2016-05-16 | 2017-12-22 | 中国人民解放军装甲兵工程学院 | MR damper fast optimal design method |
| CN109965665A (en) * | 2017-12-27 | 2019-07-05 | 佛山市顺德区美的电热电器制造有限公司 | Cooking apparatus |
| CN108087482A (en) * | 2018-01-24 | 2018-05-29 | 华东交通大学 | A kind of sinuous formula MR damper of external multi-coil excitation |
| CN108518444A (en) * | 2018-03-22 | 2018-09-11 | 杭州电子科技大学 | Permanent magnet and the hybrid MR damper of magnet exciting coil and its damping adjusting method |
| CN108302152A (en) * | 2018-04-11 | 2018-07-20 | 华东交通大学 | A kind of MR damper with complicated liquid flowing channel structure |
| CN108302152B (en) * | 2018-04-11 | 2023-10-13 | 华东交通大学 | Magnetorheological damper with complex liquid flow channel structure |
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| CN108591345A (en) * | 2018-05-14 | 2018-09-28 | 西安交通大学 | A kind of highfield utilization rate MR damper of double barrel wall |
| CN108591345B (en) * | 2018-05-14 | 2020-01-10 | 西安交通大学 | Magnetorheological damper with double cylinder walls and high magnetic field utilization rate |
| CN109826903A (en) * | 2019-02-13 | 2019-05-31 | 杨泽达 | Set channel MR damper in a kind of bottom of band sedimentation Active dispersion devices |
| CN109826903B (en) * | 2019-02-13 | 2024-06-07 | 杨泽达 | Bottom channel magneto-rheological damper with sedimentation active dispersing device |
| CN109944896A (en) * | 2019-04-04 | 2019-06-28 | 四川大学 | A kind of self-adaptive current liquescent damper of self-induction power supply |
| CN110504079A (en) * | 2019-09-17 | 2019-11-26 | 杭州永迪电器器材厂 | A kind of retractable driving device of high frequency time |
| CN114412950A (en) * | 2021-12-13 | 2022-04-29 | 重庆大学 | Multistage excitation dual-cylinder magnetorheological damper and control method thereof |
| CN114412950B (en) * | 2021-12-13 | 2024-02-02 | 重庆大学 | Multistage excitation double-cylinder magnetorheological damper and control method thereof |
| CN114922931A (en) * | 2022-06-30 | 2022-08-19 | 上海蓝科建筑减震科技股份有限公司 | Damping coefficient adjustable double-order viscous damper |
| CN114922931B (en) * | 2022-06-30 | 2024-03-19 | 上海蓝科建筑减震科技股份有限公司 | Double-order viscous damper with adjustable damping coefficient |
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