CN102182785A - Magnetic steel piston type magneto-rheological damper with double ejection rods - Google Patents
Magnetic steel piston type magneto-rheological damper with double ejection rods Download PDFInfo
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- CN102182785A CN102182785A CN 201110065164 CN201110065164A CN102182785A CN 102182785 A CN102182785 A CN 102182785A CN 201110065164 CN201110065164 CN 201110065164 CN 201110065164 A CN201110065164 A CN 201110065164A CN 102182785 A CN102182785 A CN 102182785A
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Abstract
The invention discloses a magnetic steel piston type magneto-rheological damper with double ejection rods, comprising a working cylinder, a piston and two piston rods; the working cylinder is filled with magneto-rheological fluid; the piston is made of magnetic steel, two piston rods are both made of non-magnetic materials, a magnet exciting coil and a magnetizing-demagnetizing coil are wound in the middle of the piston, and the magnetic steel piston can be magnetized and demagnetized by controlling a power source, therefore, the magnetic steel piston has certain magnetic field intensity and the magnetic steel piston type magneto-rheological damper with double ejection rods has certain output damping force, and the output damping force of the magnetic steel piston type magneto-rheological damper with double ejection rods is regulated by changing the size and the direction of current input to the magnet exciting coil of the magnetic steel piston.
Description
Technical field
The invention belongs to a kind of MR damper, be specifically related to a kind of pair of rod magnet steel piston magneto-rheological damper.
Background technique
Different with single outstretch pole magnetorheological damper is that the damping force that two outstretch pole magnetorheological dampers are exported is symmetrical, simultaneously, the size of the damping force of common double outstretch pole magnetorheological damper output can be carried out remote stepless by the control power supply and be regulated, but this adjusting is to need consumed power at any time, and, when the common double outstretch pole magnetorheological damper is zero (that is: field current is zero) at the control electric power outputting current, because of the magnetic intensity in the gap between piston and clutch release slave cylinder is zero, the viscosity of the magnetic flow liquid in the gap is minimum and damping force is less, so, in case control power supply or piston field coil break down, because of the less proper functioning that is difficult to the system that guarantees of damping force of common double outstretch pole magnetorheological damper output.
Summary of the invention
For overcoming existing two outstretch pole magnetorheological damper less and bigger deficiency of power consumption of damping force when field current is zero, the present invention proposes a kind of pair of rod magnet steel piston magneto-rheological damper, the magnet steel piston of two rod magnet steel piston magneto-rheological dampers can utilize the control power supply by filling degaussion coil it is magnetized or demagnetizing at any time, therefore, at first can make the magnet steel piston reach predetermined work magnetic intensity, and then regulate the control power supply and output on the magnet steel piston size and Orientation of electric current in the field coil, just make the direction of the electromagnetic field that field coil produces and size is consistent with the magnetic field of magnet steel piston or on the contrary, that is: reach the purpose that the size of two rod magnet steel piston magneto-rheological damper output damping forces is controlled by the magnetic intensity that strengthens or weaken the magnet steel piston, since the magnet steel piston magnetize or demagnetize after reached near predetermined work magnetic intensity or the predetermined work magnetic intensity, therefore, required electric energy of further adjusting to its output damping force will reduce and energy-conservation greatly, in addition, since the magnet steel piston magnetize or demagnetize after had certain work magnetic intensity, so, in case control power supply or piston field coil break down, the damping force of two rod magnet steel piston magneto-rheological damper outputs still can guarantee the proper functioning of system.Therefore, two rod magnet steel piston magneto-rheological dampers have the advantage of the energy-saving safe of conveniently controlling of common double outstretch pole magnetorheological damper and permanent magnet type magnetic current variable damper simultaneously.
The technical solution adopted in the present invention is as follows:
A kind of pair of rod magnet steel piston magneto-rheological damper, it comprises clutch release slave cylinder, piston, two piston rods, in clutch release slave cylinder, be full of magnetic flow liquid, described piston is made of magnet steel, be wound with field coil and fill degaussion coil at the piston middle part, piston rod is made of non-magnet_conductible material, and wherein there is through hole at a piston rod center, and the field coil at piston middle part and the guide line that fills degaussion coil are drawn by the central through bore of a piston rod wherein.
Function of the present invention is achieved in that at first utilizes the control power supply that the degaussion coil that fills at magnet steel piston middle part is switched on, make the work magnetic intensity of magnet steel piston by magnetizing or demagnetizing and reach predetermined, like this, when magnet steel piston field coil no electric circuit, magnet steel piston with work magnetic intensity will produce certain magnetic field on the gap of piston external diameter and clutch release slave cylinder internal diameter, the viscosity of the magnetic flow liquid in the gap is uprised, when piston rod drive magnet steel piston moves in clutch release slave cylinder, will under predetermined work damping force, move; When magnet steel piston field coil feeds forward current, when the electromagnetic field that magnet steel piston field coil energising back is produced is consistent with the magnetic direction of magnet steel piston, this will make the magnetic intensity in magnet steel piston external diameter and the clutch release slave cylinder internal diameter gap higher, the viscosity of the magnetic flow liquid in the gap is higher, when piston rod drive magnet steel piston moves, will be subjected to bigger damping force in clutch release slave cylinder; When magnet steel piston field coil feeds back current, when the electromagnetic field that is produced after magnet steel piston field coil is switched on is opposite with the magnetic direction of magnet steel piston, this will make the magnetic intensity in piston external diameter and the clutch release slave cylinder internal diameter gap reduce, the viscosity of the magnetic flow liquid in the gap descends, when piston rod drive magnet steel piston moves, will be subjected to less damping force in clutch release slave cylinder; When magnet steel piston field coil feeds back current, when the electromagnetic field that is produced after magnet steel piston field coil is switched on is opposite with the magnetic field equal and opposite in direction of magnet steel piston and direction, to make magnetic intensity in magnet steel piston external diameter and the clutch release slave cylinder internal diameter gap drop to minimum like this and during near zero magnetic field, the viscosity minimum of the magnetic flow liquid in the gap, when piston rod drive magnet steel piston moves, will be subjected to minimal damping power in clutch release slave cylinder; Therefore, compare with the common double outstretch pole magnetorheological damper, since the magnet steel piston of two rod magnet steel piston magneto-rheological dampers through magnetizing or demagnetize after reached near predetermined work magnetic intensity or the predetermined work magnetic intensity, it is energy-conservation so the control power supply exports to it that damping force regulates that required electric energy will reduce greatly by field coil on the magnet steel piston, simultaneously, because of utilizing the control power supply that the magnet steel piston is magnetized at any time or demagnetizing operation, make the magnet steel piston have certain magnetic intensity, even control power supply or magnet steel piston field coil breaks down like this, can guarantee that also the damping force of two rod magnet steel piston magneto-rheological dampers outputs can keep the proper functioning of system.
Description of drawings
Fig. 1 is a kind of structural representation of the present invention, and N among the figure and S are the magnetic direction of magnet steel piston after magnetizing.
Fig. 2 is the present invention when work, the schematic representation that concerns of input current and output damping force, and the F among the figure is a damping force, I is an electric current.
Fig. 3 and Fig. 4 are the present invention when work, the schematic representation that concerns of the input current of magnet steel piston when being filled with different magnetic field intensity and output damping force.
Fig. 5 is an another kind of structural representation of the present invention, and the magnet steel piston is fixed on the two ends of cylindrical magnet steel 16 by soft iron ring 17 and soft iron ring 18 and constitutes.
Embodiment
Describe structure of the present invention in detail below in conjunction with accompanying drawing:
Referring to Fig. 1, this is a kind of concrete structure of the present invention, and it comprises clutch release slave cylinder 3, piston 5, piston rod 9 and piston rod 2; Piston 5 is made of magnet steel, be wound with field coil 6 at magnet steel piston 5 middle parts and fill degaussion coil 14, field coil 6 and fill the guide line 11 of degaussion coil 14 and guide line 15 is drawn the back from piston rod 9 central through bores 10 and joined with control power supply 13, magnet steel piston 5 is installed in the clutch release slave cylinder 3, the external diameter of magnet steel piston 5 is less than the internal diameter of clutch release slave cylinder 3 and leave magnetic flow liquid 4 flow gap 12, the two ends that piston rod 9 that is made of non-magnet_conductible material and piston rod 2 are separately fixed at magnet steel piston 5, the other end of piston rod 9 and piston rod 2 seal ring 7 by clutch release slave cylinder 3 end faces and bearing 8 and seal ring 1 and bearing 14 respectively stretches out from the two ends of clutch release slave cylinder 3, is full of magnetic flow liquid 4 in clutch release slave cylinder 3.
At first utilize control power supply 13 to magnetize or demagnetize by the 14 pairs of magnet steel pistons 5 of degaussion coil that fill at magnet steel piston 5 middle parts, make magnet steel piston 5 reach predetermined work magnetic intensity, like this when controlling power supply 13 not to magnet steel piston field coil 6 output currents, the magnet steel piston 5 that is filled with certain magnetic field will produce certain magnetic field on the gap 12 of magnet steel piston 5 external diameters and clutch release slave cylinder 3 internal diameters, the viscosity of the magnetic flow liquid 4 in the gap 12 is uprised, when piston rod 9 drive magnet steel pistons 5 move in clutch release slave cylinder 3, the work damping force that will be scheduled to, i.e. F0 among Fig. 2.
When control power supply 13 is exported forward currents to magnet steel piston field coil 6, when making the direction in electromagnetic field that magnet steel piston field coil 6 produced and magnet steel piston 5 magnetic fields consistent, this will make the magnetic intensity in magnet steel piston 5 external diameters and the clutch release slave cylinder 3 internal diameter gaps higher, the viscosity of the magnetic flow liquid 4 in the gap is higher, when piston rod 9 drive magnet steel pistons 5 move in clutch release slave cylinder 3, will be subjected to bigger damping force, i.e. F0 to F2 line segment among Fig. 2;
When control power supply 13 is exported back currents to magnet steel piston field coil 6, when making the direction in electromagnetic field that magnet steel piston field coil 6 produced and magnet steel piston 5 magnetic fields opposite, this will make the magnetic intensity in magnet steel piston 5 external diameters and the clutch release slave cylinder 3 internal diameter gaps 12 reduce, the viscosity of the magnetic flow liquid 4 in the gap 12 descends, when piston rod 9 drive magnet steel pistons 5 move in clutch release slave cylinder 3, will be subjected to less damping force, i.e. F0 to F1 line segment among Fig. 2;
When control power supply 13 is given magnet steel piston field coil 6 output back currents, when making the magnetic field equal and opposite in direction of electromagnetic field that energising piston field coil 6 produced and magnet steel piston 5 and direction opposite, in the time of will making magnet steel piston 5 external diameters and clutch release slave cylinder 3 internal diameter gaps 12 interior magnetic intensities reduce so also near zero magnetic field, the viscosity minimum of the magnetic flow liquid in the gap 12, when piston rod 9 drive magnet steel pistons 5 move in clutch release slave cylinder 3, will be subjected to minimal damping power, i.e. F1 among Fig. 2.
Claims (2)
1. two rod magnet steel piston magneto-rheological damper, it comprises clutch release slave cylinder, piston, two piston rods, in clutch release slave cylinder, be full of magnetic flow liquid, it is characterized in that: described piston is made of magnet steel, be wound with field coil and fill degaussion coil at the piston middle part, described two piston rods are made of non-magnet_conductible material, and wherein there is through hole at a piston rod center.
2. a kind of pair of rod magnet steel piston magneto-rheological damper as claimed in claim 1 is characterized in that: the field coil at described piston middle part and the guide line that fills degaussion coil are drawn by piston rod central through bore wherein.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110065164 CN102182785A (en) | 2011-03-18 | 2011-03-18 | Magnetic steel piston type magneto-rheological damper with double ejection rods |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201110065164 CN102182785A (en) | 2011-03-18 | 2011-03-18 | Magnetic steel piston type magneto-rheological damper with double ejection rods |
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| Publication Number | Publication Date |
|---|---|
| CN102182785A true CN102182785A (en) | 2011-09-14 |
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| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201110065164 Pending CN102182785A (en) | 2011-03-18 | 2011-03-18 | Magnetic steel piston type magneto-rheological damper with double ejection rods |
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| CN (1) | CN102182785A (en) |
Cited By (7)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102788110A (en) * | 2012-08-17 | 2012-11-21 | 上海应用技术学院 | Dual-rod magnetorheological fluid damper and seal structure thereof |
| CN103075459A (en) * | 2013-01-28 | 2013-05-01 | 中国矿业大学 | Double-ejection rod ring magnetic steel piston magnetorheological damper |
| CN103089889A (en) * | 2011-11-03 | 2013-05-08 | 长春孔辉汽车科技有限公司 | Magneto-rheological pump type variable-damping shock absorber |
| CN105715731A (en) * | 2016-03-31 | 2016-06-29 | 华中科技大学 | Two-freedom-degree shearing type magnetorheological fluid damper |
| CN112923001A (en) * | 2021-01-29 | 2021-06-08 | 中国劳动关系学院 | Circumferential excitation magnetorheological damper |
| CN111005968B (en) * | 2018-10-05 | 2021-08-24 | 本田技研工业株式会社 | Mounting bushing |
| CN114198451A (en) * | 2021-12-15 | 2022-03-18 | 中国船舶重工集团公司第七0九研究所 | Controllable limiting damping support rod and use method thereof |
Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6497309B1 (en) * | 2001-08-13 | 2002-12-24 | Delphi Technologies, Inc. | Magneto-rheological damper with an external coil |
| CN1587738A (en) * | 2004-07-09 | 2005-03-02 | 北京工业大学 | Inverse type magnetic flow damper |
| CN1601139A (en) * | 2003-09-25 | 2005-03-30 | 欧进萍 | Internal air chamber type damper as a magnetic current variable flow body with dual out poles |
| CN201627871U (en) * | 2010-03-30 | 2010-11-10 | 谭和平 | Double-ejector rod self-adaptation double-control magnetic current damper |
| CN202007856U (en) * | 2011-03-18 | 2011-10-12 | 谭晓婧 | Double-rod magnetic steel piston type magneto-rheological damper |
-
2011
- 2011-03-18 CN CN 201110065164 patent/CN102182785A/en active Pending
Patent Citations (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US6497309B1 (en) * | 2001-08-13 | 2002-12-24 | Delphi Technologies, Inc. | Magneto-rheological damper with an external coil |
| CN1601139A (en) * | 2003-09-25 | 2005-03-30 | 欧进萍 | Internal air chamber type damper as a magnetic current variable flow body with dual out poles |
| CN1587738A (en) * | 2004-07-09 | 2005-03-02 | 北京工业大学 | Inverse type magnetic flow damper |
| CN201627871U (en) * | 2010-03-30 | 2010-11-10 | 谭和平 | Double-ejector rod self-adaptation double-control magnetic current damper |
| CN202007856U (en) * | 2011-03-18 | 2011-10-12 | 谭晓婧 | Double-rod magnetic steel piston type magneto-rheological damper |
Cited By (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103089889A (en) * | 2011-11-03 | 2013-05-08 | 长春孔辉汽车科技有限公司 | Magneto-rheological pump type variable-damping shock absorber |
| CN103089889B (en) * | 2011-11-03 | 2016-01-20 | 长春孔辉汽车科技股份有限公司 | A kind of magnetorheological pump type mutative damp vibration damper |
| CN102788110A (en) * | 2012-08-17 | 2012-11-21 | 上海应用技术学院 | Dual-rod magnetorheological fluid damper and seal structure thereof |
| CN102788110B (en) * | 2012-08-17 | 2015-03-04 | 上海应用技术学院 | Seal structure of dual-rod magnetorheological fluid damper |
| CN103075459A (en) * | 2013-01-28 | 2013-05-01 | 中国矿业大学 | Double-ejection rod ring magnetic steel piston magnetorheological damper |
| CN103075459B (en) * | 2013-01-28 | 2015-05-27 | 中国矿业大学 | Double-ejection rod ring magnetic steel piston magnetorheological damper |
| CN105715731A (en) * | 2016-03-31 | 2016-06-29 | 华中科技大学 | Two-freedom-degree shearing type magnetorheological fluid damper |
| CN111005968B (en) * | 2018-10-05 | 2021-08-24 | 本田技研工业株式会社 | Mounting bushing |
| US11221052B2 (en) | 2018-10-05 | 2022-01-11 | Honda Motor Co., Ltd. | Mount bush |
| CN112923001A (en) * | 2021-01-29 | 2021-06-08 | 中国劳动关系学院 | Circumferential excitation magnetorheological damper |
| CN114198451A (en) * | 2021-12-15 | 2022-03-18 | 中国船舶重工集团公司第七0九研究所 | Controllable limiting damping support rod and use method thereof |
| CN114198451B (en) * | 2021-12-15 | 2024-03-22 | 中国船舶重工集团公司第七0九研究所 | Using method of controllable limiting damping stay bar |
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Application publication date: 20110914 |