CN104196949B - A kind of vibration damper based on magnetic fluid - Google Patents
A kind of vibration damper based on magnetic fluid Download PDFInfo
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- CN104196949B CN104196949B CN201410474853.9A CN201410474853A CN104196949B CN 104196949 B CN104196949 B CN 104196949B CN 201410474853 A CN201410474853 A CN 201410474853A CN 104196949 B CN104196949 B CN 104196949B
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Abstract
The present invention is a kind of vibration damper based on magnetic fluid, and the composition of described vibration damper comprises compression chamber and piston rod; Described compression chamber is made up of interior compression cavity case and external compression chamber enclosure, in the opening of interior compression cavity case compression cavity case outside, coaxial-symmetrical distributes, an identical ring permanent magnet is respectively equipped with in the bottom of interior compression cavity case and the outside of bottom, the permanent magnet on top is equipped with adjustable lever, adjustable lever and upwards extend lean out external compression chamber enclosure; Position between individual permanent magnet has throttling circular hole to interior compression cavity case; Spring fitting is in interior compression cavity case; The non magnetic annular baffle of welding one deck in compression cavity case outside, in cylindrical piston bar inserts in compression chamber.The present invention uses throttle orifice and throttle chink, belongs to thin wall small hole and goes out flow model, and the time that magnetic liquid flows through aperture and gap is shorter, achieves the damping to dither.
Description
Technical field
The invention belongs to liquid sticky type vibration damper, be specially a kind of vibration damper based on magnetic fluid.
Background technique
Existing single-cylinder type magnetorheological fluid shock absorber utilizes the pipe flow damping power of magnetic liquid to carry out damping, and its structure mainly comprises the compression chamber being full of magnetic flow liquid, and has the piston rod of throttling passage, and installs electromagnet around throttling passage.The visible patent CN201210449699 of this structure, when the external world applies vibrations, piston rod is forced to compress magnetic flow liquid motion, magnetic flow liquid is extruded and flows through the damp channel be in magnetic field, external magnetic field can increase the viscosity of magnetic flow liquid, makes to produce larger pipe flow damping power during magnetic current and liquid flow overdamping passage and realizes damping.
Existing single-cylinder type magnetorheological fluid shock absorber uses electromagnet generation externally-applied magnetic field to change magnetic flow liquid viscosity.Because the electric current reaching the magnetic field needs changing magnetic flow liquid viscosity is larger, this just makes the requirement of vibration damper to power supply higher, limits the use field of vibration damper.
Magnet spool operationally can produce a large amount of heat, changes the temperature of magnetic flow liquid, and then affects the viscosity of magnetic flow liquid, makes damping effect be difficult to control.
Single-barrel shock absorber uses magnetic flow liquid to be damping fluid, this just exists the settlement issues of magnetic flow liquid, the extreme influence reliability of vibration damper.For addressing this problem, often using more complicated shock absorber structure, needing in damping device, add magnetic flow liquid circulation means, maybe can play the special construction that magnetic flow liquid is circulated, this adds increased the design cost of vibration damper.
Existing single-cylinder type magnetorheological fluid shock absorber is due to its structural complexity, so many places seal point adopts contact seal.This sealing wear is large, heating is fast, seal low temperature fast without bi-directional sealing capabilities, packing grease consumption time harden increased wear, seal high temperature time snap_through.
The throttling passage that existing single-cylinder type magnetorheological fluid shock absorber uses is longer, and the time that magnetic flow liquid flows through passage is longer, makes vibration damper cannot to the damping of high-frequency vibration source.
Summary of the invention
In order to solve the above-mentioned shortcoming of existing magnetic fluid vibration damper, the present invention proposes a kind of novel magnetic fluid vibration damper, this vibration damper is made up of inside and outside compression chamber and the piston rod that is wrapped in permanent magnet.The feature that relates to of this vibration damper is: 1, and compression chamber uses inside and outside distribution; 2, use throttle orifice and baffle plate gap to replace throttling passage, the damping of high-frequency vibration can be realized; 3, use position is adjustable, and permanent magnet replaces electromagnet; 4 use magnetic fluid to replace magnetic flow liquid.Use position is adjustable, and permanent magnet replaces electromagnet, has broken away from the constraint of power supply, solves the problem of electromagnet coil heating.This external sealing place adopts magnet fluid sealing, reduces frictional loss.This vibration damper can be used as the damping to vibration component.On piston rod, permanent magnet is not only gap place magnetic fluid and provides magnetic field, can also form seal ring and play sealing effect, simplify the structure.
Technological scheme of the present invention:
Based on a vibration damper for magnetic fluid, the composition of described vibration damper comprises compression chamber and piston rod;
Described compression chamber is made up of interior compression cavity case and external compression chamber enclosure, and interior compression cavity case and external compression chamber enclosure are cylindrical shape, wherein airtight bottom external compression chamber enclosure, and the center at top has the circular open identical with interior compression chamber internal diameter; In the opening of interior compression cavity case compression cavity case outside, coaxial-symmetrical distributes, and interior compression cavity case is upper and lower penetrating, and upper end connects the edge of external compression chamber circular open and airtight, and lower end connects the bottom of external compression chamber enclosure;
An identical ring permanent magnet is respectively equipped with in the bottom of interior compression cavity case and the outside of bottom, and the permanent magnet on top is equipped with adjustable lever, adjustable lever and upwards extend lean out external compression chamber enclosure; Position between individual permanent magnet has throttling circular hole to interior compression cavity case;
Spring fitting, in interior compression cavity case, is connected with the bottom of external compression chamber enclosure; The non magnetic annular baffle of welding one deck in compression cavity case, has baffle plate gap between baffle plate and interior compression cavity case outside;
In piston rod inserts in compression chamber.
Be filled with magnetic fluid in compression chamber, wherein, be full of magnetic fluid in interior compression chamber, external compression top of chamber is that air forms air chamber, and the height of air chamber is 2 ~ 4 centimetres.
The magnetic fluid that described magnetic fluid is take tri-iron tetroxide as magnetic-particle, kerosene is carrier fluid, the percentage that magnetic-particle accounts for gross mass is 4 ~ 6%.
The diameter of described interior compression cavity case is 20% ~ 40% of external compression chamber enclosure diameter.
The height of described annular baffle position is 60% ~ 70% of external compression chamber height.
Described piston rod is made up of jointly rigid frame and hollow cylinder permanent magnet; Axisymmetric shape rigid frame longitudinal section is I-shaped, and upper and lower two ends are piston cap, and centre is piston axis, and hollow cylinder permanent magnet is enclosed within outside piston axis, and clamps fixing by upper and lower two piston caps; Hollow cylinder permanent magnet is that fan-shaped cylinder forms by eight pieces of cross sections, and permanent magnet prolongs radial magnetizing.
Beneficial effect of the present invention is: 1, the present invention adopts permanent magnet to provide magnetic field, does not need additional power source, solves the heating problem of electromagnet coil simultaneously, makes magnetic fluid can not be subject to the impact of temperature variation, improves the application of vibration damper.2, adjustable lever is equipped with in the present invention, can the position of up-down adjustment permanent magnet, and the power of controlling magnetic field realizes the adjustability of damping effect.3, because throttle pipe in existing magnetic fluid vibration damper is longer, the time that magnetohydrodynamic flow crosses throttle pipe is longer, causes vibration damper cannot to the damping of dither source.Throttle orifice and throttle chink is used in the present invention, belong to thin wall small hole and go out flow model, thickness due to aperture is 1/10 of throttling passage thickness, the time in magnetohydrodynamic flow small holes and gap is shorter than throttling passage, the damping frequency that vibration damper is suitable for improves an order of magnitude, achieves the damping to dither.4, the outer permanent magnet of piston rod can adsorb magnetic fluid formation seal ring, seals, reduce the loss rubbing and bring vibration damper to sealing place.5, the magnetic fluid that the present invention uses physical property more stable replaces magnetic flow liquid, solves the problem of magnetorheological fluid sedimentation.Use damping hole and flapper gap to produce damping force to magnetic fluid simultaneously, increase damping effect, solve the shortcoming that damping force that is that cause is little by magnetic fluid viscosity is little.6, structure of the present invention is simple, with low cost.
Accompanying drawing explanation
Fig. 1 is the overall structure figure of magnetic fluid vibration damper of the present invention;
Fig. 2 is the schematic diagram of compression chamber;
Fig. 3 is the piston rod schematic diagram being embedded with permanent magnet;
Fig. 4 is piston rod rigid frame schematic diagram;
Fig. 5 is permanent magnet magnetizing direction on piston rod;
Fig. 6 is the plotted curve that magnetic fluid viscosity changes with external magnetic field;
Wherein, 1-air chamber; 2-external compression chamber enclosure; Compression cavity case in 3-; 4-baffle plate; Compression chamber in 5-; 6-throttle orifice place permanent magnet; 7-adjustable lever; 8-external compression chamber; 9-baffle plate gap; 10-spring; 11-throttle orifice; 12-piston rod; Permanent magnet on 13-piston rod; 14-piston pole cap; 15-piston rod axis.
Specific embodiments
The present invention is based on the structure of the vibration damper of magnetic fluid as shown in Figure 1, the composition of described vibration damper comprises compression chamber and piston rod;
Described compression chamber is made up of interior compression cavity case 3 and external compression chamber enclosure 2, and interior compression cavity case 3 and external compression chamber enclosure 2 are cylindrical shape, wherein airtight bottom external compression chamber enclosure 2, and the center at top has the circular open identical with interior compression chamber 5 internal diameter; In the opening of interior compression cavity case 3 compression cavity case 2 outside, coaxial-symmetrical distributes, and interior compression cavity case 3 is upper and lower penetrating, and upper end connects the edge of the circular open of external compression chamber enclosure 2 and airtight, and lower end connects the bottom of external compression chamber enclosure 2; The longitudinal section of compression chamber as shown in Figure 2;
An identical ring permanent magnet 6 is respectively equipped with in the bottom of interior compression cavity case 3 and the outside of bottom, and the permanent magnet 6 on top is equipped with adjustable lever 7, and upwards extension leans out external compression chamber enclosure 2; Position between 2 permanent magnets 6 has throttling circular hole 11 to interior compression cavity case 3, and the quantity of throttling circular hole 11 is 3 rows;
Spring 10 is arranged in interior compression cavity case 3, is connected with the bottom of external compression chamber enclosure 2; The non magnetic annular baffle 4 of welding one deck in compression cavity case 2, has baffle plate gap 9 between baffle plate 4 and interior compression cavity case 3 outside;
The internal diameter 1mm longer than the diameter of cylindrical piston bar of interior compression chamber 5, in being inserted by cylindrical piston bar in compression chamber 5, cylindrical piston bar, by non magnetic rigid frame 12, forms with the Nd-Fe-B permanent magnet 13 being enclosed in outside.This framework 12 longitudinal section is I-shaped as Fig. 4, and it is by piston pole cap 14, and piston rod axis 15 forms; Hollow cylinder type permanent magnet 13, be that fan-shaped cylinder forms by eight pieces of identical cross sections, and be wrapped on piston rod axis 15, permanent magnet 13 prolongs radial magnetizing as shown in Figure 5; In the present invention, piston rod is known technology.
The thickness of annular baffle 4 is 3mm, and material is Austenitic Stainless Steel (nonmagnetic substance), and it is highly 60% ~ 70% of external compression chamber 8 height.
Be filled with magnetic fluid in compression chamber, wherein, be full of magnetic fluid in interior compression chamber 5, top, external compression chamber 8 is that air forms air chamber 1, and the height of air chamber 1 is 2 ~ 4 centimetres;
Described magnetic fluid is take tri-iron tetroxide as magnetic-particle, and kerosene is the magnetic fluid of carrier fluid, and the percentage that magnetic-particle accounts for gross mass is 5.8%.
The diameter of described interior compression cavity case 3 is 20% ~ 40% of external compression chamber enclosure 2 diameter.
The selection of spring heights and elasticity coefficient is relevant with by the quality of damping object, shockproofness, and the length of spring and the selection of elasticity coefficient should be guaranteed in shock absorbing process, and the bottom of piston rod can not higher than the level height of baffle plate 4.
In in the present invention, the rigid frame 12 of compression cavity case 3, external compression chamber enclosure 2, ring baffle 4 and piston rod uses non magnetic rigid material, such as Austenitic is nonmagnetic stainless steel.Permanent magnet 6,13 uses Nd-Fe-B permanent magnet, and the magnetizing direction of permanent magnet 6 magnetizes vertically, and permanent magnet 13 magnetizing direction is shown in Fig. 5.
The concrete data of the present embodiment vibration damper are: air chamber 1 is highly 2cm; External compression chamber enclosure 2 thickness is 1mm; Interior compression cavity case 3 thickness is 1mm; Baffle plate 4 thickness is 3mm, on the height and position of shell 13cm; Interior compression chamber 5 diameter 4cm, height 20cm; Throttle orifice place permanent magnet 6 internal diameter 4.1cm, external diameter 4.5cm, the height of the permanent magnet 6 of its middle and upper part is 3cm; External compression chamber 8 diameter 10cm, height 20cm; Baffle plate gap 9 width 3mm; Spring 10 is 10cm without length former time stressed, and radial length is 3.8cm, elasticity coefficient 100N/m.; Throttle orifice 11 diameter 2mm; The diameter 3.9cm of piston pole cap 14, thickness is 2mm; Piston rod axis 15 diameter 3.4cm; Permanent magnet 13 outer dia 3.9cm, inner diameter 3.4cm on piston rod;
The concave shape region that external compression chamber enclosure 2 and interior compression cavity case 3 surround is external compression chamber 8.Due to the special shape of shell 2,3, form the interior compression chamber 5 of upper end open simultaneously.Piston rod 12 being inserted interior compression chamber 5 makes it close.In interior compression chamber 5, be full of magnetic fluid, be filled with part magnetic fluid in external compression chamber 8, leave partial air and form air chamber 1, the height of air chamber 1 is 2cm.The external compression chamber enclosure 2 of magnetic fluid vibration damper and piston rod 12 are arranged on non-vibration component and vibration component place respectively, the magnetic fluid that (amplitude of vibration is no more than 6cm) piston rod can extrude in inner chamber 5 when there are vibrations enters exocoel 8 by throttle orifice 11, when magnetohydrodynamic flow crosses throttle orifice 11 with gap 9, the magnetic field that permanent magnet 6,13 produces can increase the viscosity of magnetic fluid, increase liquid discharge stream throttle orifice and the damping force suffered by gap, slow down the relative movement of compression chamber and piston rod, reach effectiveness in vibration suppression.In shock absorbing process, permanent magnet 13 can form seal ring with magnetic fluid, avoids magnetic fluid to reveal.Adjustable lever 7 can regulate the position of permanent magnet 6, and then adjusts flow damping power, realizes the adjustability of damping effect.After spring 10 and the air in air chamber 1 are compressed, for piston rod provides restoring force.
This vibration damper can be used as the damping to vibration component.It is embedded with the piston rod of permanent magnet as shown in Figure 3 by one, and inside and outside two non magnetic compression chamber compositions as shown in Figure 2.Interior compression chamber is used as the compression movement of piston rod, the throttle orifice that compression chamber inside and outside the spring of restoring force and several UNICOM is provided is had bottom interior compression chamber, and moveable permanent magnet is installed to increase the viscosity of magnetic fluid at throttle orifice place, simultaneously by regulating permanent magnet position, the magnetic field changing throttle orifice place realizes the adjustability of damping effect, use position is adjustable, and permanent magnet replaces electromagnet, has broken away from the constraint of power supply, solves the problem of electromagnet coil heating.External compression chamber is filled with magnetic fluid, and stay a certain amount of air (volume of air should be greater than vibratory source vibration amplitude and be multiplied by interior compression chamber cross-section area) formed air chamber be used as cushion and part restoring force be provided.A non magnetic baffle plate is also housed in external compression chamber, and there is certain interval with interior compression chamber outer wall, and in the region that permanent magnet shakes on the piston rod, the position of baffle plate.Piston rod is by rigid frame as Fig. 4, and permanent magnet such as Fig. 5 that annular radial magnetizes forms.
The present invention utilizes magnetic fluid to have this property of mobility of magnetic and liquid simultaneously, increases the viscosity of throttle orifice and gap place magnetic fluid, be subject to damping force, realize the damping to vibratory source when magnetohydrodynamic flow crosses throttle orifice and gap with permanent magnet field.Magnetic fluid under different magnetic field intensity, different rotating speeds viscosity B coefficent relation as shown in Figure 6, these data are drawn by NDG-5S rotary viscosity measuring.Because magnetic fluid belongs to non-Newtonian fluid, therefore its viscosity changes along with the change of liquid layer relative movement.In addition the viscosity of magnetic fluid is relevant with the size of externally-applied magnetic field.The rotating speed that this experiment use three kinds is different, measures the variation tendency that magnetic fluid viscosity increases with externally-applied magnetic field, confirms the variation relation that magnetic fluid viscosity increases with the increase of externally-applied magnetic field.From experiment, magnetic fluid viscosity increases along with the increase of externally-applied magnetic field, so the present invention can regulate magnetic fluid viscosity by the size changing externally-applied magnetic field, realizes the adjustability of damping effect.
Unaccomplished matter of the present invention is known technology.
Claims (6)
1., based on a vibration damper for magnetic fluid, the composition that it is characterized by this vibration damper comprises compression chamber and piston rod;
Described compression chamber is made up of interior compression cavity case and external compression chamber enclosure, and interior compression cavity case and external compression chamber enclosure are cylindrical shape, wherein airtight bottom external compression chamber enclosure, and the center at top has the circular open identical with interior compression chamber internal diameter; In the opening of interior compression cavity case compression cavity case outside, coaxial-symmetrical distributes, and interior compression cavity case is upper and lower penetrating, and upper end connects the edge of external compression chamber circular open and airtight, and lower end connects the bottom of external compression chamber enclosure;
An identical ring permanent magnet is respectively equipped with in the bottom of interior compression cavity case and the outside of bottom, and the permanent magnet on top is equipped with adjustable lever, adjustable lever and upwards extend lean out external compression chamber enclosure; Position between 2 ring permanent magnets has throttling circular hole to interior compression cavity case;
Spring fitting, in interior compression cavity case, is connected with the bottom of external compression chamber enclosure; The non magnetic annular baffle of welding one deck in compression cavity case, has baffle plate gap between baffle plate and interior compression cavity case outside;
In piston rod inserts in compression chamber.
2. as claimed in claim 1 based on the vibration damper of magnetic fluid, it is characterized by compression chamber and be filled with magnetic fluid, wherein, be full of magnetic fluid in interior compression chamber, external compression top of chamber is that air forms air chamber, and the height of air chamber is 2 ~ 4 centimetres.
3. as claimed in claim 1 based on the vibration damper of magnetic fluid, it is characterized by described magnetic fluid be take tri-iron tetroxide as magnetic-particle, the kerosene magnetic fluid that is carrier fluid, the percentage that magnetic-particle accounts for gross mass is 4 ~ 6%.
4., as claimed in claim 1 based on the vibration damper of magnetic fluid, the diameter that it is characterized by described interior compression cavity case is 20% ~ 40% of external compression chamber enclosure diameter.
5., as claimed in claim 1 based on the vibration damper of magnetic fluid, the height that it is characterized by described annular baffle position is 60% ~ 70% of external compression chamber height.
6., as claimed in claim 1 based on the vibration damper of magnetic fluid, it is characterized by described piston rod and be jointly made up of rigid frame and hollow cylinder permanent magnet; Axisymmetric shape rigid frame longitudinal section is I-shaped, and upper and lower two ends are piston cap, and centre is piston axis, and hollow cylinder permanent magnet is enclosed within outside piston axis, and clamps fixing by upper and lower two piston caps; Hollow cylinder permanent magnet is that fan-shaped cylinder forms by eight pieces of cross sections, and permanent magnet radially magnetizes.
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| CN201410474853.9A CN104196949B (en) | 2014-09-17 | 2014-09-17 | A kind of vibration damper based on magnetic fluid |
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| CN201410474853.9A CN104196949B (en) | 2014-09-17 | 2014-09-17 | A kind of vibration damper based on magnetic fluid |
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| CN104196949B true CN104196949B (en) | 2016-02-17 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN106499824B (en) * | 2017-01-09 | 2018-08-10 | 昆明理工大学 | A kind of reciprocating magnetic liquid self-circulation lubricating sealing device |
| CN109253203B (en) * | 2018-10-17 | 2020-08-14 | 常州大学 | High-frequency impact non-Newtonian fluid damper |
| CN111022542A (en) * | 2019-12-24 | 2020-04-17 | 河北工业大学 | Built-in steel ball tuning type magnetic liquid damping shock absorber |
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| CN1166875C (en) * | 2000-07-11 | 2004-09-15 | 株式会社三角工具加工 | Vibration damper using magnetic circuit |
| CN101832354A (en) * | 2010-01-19 | 2010-09-15 | 谭和平 | Single-output rod double-cylinder magneto-rheological damper |
| CN102162499A (en) * | 2011-03-04 | 2011-08-24 | 海尔集团公司 | Variable damping shock absorber and drum washing machine using shock absorber |
| US20120160622A1 (en) * | 2005-08-11 | 2012-06-28 | Eko Sport, Inc. | Magnetic valve for shock absorbers |
| US20130161138A1 (en) * | 2005-08-11 | 2013-06-27 | Eko Sport, Inc. | Valve for shock absorbers |
| CN204061700U (en) * | 2014-09-17 | 2014-12-31 | 河北工业大学 | A kind of vibration damper based on magnetic fluid |
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2014
- 2014-09-17 CN CN201410474853.9A patent/CN104196949B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1166875C (en) * | 2000-07-11 | 2004-09-15 | 株式会社三角工具加工 | Vibration damper using magnetic circuit |
| US20120160622A1 (en) * | 2005-08-11 | 2012-06-28 | Eko Sport, Inc. | Magnetic valve for shock absorbers |
| US20130161138A1 (en) * | 2005-08-11 | 2013-06-27 | Eko Sport, Inc. | Valve for shock absorbers |
| CN101832354A (en) * | 2010-01-19 | 2010-09-15 | 谭和平 | Single-output rod double-cylinder magneto-rheological damper |
| CN102162499A (en) * | 2011-03-04 | 2011-08-24 | 海尔集团公司 | Variable damping shock absorber and drum washing machine using shock absorber |
| CN204061700U (en) * | 2014-09-17 | 2014-12-31 | 河北工业大学 | A kind of vibration damper based on magnetic fluid |
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