CN115143224B - Magnetorheological damper with low zero-field damping force and wide damping adjustable range - Google Patents
Magnetorheological damper with low zero-field damping force and wide damping adjustable range Download PDFInfo
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- CN115143224B CN115143224B CN202210957290.3A CN202210957290A CN115143224B CN 115143224 B CN115143224 B CN 115143224B CN 202210957290 A CN202210957290 A CN 202210957290A CN 115143224 B CN115143224 B CN 115143224B
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- 238000013016 damping Methods 0.000 title claims abstract description 68
- 239000012530 fluid Substances 0.000 claims abstract description 30
- 238000002955 isolation Methods 0.000 claims abstract description 13
- 230000005284 excitation Effects 0.000 claims abstract description 11
- 230000005389 magnetism Effects 0.000 claims description 18
- WABPQHHGFIMREM-UHFFFAOYSA-N lead(0) Chemical compound [Pb] WABPQHHGFIMREM-UHFFFAOYSA-N 0.000 claims description 10
- 239000007788 liquid Substances 0.000 claims description 8
- 238000007789 sealing Methods 0.000 claims description 7
- 238000002347 injection Methods 0.000 claims description 5
- 239000007924 injection Substances 0.000 claims description 5
- 238000004804 winding Methods 0.000 claims description 5
- 230000000694 effects Effects 0.000 abstract description 5
- 230000009467 reduction Effects 0.000 abstract description 2
- 230000006698 induction Effects 0.000 description 9
- 230000009471 action Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 2
- 238000010586 diagram Methods 0.000 description 2
- 239000000463 material Substances 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 230000008859 change Effects 0.000 description 1
- 239000004020 conductor Substances 0.000 description 1
- 238000010276 construction Methods 0.000 description 1
- 230000002349 favourable effect Effects 0.000 description 1
- 239000000696 magnetic material Substances 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000012986 modification Methods 0.000 description 1
- 230000004048 modification Effects 0.000 description 1
- 230000000149 penetrating effect Effects 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
- 239000007787 solid Substances 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
Classifications
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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
- F16F9/30—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium with solid or semi-solid material, e.g. pasty masses, as damping medium
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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
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/504—Inertia, i.e. acceleration,-sensitive means
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Fluid-Damping Devices (AREA)
Abstract
A magnetorheological damper with low zero-field damping force and wide damping adjustable range belongs to the technical field of vibration reduction systems. The device comprises a cylinder body, a piston coaxially arranged in the cylinder body, two cylinder body end covers detachably arranged at two ends of the cylinder body and used for supporting the piston to reciprocate, and a coil arranged in the middle of the outer wall of the piston; the piston is characterized in that a bulge is arranged in the middle of the piston, the coil is arranged on the bulge, the bulge divides a cavity of the cylinder body into a cavity I and a cavity II, and the cavity I and the cavity II are communicated with the inner wall of the cylinder body through a gap between the bulge and the inner wall of the cylinder body. The magnetorheological damper provided by the invention can provide smaller zero-field damping force. Under the working condition that the exciting coil is not electrified, magnetorheological fluid can freely flow in the inner annular throttling channel and the outer annular throttling channel, compared with a traditional single-channel magnetorheological damper, the sectional area of the throttling channel is greatly increased, the minimum damping force output value of the damper can be reduced, and the vibration isolation effect under the high-frequency excitation working condition is improved.
Description
Technical Field
The invention belongs to the technical field of vibration reduction systems, and particularly relates to a magneto-rheological damper.
Background
Magnetorheological fluid is a novel intelligent material, and is in a Newtonian fluid state when no magnetic field exists in the environment. The magnetorheological fluid is capable of transitioning from a newtonian fluid state to a semi-solid state within milliseconds upon application of a magnetic field thereto, and the change is reversible. The magneto-rheological damper is a semi-active actuator designed based on the magneto-rheological effect, and the output damping force can be adjusted by controlling the exciting current. Compared with the traditional hydraulic damper, the magnetorheological damper has the outstanding advantages of continuously adjustable damping, high failure safety, quick response and the like, so that the magnetorheological damper becomes a research hot spot in recent years and is widely applied to the fields of vehicle suspensions, civil construction, aerospace and the like.
The damping force adjustable range is a key index for evaluating the performance of the magnetorheological damper. The existing magnetorheological damper structure increases the maximum output damping force of the magnetorheological damper by increasing the number of exciting coils, increasing the effective area of a magnetic field, increasing the length of a throttling channel and the like, so that the aim of widening the adjustable range of the damping force is fulfilled. However, according to the linear vibration isolation theory, in the high-frequency vibration isolation area, the damping coefficient of the system is reduced to be beneficial to improving the vibration isolation performance of the system, so that it is necessary to provide a magneto-rheological damper with smaller zero-field damping force and wider damping adjustable range.
The damping force output of the magneto-rheological damper comprises three parts, namely viscous damping force, coulomb damping force and friction force. The viscous damping force is damping force caused by viscosity of magnetorheological fluid, belongs to uncontrollable damping force, and needs to be reduced in order to reduce zero-field damping force of the magnetorheological damper. The coulomb damping force is a damping force generated by a magneto-rheological effect, belongs to a controllable damping force, and needs to be increased in order to improve the adjustable range of the damping force. The friction force mainly refers to friction between sealing elements in the magnetorheological damper, the friction force belongs to uncontrollable damping force, and in order to reduce damping force caused by friction, the use of sliding sealing elements is required to be reduced as much as possible in structural design.
Most of the existing magnetorheological dampers adopt a single annular throttling channel structure, and according to the theory of fluid mechanics, in order to reduce viscous damping force, the gap of the throttling channel needs to be increased. However, on the premise that the number of turns of the exciting coil is certain, the increase of the gap of the throttling channel can reduce the magnetic induction intensity in the throttling channel, so that the coulomb damping force is reduced, and the damping force adjustable range of the magnetorheological damper is reduced. Therefore, the traditional single-channel magneto-rheological damper is difficult to realize the two design targets of low zero-field damping and wide damping adjustable range at the same time.
The reference literature finds that the existing double-channel magneto-rheological damper structure mostly adopts a single coil structure, the magnetic field intensity in two throttling channels is simultaneously controlled by the same turn of exciting coil, and the magnetic induction wires generated by the coils need to vertically penetrate through the gaps of the two throttling channels at the same time, so that the magnetic resistance in a magnetic loop is greatly increased. In order to ensure that the magnetic induction intensity in the throttling channel meets the requirement, the number of turns of the exciting coil is required to be increased, so that the radial size of the existing double-channel magneto-rheological damper is greatly increased, the area of the piston is increased, and the zero-field damping force of the magneto-rheological damper is further increased.
To sum up, in order to improve the vibration isolation performance of the magnetorheological damper, it is necessary to improve the existing magnetorheological damper structure, and design a magnetorheological damper with low zero-field damping force and wide damping adjustable range. The vibration isolation performance of the magnetorheological damper under high-frequency excitation is improved, and the application scene of the magnetorheological damper is widened.
Disclosure of Invention
The invention aims to solve the problems in the background art, and further provides a magnetorheological damper with low zero-field damping force and wide damping adjustable range.
The technical scheme adopted by the invention is as follows: a magnetorheological damper with low zero-field damping force and wide damping adjustable range comprises a cylinder body, a piston coaxially arranged in the cylinder body, two cylinder body end covers detachably arranged at two ends of the cylinder body and used for supporting the piston to reciprocate, and a coil arranged in the middle of the outer wall of the piston; the piston is characterized in that a bulge is arranged in the middle of the piston, the coil is arranged on the bulge, the bulge divides a cavity of the cylinder body into a cavity I and a cavity II, and the cavity I and the cavity II are communicated with the inner wall of the cylinder body through a gap between the bulge and the inner wall of the cylinder body.
Compared with the prior art, the invention has the following beneficial effects:
1. compared with the existing magnetorheological damper, the magnetorheological damper provided by the invention can provide smaller zero-field damping force. Under the working condition that the exciting coil is not electrified, magnetorheological fluid can freely flow in the inner annular throttling channel and the outer annular throttling channel, compared with a traditional single-channel magnetorheological damper, the sectional area of the throttling channel is greatly increased, the minimum damping force output value of the damper can be reduced, and the vibration isolation effect under the high-frequency excitation working condition is improved.
2. The magnetorheological damper provided by the invention is provided with the magnetic conduction ring and the magnetism isolation ring at the inner sides of the two throttling channels, and the design of the magnetic conduction ring and the magnetism isolation ring can greatly increase the effective coverage area of a magnetic field under the power-on working condition, so that the maximum output damping force of the magnetorheological damper is increased, and the vibration suppression effect of the magnetorheological damper in a low-frequency resonance area is improved.
3. The magnetorheological damper provided by the invention has an impact overload protection function. When the current in the inner exciting coil is greater than the current in the outer exciting coil, the magnetorheological fluid shear yield stress in the inner throttle passage is greater. When the piston moving speed is lower under the working condition, the outer throttling channel is opened, the inner throttling channel is closed, when the magnetorheological damper is excited by impact, the piston moving speed is rapidly increased, at the moment, the liquid flow velocity in the outer throttling channel is rapidly increased, the viscous pressure loss generated by the outer throttling channel is larger than the coulomb pressure loss generated by the inner throttling channel, at the moment, the outer throttling channel and the inner throttling channel are simultaneously opened, the liquid flow velocity in the channels is obviously reduced, the rapid increase of damping force can be restrained, the force transmitted to an object to be isolated by the impact excitation is further reduced, and the impact overload protection function is realized.
Drawings
FIG. 1 is a schematic diagram of the structure of the present invention;
FIG. 2 is a schematic illustration of the piston end cap structure of the present invention;
FIG. 3 is a schematic diagram of the cylinder end cap structure of the present invention;
FIG. 4 is a schematic view of the structure of the toroidal magnetic pole of the present invention;
FIG. 5 is a cut-away view of section A-A of FIG. 4;
FIG. 6 is a graph of the magnetic induction lines of the present invention when the inside excitation coil is energized;
FIG. 7 is a graph of the magnetic induction lines of the present invention when the outside excitation coil is energized;
FIG. 8 is a graph of the magnetic induction lines of the present invention when the inner and outer exciting coils are energized simultaneously;
wherein: 1. a piston rod sealing ring; 2. a cylinder end cover; 3. a bolt; 4. a lead hole; 5. a piston end cap; 6. circular ring magnetic poles; 7. an outer magnetic conduction ring I; 8. an outer magnetism isolating ring; 9. an outer magnetic conduction ring II; 10. an outer exciting coil; 11. an inner exciting coil; 12. a screw; 13. a cylinder end cover sealing ring; 14. a chamber II; 15. an inner side magnetic conduction ring I; 16. an inner magnetism isolating ring I; 17. an inner side magnetic conduction ring II; 18. a cylinder; 19. a chamber I; 20. a liquid injection hole; 21. a piston rod; 22. a circular ring-shaped groove; 23. an arc-shaped through hole; 24. screw holes; 25. a cylinder end cover wire groove; 26. bolt holes; 27. circular ring type boss.
Detailed Description
For a better understanding of the objects, structures and functions of the present invention, reference should be made to the following detailed description of the invention with reference to the accompanying drawings.
Referring to fig. 1, the magnetorheological damper with low zero-field damping force and wide damping adjustable range of the invention comprises a cylinder 18, a piston rod 21 coaxially arranged in the cylinder 18, two cylinder end covers 2 detachably arranged at two ends of the cylinder 18 and used for supporting the piston rod 21 to reciprocate, and a coil arranged in the middle of the outer wall of the piston rod 21; the middle of the piston rod 21 is provided with a bulge, the coil is arranged on the bulge, the bulge divides the cavity of the cylinder body 18 into a cavity I19 and a cavity II 14, and the cavity I19 and the cavity II 14 are communicated with the inner wall of the cylinder body 18 through gaps between the bulge and the inner wall of the cylinder body 18.
Magnetorheological fluid is in the chamber I19 and the chamber II 14.
Wherein: the coils consist of an inner exciting coil 11 and an outer exciting coil 10;
the inner exciting coil 11 is wound in a winding groove arranged on a boss part of the piston rod 21, and a lead of the inner exciting coil 11 is led out through a lead hole 4 arranged on the piston rod 21;
the outer exciting coil 10 is wound in a winding groove formed in the ring magnetic pole 6, and a lead wire of the outer exciting coil 10 is led out through the lead wire groove of the ring magnetic pole 6, the cylinder end cover lead wire groove 25 and the lead wire hole 4.
The ring magnetic pole 6 is sleeved outside the inner exciting coil 11, a gap is formed between the ring magnetic pole 6 and the inner exciting coil 11 to form an inner throttling channel, a gap between the outer exciting coil 10 and the inner wall of the cylinder body 18 forms an outer throttling channel, magnetorheological fluid in the cavity I19 and the cavity II 14 can flow freely in the inner throttling channel and the outer throttling channel, compared with a traditional single-channel magnetorheological damper, the sectional area of the throttling channel is greatly increased, the minimum damping force output value of the damper can be reduced, and the vibration isolation effect under the high-frequency excitation working condition is improved.
And the circular ring magnetic pole 6 is clamped and fixed by the piston end covers 5 arranged at the two ends of the boss part of the piston rod 21.
In addition, the magnetorheological damper further comprises an inner side magnetic conduction ring I15, an inner side magnetic conduction ring II 17, an inner side magnetism isolating ring 16, an outer side magnetic conduction ring I7, an outer side magnetic conduction ring II 9 and an outer side magnetism isolating ring 8;
the inner side magnetic conduction ring I15 and the inner side magnetic conduction ring II 17 are sleeved on the outer surface of the protruding part of the piston rod 21, the inner side magnetic isolation ring 16 is arranged between the inner side magnetic conduction ring I15 and the inner side magnetic conduction ring II 17 and sleeved on the outer surface of the inner side exciting coil 11, and the inner side magnetic conduction ring I and the inner side magnetic conduction ring II 17 are clamped and fixed on the piston rod 21 through the two piston end covers 5;
the outer magnetic conduction ring I7 and the outer magnetic conduction ring II 9 are sleeved on the outer surface of the circular ring magnetic pole 6, and are clamped and fixed on the piston rod 21 through the two piston end covers 5; the outer magnetism isolating ring 8 is arranged between the outer magnetic conducting ring I7 and the outer magnetic conducting ring II 9 and sleeved on the outer surface of the outer exciting coil 10;
the outer wall of the inner side magnetic conduction ring I15, the outer wall of the inner side magnetism isolating ring 16, the outer wall of the inner side magnetic conduction ring II 17 and the inner wall of the circular ring magnetic pole 6 form an inner side throttling channel;
the outer walls of the outer magnetic conduction ring I7, the outer magnetism isolating ring 8 and the outer magnetic conduction ring II 9 and the inner wall of the cylinder body 18 form an outer throttling channel.
The design of the magnetic conduction ring and the magnetism isolation ring can greatly increase the effective coverage area of the magnetic field under the electrifying working condition, further increase the maximum output damping force of the magnetorheological damper, and be favorable for improving the vibration suppression effect of the magnetorheological damper in a low-frequency resonance area.
The method comprises the following steps: as shown in the figure 3 of the drawings,
the two piston rods 21 and the cylinder end cover 2 are sealed by a piston rod sealing ring 1.
Six bolt holes 26 which are uniformly distributed in the circumferential direction are designed on the end faces of the two cylinder end covers 2 and are used for installing bolts 3,
the two cylinder end covers 2 are connected with the cylinder 18 through bolts 3, and a cylinder end cover sealing ring 13 is designed on the end surface of the joint of the cylinder end cover 2 and the cylinder 18 to prevent the magnetorheological fluid in the cylinder 18 from overflowing,
the end face of the cylinder end cover 2 above the two cylinder end covers 2 is provided with a liquid injection hole 20, and after the assembly of the magnetorheological damper is completed, magnetorheological liquid is injected from the liquid injection hole 20.
As shown in the figure 2 of the drawings,
the two piston end covers 5 are respectively sleeved on the upper side and the lower side of the protruding part of the piston rod 21, and are fixed on the piston rod 21 through screws 12,
a plurality of arc-shaped through holes 23, preferably four, are uniformly distributed on the end surfaces of the two piston end covers 5 and are communicated with the inner throttling channel for conducting magnetorheological fluid,
a plurality of screw holes 24 are uniformly distributed on the end surfaces of the two piston end covers 5 and are used for installing the screws 12.
An annular groove 22 is arranged on the end surfaces of the two piston end covers 5 and matched with an annular boss 27 arranged on the outer wall of the annular magnetic pole 6 for positioning and clamping the annular magnetic pole 6.
A radial cylinder end cap wire groove 25 is arranged on the end face of the upper piston end cap 5 for leading out the wires of the outer exciting coil 10.
As shown in figures 4 and 5 of the drawings,
the outer circumferential surface of the circular magnetic pole 6 is provided with a winding groove for leading out the wires of the outer exciting coil 10; annular bosses 27 are designed at the two ends of the annular magnetic pole 6, and the annular bosses 27 are matched with the annular grooves 22 on the two piston end covers 5 for positioning the annular magnetic pole 6.
The cylinder end cover 2, the piston end cover 5, the inner magnetism isolating ring 16 and the outer magnetism isolating ring 8 are all made of non-magnetic materials; the rest parts are made of magnetic conductive materials.
The working principle of the invention is as follows:
when the inner exciting coil 11 and the outer exciting coil 10 are not electrified, no magnetic field exists in the inner throttling channel and the outer throttling channel, when the piston rod 21 moves, magnetorheological fluid in the chamber I19 and the chamber II 14 can flow through the inner throttling channel and the outer throttling channel, and due to viscosity of the fluid, pressure difference is generated between two end faces of the piston rod 21, and damping force is generated.
The distribution of magnetic induction lines inside the magnetorheological damper when the inner exciting coil 11 is energized and the outer exciting coil 10 is not energized is shown in fig. 6. At the moment, a magnetic field vertically passing through the channel is generated in the inner throttling channel, the magnetic field does not exist in the outer throttling channel, and the shear yield stress of magnetorheological fluid in the inner throttling channel is obviously increased under the action of the magnetic field. When the piston rod 21 moves at a low speed, magnetorheological fluid only flows through the outside throttling channel, and the increasing of the exciting current of the inside exciting coil 11 has no influence on the damping force output value; when the piston rod 21 is excited by the impact, the movement speed of the piston rod 21 is increased to cause the flow speed of the magnetorheological fluid to be increased, and further the viscous pressure drop generated by the outer throttling channel is obviously increased, when the viscous pressure drop generated by the outer throttling channel is larger than the coulomb pressure drop of the inner throttling channel, the magnetorheological fluid in the inner throttling channel starts to flow, and at the moment, the flow speed of the magnetorheological fluid in the channel is greatly reduced compared with that of the magnetorheological fluid in the channel when the magnetorheological fluid only flows by the outer throttling channel, so that the abrupt increase of damping force can be restrained, and the force transmissibility under the impact excitation working condition is reduced.
When the inner exciting coil 11 is not energized and the outer exciting coil 10 is energized, the magnetic induction lines inside the magnetorheological damper are distributed as shown in fig. 7. At this time, a magnetic field vertically passing through the channel is generated in the outer throttling channel, the magnetic field does not exist in the inner throttling channel, and the shear yield stress of the magnetorheological fluid in the outer throttling channel is obviously increased under the action of the magnetic field. At this time, the magnetorheological fluid only flows in the inner throttling channel under the low-speed working condition, and when the moving speed of the piston rod 21 is increased, the magnetorheological fluid in the inner throttling channel and the magnetorheological fluid in the outer throttling channel flow simultaneously, so that the abrupt increase of damping force under the impact excitation working condition can be restrained, and the force transmissibility under the impact excitation working condition is reduced.
When the inner exciting coil 11 and the outer exciting coil 10 are energized simultaneously, the magnetic induction lines inside the magnetorheological damper are distributed as shown in fig. 8. At the moment, magnetic fields vertically penetrating through the channels are generated in the inner throttling channel and the outer throttling channel, and the damping force output by the magnetorheological damper is maximum at the moment.
It will be understood that the invention has been described in terms of several embodiments, and that various changes and equivalents may be made to these features and embodiments by those skilled in the art without departing from the spirit and scope of the invention. In addition, many modifications may be made to adapt a particular situation or material to the teachings of the invention without departing from the essential scope thereof. Therefore, it is intended that the invention not be limited to the particular embodiment disclosed, but that the invention will include all embodiments falling within the scope of the appended claims.
Claims (6)
1. A magnetorheological damper with low zero field damping force and wide damping adjustable range, characterized in that: the device comprises a cylinder body (18), a piston rod (21) coaxially arranged in the cylinder body (18), two cylinder body end covers (2) detachably arranged at two ends of the cylinder body (18) and used for supporting the piston rod (21) to reciprocate, and a coil arranged in the middle of the outer wall of the piston rod (21); a bulge is arranged in the middle of the piston rod (21), the coil is arranged on the bulge, the bulge divides a cavity of the cylinder body (18) into a cavity I (19) and a cavity II (14), the cavity I (19) and the cavity II (14) are communicated with the inner wall of the cylinder body (18) through a gap between the bulge,
the coil consists of an inner exciting coil (11) and an outer exciting coil (10);
the inner exciting coil (11) is wound in a winding groove arranged on the boss part of the piston rod (21),
the outside exciting coil (10) is wound in a winding slot arranged on the circular ring magnetic pole (6), the circular ring magnetic pole (6) is sleeved outside the inside exciting coil (11), a gap is arranged between the circular ring magnetic pole (6) and the inside exciting coil (11) to form an inside throttling channel, a gap between the outside exciting coil (10) and the inner wall of the cylinder body (18) forms an outside throttling channel, magnetorheological fluid in the cavity I (19) and the cavity II (14) can freely flow in the inside throttling channel and the outside throttling channel, the circular ring magnetic pole (6) is clamped and fixed by piston end covers (5) arranged at two ends of a boss part of the piston rod (21),
the magnetorheological damper with the low zero-field damping force and the wide damping adjustable range further comprises an inner side magnetic conduction ring I (15), an inner side magnetic conduction ring II (17), an inner side magnetism isolating ring (16), an outer side magnetic conduction ring I (7), an outer side magnetic conduction ring II (9) and an outer side magnetism isolating ring (8);
the inner side magnetic conduction ring I (15) and the inner side magnetic conduction ring II (17) are sleeved on the outer surface of the bulge of the piston rod (21), clamping is achieved through the two piston end covers (5), and the inner side magnetic isolation ring (16) is arranged between the inner side magnetic conduction ring I (15) and the inner side magnetic conduction ring II (17) and sleeved on the outer surface of the inner side excitation coil (11);
the outer magnetic conduction ring I (7) and the outer magnetic conduction ring II (9) are sleeved on the outer surface of the circular magnetic pole (6), and clamping is achieved through the two piston end covers (5); the outer magnetism isolating ring (8) is arranged between the outer magnetism conducting ring I (7) and the outer magnetism conducting ring II (9) and sleeved on the outer surface of the outer exciting coil (10);
the outer wall of the inner magnetic conduction ring I (15), the outer wall of the inner magnetism isolating ring (16), the outer wall of the inner magnetic conduction ring II (17) and the inner wall of the circular magnetic pole (6) form an inner throttling channel; the outer walls of the outer magnetic conduction rings I (7), 8 and II (9) and the inner wall of the cylinder body (18) form an outer throttling channel.
2. The magnetorheological damper of claim 1, wherein the magnetorheological damper has a low zero field damping force and a wide damping adjustable range: the two cylinder body end covers (2) are connected with the cylinder body (18) through bolts (3), a cylinder body end cover sealing ring (13) is designed on the end face of the joint of the cylinder body end cover (2) and the cylinder body (18), so that magnetorheological fluid in the cylinder body (18) is prevented from overflowing, a liquid injection hole (20) is designed on the end face of the cylinder body end cover (2) positioned above the two cylinder body end covers (2), and after the assembly of the magnetorheological damper is completed, the magnetorheological fluid is injected from the liquid injection hole (20).
3. The magnetorheological damper of claim 2, wherein the magnetorheological damper has a low zero field damping force and a wide damping adjustable range: the two piston end covers (5) are respectively sleeved on the upper side and the lower side of the bulge part of the piston rod (21), and are fixed on the piston rod (21) through screws (12), a plurality of arc-shaped through holes (23) are uniformly distributed on the end surfaces of the two piston end covers (5), are communicated with the inner side throttling channel and are used for conducting magnetorheological fluid,
a plurality of screw holes (24) are uniformly distributed on the end faces of the two piston end covers (5) and are used for installing screws (12).
4. A magnetorheological damper having a low zero field damping force and a wide damping adjustable range according to claim 3, wherein: an annular groove (22) is formed in the end faces of the two piston end covers (5), and is matched with an annular boss (27) arranged on the outer wall of the annular magnetic pole (6) for positioning and clamping the annular magnetic pole (6).
5. The magnetorheological damper of claim 4, wherein the low zero field damping force and wide damping adjustable range: a radial cylinder end cover wire groove (25) is arranged on the end face of the upper piston end cover (5) and is used for leading out wires of the outer exciting coil (10).
6. The magnetorheological damper of claim 5, wherein the low zero field damping force and wide damping adjustable range: the lead wire of the inner exciting coil (11) is led out through a lead wire hole (4) arranged on the piston rod (21);
the lead wire of the outer exciting coil (10) is led out through the lead wire groove of the circular ring magnetic pole (6), the lead wire groove (25) of the cylinder end cover and the lead wire hole (4).
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210957290.3A CN115143224B (en) | 2022-08-10 | 2022-08-10 | Magnetorheological damper with low zero-field damping force and wide damping adjustable range |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202210957290.3A CN115143224B (en) | 2022-08-10 | 2022-08-10 | Magnetorheological damper with low zero-field damping force and wide damping adjustable range |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| CN115143224A CN115143224A (en) | 2022-10-04 |
| CN115143224B true CN115143224B (en) | 2024-01-05 |
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Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN202210957290.3A Active CN115143224B (en) | 2022-08-10 | 2022-08-10 | Magnetorheological damper with low zero-field damping force and wide damping adjustable range |
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Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07332427A (en) * | 1994-06-06 | 1995-12-22 | Natl Res Inst For Metals | Variable damping force shock absorber and magnetic fluid flow control mechanism suitable thereto |
| JP2004270719A (en) * | 2003-03-05 | 2004-09-30 | Bando Chem Ind Ltd | Adjustable damping force type damper |
| JP2009216206A (en) * | 2008-03-12 | 2009-09-24 | Honda Motor Co Ltd | Variable damping force damper |
| CN106402255A (en) * | 2016-11-29 | 2017-02-15 | 哈尔滨工业大学 | Magneto-rheological damper with sinuous magnetic circuit characteristic |
| KR101984633B1 (en) * | 2018-01-18 | 2019-05-31 | 인하대학교 산학협력단 | MR damper |
| CN109973580A (en) * | 2019-04-26 | 2019-07-05 | 哈尔滨工业大学 | A kind of MR damper suitable for high speed impact |
-
2022
- 2022-08-10 CN CN202210957290.3A patent/CN115143224B/en active Active
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH07332427A (en) * | 1994-06-06 | 1995-12-22 | Natl Res Inst For Metals | Variable damping force shock absorber and magnetic fluid flow control mechanism suitable thereto |
| JP2004270719A (en) * | 2003-03-05 | 2004-09-30 | Bando Chem Ind Ltd | Adjustable damping force type damper |
| JP2009216206A (en) * | 2008-03-12 | 2009-09-24 | Honda Motor Co Ltd | Variable damping force damper |
| CN106402255A (en) * | 2016-11-29 | 2017-02-15 | 哈尔滨工业大学 | Magneto-rheological damper with sinuous magnetic circuit characteristic |
| KR101984633B1 (en) * | 2018-01-18 | 2019-05-31 | 인하대학교 산학협력단 | MR damper |
| CN109973580A (en) * | 2019-04-26 | 2019-07-05 | 哈尔滨工业大学 | A kind of MR damper suitable for high speed impact |
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| Publication number | Publication date |
|---|---|
| CN115143224A (en) | 2022-10-04 |
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