CN104196949A - Magnetofluid-based shock absorber - Google Patents
Magnetofluid-based shock absorber Download PDFInfo
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- CN104196949A CN104196949A CN201410474853.9A CN201410474853A CN104196949A CN 104196949 A CN104196949 A CN 104196949A CN 201410474853 A CN201410474853 A CN 201410474853A CN 104196949 A CN104196949 A CN 104196949A
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- compression chamber
- compression cavity
- magnetic fluid
- permanent magnet
- cavity case
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Abstract
The invention relates to a magnetofluid-based shock absorber comprising a compression cavity and a piston rod. The compression cavity is composed of an inner compression cavity shell and an outer compression cavity shell; the inner compression cavity shell is arranged in an opening of the outer compression cavity shell; the inner compression cavity shell and the outer compression cavity shell are coaxially and symmetrically distributed; the outside of each of the lower portion and bottom of the inner compression cavity shell is provided with a circular permanent magnet; the circular permanent magnets are identical; an adjusting rod is mounted on the upper one of the permanent magnets; the adjusting rod extends up out of the outer compression cavity shell; the inner compression cavity shell is provided with a throttle round orifice between the permanent magnets ; a spring is mounted within the inner compression cavity shell; a nonmagnetic circular retainer plate is welded inside the outer compression cavity shell; the piston rod in a cylindrical shape is inserted into the inner compression cavity. The magnetofluid-based shock absorber with the throttle orifice and a throttle gap is a thin-walled pored outflow model; magnetofluid flows through a pore and the throttle gap in a shorter time, and high-frequency vibration is absorbed.
Description
Technical field
The invention belongs to liquid viscosity 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 that is full of magnetic flow liquid, and has the piston rod of throttling passage, and electromagnet is installed around throttling passage.The visible patent CN201210449699 of this structure, when the external world applies vibrations, force the motion of piston rod compression magnetic flow liquid, magnetic flow liquid is extruded and flows through the damp channel being in magnetic field, external magnetic field can increase the viscosity of magnetic flow liquid, produces larger pipe flow damping power and realize damping while making magnetic current and liquid flow overdamping passage.
Existing single-cylinder type magnetorheological fluid shock absorber produces externally-applied magnetic field with electromagnet and changes magnetic flow liquid viscosity.Owing to reaching, to change the current ratio that the magnetic field of magnetic flow liquid viscosity needs larger, and this just makes vibration damper to the having relatively high expectations of power supply, and has limited the use field of vibration damper.
Magnet spool can produce a large amount of heat in the time of work, changes the temperature of magnetic flow liquid, and then affects the viscosity of magnetic flow liquid, makes damping effect be difficult to control.
What single-barrel shock absorber used is that magnetic flow liquid is damping fluid, and this just exists the settlement issues of magnetic flow liquid, has greatly affected the reliability of vibration damper.For addressing this problem, often use more complicated shock absorber structure, need in damping device, add magnetic flow liquid circulation means, maybe can play the special construction that makes magnetic flow liquid circulation, this has just 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.Snap_through when this sealing wear is large, sclerosis adds galling, seal high temperature while generating heat fast, unparalleled, seal low temperature fast to sealability, packing grease consumption.
The throttling passage that existing single-cylinder type magnetorheological fluid shock absorber uses is longer, and it is longer that magnetic flow liquid flows through time of passage, makes the vibration damper cannot be 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 what compression chamber used is inside and outside distribution; 2, use throttle orifice and baffle plate gap to replace throttling passage, can realize the damping of high-frequency vibration; 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, has solved the problem of electromagnet coil heating.This external sealing place adopts magnet fluid sealing, has reduced frictional loss.This vibration damper can be used as the damping to vibration component.On piston rod, permanent magnet, not only for gap place magnetic fluid provides magnetic field, can also form seal ring and play sealing effect, simplifies 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 cylindric, and wherein external compression chamber enclosure bottom is airtight, and the center at top has the circular open identical with interior compression chamber internal diameter; Interior compression cavity case is outside in the opening of compression cavity case, and 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 airtight, and lower end connects the bottom of external compression chamber enclosure;
An identical ring permanent magnet is respectively equipped with the outside of bottom in the bottom of interior compression cavity case, on the permanent magnet on top, adjustable lever is housed, and adjustable lever also upwards extends and leans out external compression chamber enclosure; Interior compression cavity case has throttling circular hole on the position between individual permanent magnet;
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;
Piston rod inserts in interior compression chamber.
In compression chamber, be filled with magnetic fluid, wherein, in interior compression chamber, be full of magnetic fluid, external compression top of chamber is that air forms air chamber, and the height of air chamber is 2～4 centimetres.
Described magnetic fluid be taking tri-iron tetroxide as magnetic-particle, kerosene is the magnetic fluid of 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 cross sections, and permanent magnet prolongs radial magnetizing.
Beneficial effect of the present invention is: 1, the present invention adopts permanent magnet that magnetic field is provided, and does not need additional power source, has solved the heating problem of electromagnet coil simultaneously, makes magnetic fluid can not be subject to the impact of temperature variation, has improved the application of vibration damper.2, adjustable lever is equipped with in the present invention, position that can 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, it is longer that it's time of throttle pipe is past magnetohydrodynamic flow, causes the vibration damper cannot be to the damping of dither source.In the present invention, use throttle orifice and throttle chink, belong to thin wall small hole and go out flow model, because the thickness of aperture is 1/10 of throttling passage thickness, the time in magnetohydrodynamic flow small holes and gap is shorter than throttling passage, make the applicable damping frequency of vibration damper improve an order of magnitude, realized the damping to dither.4, the outer permanent magnet of piston rod can adsorb magnetic fluid formation seal ring, and sealing place is sealed, and has reduced the loss that friction brings vibration damper.5, the present invention uses the magnetic fluid that physical property is more stable to replace magnetic flow liquid, has solved the problem of magnetorheological fluid sedimentation.Use damping hole and baffle plate gap to produce damping force to magnetic fluid simultaneously, increase damping effect, solved by the little shortcoming of magnetic fluid viscosity damping force little and that cause.6, the present invention is simple in structure, with low cost.
Brief description of the drawings
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 that is 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 magnetic fluid vibration damper structure 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 cylindric, and wherein external compression chamber enclosure 2 bottoms are airtight, and the center at top has the circular open identical with interior compression chamber 5 internal diameters; Interior compression cavity case 3 is outside in the opening of compression cavity case 2, and coaxial-symmetrical distributes, and interior compression cavity case 3 is upper and lower penetrating, and upper end connects the edge of circular open of external compression chamber enclosure 2 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 the outside of bottom in the bottom of interior compression cavity case 3, on the permanent magnet 6 on top, adjustable lever 7 is housed, and upwards extends and lean out external compression chamber enclosure 2; Interior compression cavity case 3 has throttling circular hole 11 on the position between 2 permanent magnets 6, 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 the interior welding one deck of compression cavity case 2, has baffle plate gap 9 between baffle plate 4 and interior compression cavity case 3 outside;
The internal diameter of interior compression chamber 5 is than the long 1mm of the diameter of cylindrical piston bar, and in cylindrical piston bar is inserted, in compression chamber 5, cylindrical piston bar, by non magnetic rigid frame 12, forms with the Nd-Fe-B permanent magnet 13 that is enclosed in outside.These framework 12 longitudinal sections are I-shaped as Fig. 4, and it is by piston pole cap 14, and piston rod axis 15 forms; Hollow cylindrical magnet iron 13, is that fan-shaped cylinder forms by eight identical cross sections, and is 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.
In compression chamber, be filled with magnetic fluid, wherein, in interior compression chamber 5, be full of magnetic fluid, 8 tops, external compression chamber are that air forms air chamber 1, and the height of air chamber 1 is 2～4 centimetres;
Described magnetic fluid is taking tri-iron tetroxide as magnetic-particle, the magnetic fluid that kerosene is 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 diameters.
Spring height and the selection of elasticity coefficient be with relevant by the quality of damping object, shockproofness, and the length of spring and the selection of elasticity coefficient should guarantee in damping process, and the bottom of piston rod can not be higher than the level height of baffle plate 4.
What in the present invention, the rigid frame 12 of compression cavity case 3, external compression chamber enclosure 2, ring baffle 4 and piston rod used is non magnetic rigid material, for example 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 directions are 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 are 1mm; Interior compression cavity case 3 thickness are 1mm; Baffle plate 4 thickness are 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 former length when stressed is 10cm, 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 on piston rod, inner diameter 3.4cm;
External compression chamber enclosure 2 is external compression chamber 8 with the concave shape region that interior compression cavity case 3 surrounds.Due to the special shape of shell 2,3, form the interior compression chamber 5 of upper end open simultaneously.Piston rod 12 is inserted to interior compression chamber 5 and make its sealing.In interior compression chamber 5, be full of magnetic fluid, be filled with part magnetic fluid in external compression chamber 8, leave part 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 respectively to non-vibration component and vibration component place, the magnetic fluid that (amplitude of vibration is no more than 6cm) piston rod can push in inner chamber 5 in the time there are vibrations enters exocoel 8 by throttle orifice 11, in the time that magnetohydrodynamic flow is crossed throttle orifice 11 with gap 9, the magnetic field that permanent magnet 6,13 produces can increase the viscosity of magnetic fluid, increase the suffered damping force in liquid discharge stream throttle orifice and gap, slow down the relative movement of compression chamber and piston rod, reach effectiveness in vibration suppression.In damping 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 is compressed with the air in air chamber 1, for piston rod provides restoring force.
This vibration damper can be used as the damping to vibration component.It by a piston rod that is embedded with permanent magnet as shown in Figure 3, and inside and outside two non magnetic compression chambers form as shown in Figure 2.Interior compression chamber is as the compression movement of piston rod, there is the throttle orifice that compression chamber inside and outside the spring of restoring force and several UNICOM is provided in interior compression chamber bottom, and the viscosity of permanent magnet being movably installed increasing magnetic fluid at throttle orifice place, simultaneously by regulating permanent magnet position, the adjustability of damping effect is realized in the magnetic field that changes throttle orifice place, use position is adjustable, and permanent magnet replaces electromagnet, has broken away from the constraint of power supply, has solved the problem of electromagnet coil heating.External compression chamber is filled with magnetic fluid, and leaves 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) formation air chamber as cushioning and provide part restoring force.A non magnetic baffle plate is also housed in external compression chamber, and has certain interval with interior compression chamber outer wall, and the position of baffle plate is in the region of permanent magnet vibrations on piston rod.Piston rod is by rigid frame as Fig. 4, and the permanent magnet that magnetizes of annular radial forms as Fig. 5.
The present invention utilizes magnetic fluid to have this property of mobility of magnetic and liquid simultaneously, by the viscosity of permanent magnet field increase throttle orifice and gap place magnetic fluid, is subject to damping force in the time that magnetohydrodynamic flow is crossed throttle orifice and gap, realizes the damping to vibratory source.Magnetic fluid under different magnetic field intensity, different rotating speeds viscosity variation 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 variation of liquid layer relative movement.In addition the viscosity of magnetic fluid is relevant with the size of externally-applied magnetic field.This experiment is used three kinds of different rotating speeds, measures the variation tendency that magnetic fluid viscosity increases with externally-applied magnetic field, has confirmed 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 that changes externally-applied magnetic field, realizes the adjustability of damping effect.
Unaccomplished matter of the present invention is known technology.
Claims (6)
1. the vibration damper based on 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 cylindric, and wherein external compression chamber enclosure bottom is airtight, and the center at top has the circular open identical with interior compression chamber internal diameter; Interior compression cavity case is outside in the opening of compression cavity case, and 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 airtight, and lower end connects the bottom of external compression chamber enclosure;
An identical ring permanent magnet is respectively equipped with the outside of bottom in the bottom of interior compression cavity case, on the permanent magnet on top, adjustable lever is housed, and adjustable lever also upwards extends and leans out external compression chamber enclosure; Interior compression cavity case has throttling circular hole on the position between 2 ring permanent magnets;
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;
Piston rod inserts in interior compression chamber.
2. the vibration damper based on magnetic fluid as claimed in claim 1, is characterized by compression chamber and is filled with magnetic fluid, wherein, in interior compression chamber, is full of magnetic fluid, and external compression top of chamber is that air forms air chamber, and the height of air chamber is 2～4 centimetres.
3. the vibration damper based on magnetic fluid as claimed in claim 1, is characterized by described magnetic fluid and is taking tri-iron tetroxide as magnetic-particle, kerosene is the magnetic fluid of carrier fluid, and the percentage that magnetic-particle accounts for gross mass is 4～6%.
4. the vibration damper based on magnetic fluid as claimed in claim 1, the diameter that it is characterized by described interior compression cavity case is 20% ~ 40% of external compression chamber enclosure diameter.
5. the vibration damper based on magnetic fluid as claimed in claim 1, the height that it is characterized by described annular baffle position is 60% ~ 70% of external compression chamber height.
6. the vibration damper based on magnetic fluid as claimed in claim 1, is characterized by described piston rod and is 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 cross sections, and permanent magnet prolongs radial magnetizing.
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| Application Number | Priority Date | Filing Date | Title |
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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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| Application Number | Priority Date | Filing Date | Title |
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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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| CN104196949A true CN104196949A (en) | 2014-12-10 |
| CN104196949B CN104196949B (en) | 2016-02-17 |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106499824A (en) * | 2017-01-09 | 2017-03-15 | 昆明理工大学 | A kind of reciprocating magnetic liquid self-circulation lubricating sealing device |
| CN109253203A (en) * | 2018-10-17 | 2019-01-22 | 常州大学 | A kind of high-frequency percussion non-newtonian fluid damper |
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| 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 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN106499824A (en) * | 2017-01-09 | 2017-03-15 | 昆明理工大学 | A kind of reciprocating magnetic liquid self-circulation lubricating sealing device |
| CN109253203A (en) * | 2018-10-17 | 2019-01-22 | 常州大学 | A kind of high-frequency percussion non-newtonian fluid damper |
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| Publication number | Publication date |
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| CN104196949B (en) | 2016-02-17 |
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