CN103352956A - Magneto-rheological damper with asymmetrical controllable damping characteristic - Google Patents

Magneto-rheological damper with asymmetrical controllable damping characteristic Download PDF

Info

Publication number
CN103352956A
CN103352956A CN201310244075XA CN201310244075A CN103352956A CN 103352956 A CN103352956 A CN 103352956A CN 201310244075X A CN201310244075X A CN 201310244075XA CN 201310244075 A CN201310244075 A CN 201310244075A CN 103352956 A CN103352956 A CN 103352956A
Authority
CN
China
Prior art keywords
piston head
damper
cylinder barrel
controllable damping
cavity volume
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
CN201310244075XA
Other languages
Chinese (zh)
Other versions
CN103352956B (en
Inventor
王代华
刘鹏飞
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Chongqing University
Original Assignee
Chongqing University
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Chongqing University filed Critical Chongqing University
Priority to CN201310244075.XA priority Critical patent/CN103352956B/en
Publication of CN103352956A publication Critical patent/CN103352956A/en
Application granted granted Critical
Publication of CN103352956B publication Critical patent/CN103352956B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Landscapes

  • Fluid-Damping Devices (AREA)

Abstract

The invention discloses a magneto-rheological damper with an asymmetrical controllable damping characteristic. The magneto-rheological damper comprises a magneto-rheological damper body, wherein a piston head of the magneto-rheological damper body is provided with a magnet exciting coil and separates an inner cavity of a cylinder barrel into a first accommodating cavity close to the lower end of the cylinder barrel and a second accommodating cavity close to the upper end of the cylinder barrel; convection holes which are communicated with the first accommodating cavity and the second accommodating cavity are formed inside the piston head; and valve components which are used for performing one-way throttling on a magneto-rheological fluid from the second accommodating cavity to the first accommodating cavity are arranged in the convection holes. The magneto-rheological damper with the asymmetrical controllable damping characteristic can enable recovery and controllable damping force to be larger than compression controllable damping force, can produce larger recovery damping force under smaller current, can prolong the recovery time, and is applicable to a vibration control system such as a motorcycle rear suspension or other vehicle suspension system, which requires asymmetrical controllable damping, and semi-active vibration control is realized by changing current of the magnet exciting coil of the magneto-rheological damper; and the magneto-rheological damper is simple in structure, can realize asymmetrical controllable damping force, and is low in use cost and beneficial to popularization and utilization.

Description

The MR damper of asymmetric controllable damping characteristic
Technical field
The present invention relates to a kind of vibration control apparatus, relate in particular to a kind of MR damper of asymmetric controllable damping characteristic.
Background technique
That damper is divided into is passive, half initiatively and initiatively three kinds.Common passive damping device can not be according to the variation damping adjusting power size of external load.Active control system is to obtain external load with sensor to change in order to allow the correct damping force size of system's output, the whole system more complicated.And more and more be subject to now magnetic converting technique and half ACTIVE CONTROL thereof that people pay attention to, well combine advantage passive and active, as required the output damping force of damping adjusting device.
MR damper is a kind of shock absorber part for half ACTIVE CONTROL suspension that recent two decades occurs.MR damper is the most widely device that magnetic converting technique is used.Have simple in structure, damping force continuously and contrary along adjustable based on the MR damper of magnetic converting technique, and the damping force adjustable extent is large, response is fast, excellent in stability and can with the characteristics such as microcomputer control combination.So MR damper has been subject to various countries research scholars' extensive concern in semi-active suspension.At present, MR damper has obtained preliminary application at the vibration damping of vehicle suspension system, cable-stayed bridge cable vibration control, offshore platform structure and the aspects such as vibration isolation of tall building, has shown good application prospect.But because there are the problem of particles settling in cost and magnetic flow liquid itself, MR damper also generally is not used for civilian vehicle at present, and majority is all used in some luxury cars and military equipment.
Magnetic flow liquid is comprised of ferromagnetic particle, surface active agent and suspension.The size of ferromagnetic particle generally adopts the magnetic materials processings such as iron, cobalt, nickel to form generally in the 1-10um scope; Carrier fluid is used silicone oil, kerosene and mineral oil usually, has good flame retarding and temperature stability, and environment is not polluted, and contacts also with general material and can not cause corrosive action; Active agent mainly has been stable effect, prevents that ferromagnetic particle is together inter-adhesive, causes the conglomeration sedimentation phenomenon.The structure of molecule of this Active agent is very special, and an end has very large affinity to the magnetic-particle surface, can firmly be adsorbed on the magnetic-particle surface, and the other end is very easily to be scattered in the elasticity group that has suitable length in the carrier fluid.Therefore the Active agent that adds in the carrier fluid generally adopts silica additive or other surfactants.
Magnetic rheological liquid is a kind of intellectual material, and when having magnetic field in the magnetic flow liquid, huge variation will occur the anti-shearing force of liquid, is exactly so-called magnetic rheology effect.Just because of the easy control of magnetic rheology effect, magnetic flow liquid has a wide range of applications in vibration control.Specifically, magnetic flow liquid can become half liquid by free-pouring liquid in magnetic field semi-solid, and the conversion time between this very fast (Microsecond grade).Under the free-flow form, the plastic viscosity of the magnetic flow liquid only volume fraction with the viscosity of carrier fluid and ferromagnetic particle is relevant.And behind externally-applied magnetic field, the performance of magnetic flow liquid will change along with the variation of externally-applied magnetic field, and before not reaching magnetic saturation, magnetic intensity is larger, and anti-shearing force is just larger.The plastic viscosity of magnetic flow liquid can be treated as a constant, changes very little.Behind the externally-applied magnetic field, only have when shearing stress surpasses yield stress, magnetic flow liquid could free-flow.Above-mentioned characteristic based on magnetic flow liquid, the size of MR damper damping force of the prior art is only controlled by externally-applied magnetic field, namely realize by the size of current that changes field coil, and when MR damper is applied in the vehicle, because the state difference that jolts that vehicle travels under different road conditions is larger, therefore the real-time adjusting function of the vibration control of damper is had relatively high expectations, even if in conjunction with controller, the state of jolting that also can't predict vehicle comes the size of current of field coil is regulated in real time, and MR damper of the prior art does not have asymmetric controllable damping characteristic, and the damping force size was consistent substantially when damper was done recovery motion and compression movement under the equal conditions.And in the motorbike back suspension damper, given when mounted very large pre-pressing with the spring of damper coupling, this just causes damper resistance when doing compression movement very large, if damper itself has very large resistance to compression pression, will be unfavorable for the normal to-and-fro motion of piston head.So in motorbike back suspension, require to restore resistance much larger than resistance to compression pression.If the MR damper of traditional symmetrical damping characteristic needing to be used for the occasion of asymmetric controllable damping characteristic, such as the motorbike back suspension system, will when doing compression movement, turn by damper electric current or close current down with controller so, this not only needs to introduce sensor and control circuit, and increased system complexity, improved cost.Therefore the MR damper that does not also have at present to realize asymmetric controllable damping characteristic is used for motorbike back suspension.
Therefore, for solving the appeal problem, need to be improved the MR damper of the symmetrical damping characteristic of tradition, allow MR damper restore resistance much larger than resistance to compression pression, on the MR damper basis that keeps traditional symmetrical damping characteristic, keep its restoration damping characteristics, namely regulate recovery damping force by regulating size of current, but change its compression damping characteristic, allow resistance to compression pression greatly reduce, need not repeatedly to regulate the size of current in the to-and-fro motion conversion process, need to be applicable in the vibration control system of asymmetric controllable damping characteristic, such as the damper on the motorbike back suspension or other vehicle suspension systems, play preferably damping effect.
Summary of the invention
In view of this, the MR damper that the purpose of this invention is to provide a kind of asymmetric controllable damping characteristic, on the basis of original ring magnetic rheological valve, increase asymmetric convection holes and magnetic flow liquid has been carried out the valve member of one-way throttle along convection holes, when restoring motion, regulate size of current and just can obtain different damping forces, but when compression movement, size of current is very little on the impact of damping force size, resistance to compression pression all remains on a very low level, need to be applicable to such as the damper on the motorbike back suspension or other vehicle suspension systems, play preferably damping effect in the vibration control system of asymmetric damping.
The MR damper of asymmetric controllable damping characteristic of the present invention comprises the MR damper body; Described MR damper body comprises cylinder barrel, piston rod, piston head and is filled in the magnetic flow liquid of inner cavity of cylinder; Described piston head is provided with field coil and piston head and is located in the cylinder barrel and inner cavity of cylinder is divided near the first cavity volume of cylinder barrel lower end with near the second cavity volume of cylinder barrel upper end; Described piston head inside is provided with the convection holes that is communicated in the first cavity volume and the second cavity volume; Described convection holes is provided with for the valve member that magnetic flow liquid is carried out one-way throttle by the second cavity volume to the first cavity volume;
Further, the elastic reset normally closed structure of described valve member for can under the magnetic flow liquid pressure-acting, opening;
Further, it is circumferentially uniform along piston head that described convection holes is at least two and each convection holes;
Further, described valve member is located in the second cavity volume, and valve member comprises annular reed and Returnning spring, and described annular reed is with the coaxial setting of piston head and be slidingly connected to vertically piston head; Described Returnning spring bullet peaks at and is used between piston rod and the reed reed is suppressed in piston head end face and then sealing convection holes;
Further, described Returnning spring is the tower spring;
Further, the corresponding Returnning spring of described piston rod and annular reed are provided with the shell-like block; Described shell-like block clamping and positioning is between piston rod and piston head, and the shell-like block is provided with the flange that is used for supporting Returnning spring that radially protrudes; Annular reed and the axial sliding fit of shell-like block outer wall;
Further, described field coil be two and two field coils around on the contrary;
Further, described MR damper body also comprises the positioning disk that piston rod and piston head is carried out slide-and-guide with inner wall of cylinder being used for of being slidingly matched; The positioning disk excircle is fixed with the seal ring that is sealed and matched with inner wall of cylinder; Be provided with the damp channel that between the first cavity volume and the second cavity volume, flows for for magnetic flow liquid between described piston head and the cylinder barrel; Described positioning disk is provided with the through flow hole that is communicated with damp channel and convection holes for the first cavity volume, and separately moulding and be fixedly connected with by screw thread with piston head of positioning disk also can be one-body molded with piston head;
Further, be provided with the upper black box that is sealedly attached to piston rod and cylinder barrel on the described cylinder barrel; Described upper black box comprises upper end cap, upper end cap rubber envelope, the fixing interior safety pad of Z-shaped card, Z-shaped card, slide plate, oil sealing card, oil sealing and cylinder; Described piston rod upper end is fixed with end connector; Be positioned at the end connector lower end and be placed in the piston rod outer wall and be provided with the outer safety pad of cylinder; Described field coil draw wire along the axis setting of piston head and piston rod and by drawing in the upper end connector; Described cylinder barrel lower end is sealedly connected with lower end connector; Described lower end connector is provided with the air bag that is communicated with the first cavity volume; Described lower end connector is connected by rolling or thread seal with cylinder barrel;
Further, described cylinder barrel and piston head are made by high permeability material and are also made by high permeability material when positioning disk and piston head are one-body molded; Described shell-like block, piston rod and upper black box are made by non-magnet_conductible material and are also made by non-magnet_conductible material when the independent moulding of positioning disk; Described field coil is by the enameled cable coiled.
The invention has the beneficial effects as follows: the MR damper of asymmetric controllable damping characteristic of the present invention, on the basis of original ring magnetic rheological valve, increase asymmetric convection holes and magnetic flow liquid has been carried out the valve member of one-way throttle along convection holes, when restoring motion, regulate size of current and just can obtain different damping forces, but when compression movement, size of current is very little on the impact of damping force size, resistance to compression pression all remains on a very low level, need to be applicable in the vibration control system of asymmetric damping, such as the damper on the motorbike back suspension or other vehicle suspension systems, realize the control of half active vibration by the electric current that changes the MR damper field coil; The present invention is simple in structure, realizes asymmetric controllable damping force; Easy and simple to handle, but energy efficient, and user cost is low, is beneficial to promote the use of.
Description of drawings
The invention will be further described below in conjunction with drawings and Examples:
Fig. 1 is the structural representation of compression stroke of the present invention;
Fig. 2 is the structural representation that the present invention restores stroke;
Fig. 3 is the A place zoomed-in view of Fig. 1;
Fig. 4 is the B place zoomed-in view of Fig. 2;
Fig. 5 is monopolar configuration schematic representation of the present invention;
Fig. 6 is that piston rod stretches into fixed connection structure schematic representation in the piston head;
Fig. 7 is that piston rod runs through piston head fixed connection structure schematic representation.
Embodiment
Fig. 1 is the structural representation of compression stroke of the present invention, Fig. 2 is the structural representation that the present invention restores stroke, Fig. 3 is the A place zoomed-in view of Fig. 1, Fig. 4 is the B place zoomed-in view of Fig. 2, Fig. 5 is monopolar configuration schematic representation of the present invention, and Fig. 6 is that piston rod stretches into fixed connection structure schematic representation in the piston head, and Fig. 7 is that piston rod runs through piston head fixed connection structure schematic representation, as shown in the figure: the MR damper of the asymmetric controllable damping characteristic of present embodiment comprises the MR damper body; Described MR damper body comprises cylinder barrel 14, piston rod 4, piston head 22 and is filled in the magnetic flow liquid of cylinder barrel 14 inner chambers; Described piston head 22 is provided with field coil 20 and piston head 22 and is located at that cylinder barrel 14 is interior to be divided into cylinder barrel 14 inner chambers near the first cavity volume 26 of cylinder barrel 14 lower ends with near the second cavity volume 15 of cylinder barrel 14 upper ends; Cylinder barrel 14 upper ends refer to the end that cylinder barrel 14 corresponding piston rods 4 stretch out; Described piston head 22 inside are provided with the convection holes 21 that is communicated in the first cavity volume 26 and the second cavity volume 15, have effectively utilized piston head 22 volumes; Described convection holes 21 is provided with for the valve member that magnetic flow liquid is carried out one-way throttle by the second cavity volume 15 to first cavity volumes 26; Piston head 22 adopt permeability magnetic materials make and piston head 22 and cylinder barrel 14 between be provided with for for magnetic flow liquid mobile damp channel 19 between the first cavity volume 26 and the second cavity volume 15, during compression stroke, as shown in Figure 1: wherein dotted line and arrow represent the mobile path of magnetic flow liquid and direction, because the magnetic field concentration of field coil 20 inboards is distributed in piston head 22 inside, convection holes 21 internal magnetic fields a little less than, therefore magnetic flow liquid very easily flow to the second cavity volume 15 by convection holes 21 by the first cavity volume 26, and suffered resistance and current relationship are very little, make compression damping power size remain on a very low level; When restoring stroke, as shown in Figure 2: wherein dotted line and arrow represent the mobile path of magnetic flow liquid and direction, by valve member convection holes 21 is carried out partially or completely throttling, make the magnetic flow liquid major part or all flow to the first cavity volume 26 by damp channel 19 by the second cavity volume 15, and via the magnetic flow liquid of damp channel 19 because magnetic fields produces larger damping force, it is recovery damping force, its magnetic induction intensity big or small and in the damp channel 19 is directly proportional, can control by the size of current of regulating field coil 20 size of recovery damping force, field coil 20 can be set to one or more, all can realize the object of the invention, can realize that recovery damping force regulates in real time according to the vehicle state that jolts, resistance to compression pression remains on very low level, can play preferably damping effect.
In the present embodiment, the elastic reset normally closed structure of described valve member for can under the magnetic flow liquid pressure-acting, opening; The aperture that makes valve member is magnetic flow liquid is flow to the second cavity volume 15 through convection holes 21 by the first cavity volume 26 sectional area size and the big or small proportional variation that is subject to magnetic flow liquid pressure, when being applied to vehicle, can realize that compression damping power regulates in real time according to the vehicle state that jolts, can play preferably damping effect.
In the present embodiment, it is circumferentially uniform along piston head 22 that described convection holes 21 is at least two and each convection holes 21; Make piston head 22 stressed even, avoid piston head 22 to produce the linkage structure that radial component destroys piston rod 4, piston head 22 and cylinder barrel 14 because of unbalance stress, guarantee working life.
In the present embodiment, described valve member is located in the second cavity volume 15, and valve member comprises annular reed 18 and Returnning spring 17, and described annular reed 18 is with piston head 22 coaxial settings and be slidingly connected to vertically piston head 22; Described Returnning spring 17 bullets peak at and are used between piston rod 4 and the reed 18 reed 18 is suppressed in piston head 22 end faces and then sealing convection holes 21; Simple in structure, easily manufactured, when being applied to vehicle, the Returnning spring 17 by adopting certain Young's modulus can corresponding car load and the aperture of the state control pair discharge orifice 21 that jolts accordingly, and is practical.
In the present embodiment, described Returnning spring 17 is the tower spring, i.e. volute spring, and its decrement is large, therefore adopts short tower spring just can realize the larger opening scope of convection holes 21, makes the valve member compact structure, good stability.
In the present embodiment, described piston rod 4 corresponding Returnning springs 17 and annular reed 18 are provided with shell-like block 16; Described shell-like block 16 clamping and positioning are between piston rod 4 and piston head 22, and shell-like block 16 is provided with the flange that is used for supporting Returnning spring 17 that radially protrudes; Annular reed 18 and the 16 outer wall axial sliding fits of shell-like block; Piston head 22 is threaded connection fixing with piston rod 4; Piston head 22 can be structure shown in Figure 1 with the linkage structure of piston rod 4, and namely piston head 22 top axials arrange connecting screw rod, and the axial corresponding connecting screw rod of piston rod 4 lower end edges arranges connecting screw hole; Also can be structure shown in Figure 5, namely piston rod 4 lower ends axially arrange connecting screw rod, and the axial corresponding connecting screw rod of piston head 22 upper end edges arranges connecting screw hole; It also can be structure shown in Figure 6, be that piston rod 4 lower ends axially arrange axial length greater than the long connecting screw rod of piston head 22, piston head 22 vertically corresponding long connecting screw rod arranges connecting through hole, long connecting screw rod is stretched out by connecting through hole and by the attaching nut piston head 22 is locked in piston rod 4, all can realize the object of the invention; Shell-like block 16 is removable is placed in corresponding connecting screw rod or long connecting screw rod location, annular reed 18 is slidingly matched with shell-like block 16, replaceable after the shell-like slider wear, be beneficial to the reduction user cost, can carry out reliable supporting and location to Returnning spring 17 by flange simultaneously, need not at the larger step surface of piston rod 4 processing, be beneficial to the radial dimension that reduces piston rod 4, economize on material, reduce weight and guarantee the second cavity volume 15 capacity, improve the vibration control performance.
In the present embodiment, described field coil 20 be two and two field coils 20 around on the contrary, produce opposite two-way magnetic field, seal in field coil 20 outside gluings after installing field coil 20, field coil 20 and magnetic flow liquid is isolated, to avoid magnetic flow liquid and field coil 20 repeatedly to rub, damage coil, cause short circuit.
In the present embodiment, described MR damper body also comprises the positioning disk 24 that piston rod 4 and piston head 22 is carried out slide-and-guide with cylinder barrel 14 inwalls being used for of being slidingly matched; Positioning disk 24 excircles are fixed with the seal ring 25 that cooperates with cylinder barrel 14 inner wall sealings; Be provided with the damp channel 19 that between the first cavity volume 26 and the second cavity volume 15, flows for for magnetic flow liquid between described piston head 22 and the cylinder barrel 14; Described positioning disk 24 is provided with the through flow hole 23 that is communicated with damp channel 19 and convection holes 21 for the first cavity volume 26, and separately moulding and be fixedly connected with by screw thread with piston head 22 of positioning disk 24 also can be one-body molded with piston head 22; Positioning disk 24 can be tabular or sleeve-like structure, when positioning disk 24 is platy structure, as shown in Figure 1, positioning disk 24 is connected and fixed with the center of piston head 22 coaxial settings and positioning disk 24 and the center of piston head 22, make and form annular groove 30 between positioning disk 24 and the piston head 22, through flow hole 23 axially arranges and is uniform around positioning disk 24 axis, and through flow hole 23 is communicated with damp channel 19 and convection holes 21 by annular groove 30; When positioning disk 24 is sleeve-like structure, as shown in Figure 7, positioning disk 24 is fixedly connected on piston head 22 end faces with the sidewall of piston head 22 coaxial settings and positioning disk 24, the positioning disk endoporus is communicated with each convection holes 21, positioning disk 24 sidewalls are radially offered the by-pass hole 29 that is communicated with damp channel 19 for the positioning disk endoporus, so positioning disk endoporus and by-pass hole 29 are combined to form through flow hole 23; When consisting of damp channel 19, realize being slidingly matched of piston head 22 and cylinder barrel 14, and damping force output is large, abandoned and stretched out the structure that cylinder barrel 14 basal slidings cooperate by piston rod 4 lower ends in the prior art, significantly shortened entire length, reduced the area that is sealed and matched, be beneficial to reduce and leak, guarantee the vibration control performance.
In the present embodiment, described cylinder barrel 14 upper ends are provided with the upper black box that is sealedly attached to piston rod 4 and cylinder barrel 14; Described upper black box comprises upper end cap 6, upper end cap rubber envelope 7, fixing safety pad 13 in Z-shaped card 8, Z-shaped card 9, slide plate 10, oil sealing card 11, oil sealing 12 and the cylinder, can avoid damper generation oil leakage phenomenon when the work by upper black box; Described piston rod 4 upper ends are fixed with end connector 1; Be positioned at end connector 1 lower end and be placed in piston rod 4 outer walls and be provided with the outer safety pad 3 of cylinder, can when damper bears very large external load, protect damper not to be damaged; Described field coil 20 draw wire 2 along the axis setting of piston head 22 and piston rod 4 and by drawing at least part of center hole 5 of drawing wire be used to holding that is provided with of upper end connector 1, piston rod 4 and piston head 22 in the upper end connector 1; Described cylinder barrel 14 lower ends are sealedly connected with lower end connector 28; Be provided with the O shape circle 27 for sealing between lower end connector 28 and the cylinder barrel 14; Described lower end connector 28 is provided with the air bag that is communicated with the first cavity volume 26, can effective compensation piston rod 4 and the volume-variation of caused the first cavity volume 26 of piston head 22 to-and-fro motion; Described lower end connector 28 is connected by rolling or thread seal with cylinder barrel 14, and linkage structure is stable, and easily manufacturing is beneficial to sealing.
In the present embodiment, described cylinder barrel 14 and piston head 22 are made by high permeability material and are also made by high permeability material when positioning disk 24 and piston head 22 are one-body molded; Described shell-like block 16, piston rod 4 and upper black box are made by non-magnet_conductible material and are also made by non-magnet_conductible material when positioning disk 24 independent moulding, can guarantee that the most of magnetic line of force in the field circuit passes damp channel 19, can give full play to vertical magnetic field to the effect of magnetic flow liquid, effectively control the size of damping force, improve control efficiency, reduce power consumption; Described field coil 20 is by the enameled cable coiled, and usability is better.
Explanation is at last, above embodiment is only unrestricted in order to technological scheme of the present invention to be described, although with reference to preferred embodiment the present invention is had been described in detail, those of ordinary skill in the art is to be understood that, can make amendment or be equal to replacement technological scheme of the present invention, and not breaking away from aim and the scope of technical solution of the present invention, it all should be encompassed in the middle of the claim scope of the present invention.

Claims (10)

1. the MR damper of an asymmetric controllable damping characteristic is characterized in that: comprise the MR damper body; Described MR damper body comprises cylinder barrel, piston rod, piston head and is filled in the magnetic flow liquid of inner cavity of cylinder; Described piston head is provided with field coil and piston head and is located in the cylinder barrel and inner cavity of cylinder is divided near the first cavity volume of cylinder barrel lower end with near the second cavity volume of cylinder barrel upper end; Described piston head inside is provided with the convection holes that is communicated in the first cavity volume and the second cavity volume; Described convection holes is provided with for the valve member that magnetic flow liquid is carried out one-way throttle by the second cavity volume to the first cavity volume.
2. the MR damper of asymmetric controllable damping characteristic according to claim 1 is characterized in that: the elastic reset normally closed structure of described valve member for opening under the magnetic flow liquid pressure-acting.
3. the MR damper of asymmetric controllable damping characteristic according to claim 2 is characterized in that: it is circumferentially uniform along piston head that described convection holes is at least two and each convection holes.
4. the MR damper of asymmetric controllable damping characteristic according to claim 3, it is characterized in that: described valve member is located in the second cavity volume, valve member comprises annular reed and Returnning spring, and described annular reed is with the coaxial setting of piston head and be slidingly connected to vertically piston head; Described Returnning spring bullet peaks at and is used between piston rod and the reed reed is suppressed in piston head end face and then sealing convection holes.
5. the MR damper of asymmetric controllable damping characteristic according to claim 4, it is characterized in that: described Returnning spring is the tower spring.
6. the MR damper of asymmetric controllable damping characteristic according to claim 5 is characterized in that: the corresponding Returnning spring of described piston rod and annular reed are provided with the shell-like block; Described shell-like block clamping and positioning is between piston rod and piston head, and the shell-like block is provided with the flange that is used for supporting Returnning spring that radially protrudes; Annular reed and the axial sliding fit of shell-like block outer wall.
7. the MR damper of asymmetric controllable damping characteristic according to claim 6 is characterized in that: described field coil be two and two field coils around on the contrary.
8. the MR damper of asymmetric controllable damping characteristic according to claim 7 is characterized in that: described MR damper body also comprises the positioning disk that piston rod and piston head is carried out slide-and-guide with inner wall of cylinder being used for of being slidingly matched; The positioning disk excircle is fixed with the seal ring that is sealed and matched with inner wall of cylinder; Be provided with the damp channel that between the first cavity volume and the second cavity volume, flows for for magnetic flow liquid between described piston head and the cylinder barrel; Described positioning disk is provided with the through flow hole that is communicated with damp channel and convection holes for the first cavity volume; Separately moulding and be fixedly connected with by screw thread with piston head of positioning disk also can be one-body molded with piston head.
9. the MR damper of asymmetric controllable damping characteristic according to claim 8 is characterized in that: be provided with the upper black box that is sealedly attached to piston rod and cylinder barrel on the described cylinder barrel; Described upper black box comprises upper end cap, upper end cap rubber envelope, the fixing interior safety pad of Z-shaped card, Z-shaped card, slide plate, oil sealing card, oil sealing and cylinder; Described piston rod upper end is fixed with end connector; Be positioned at the end connector lower end and be placed in the piston rod outer wall and be provided with the outer safety pad of cylinder; Described field coil draw wire along the axis setting of piston head and piston rod and by drawing in the upper end connector; Described cylinder barrel lower end is sealedly connected with lower end connector; Described lower end connector is provided with the air bag that is communicated with the first cavity volume; Described lower end connector is connected by rolling or thread seal with cylinder barrel.
10. the MR damper of asymmetric controllable damping characteristic according to claim 9 is characterized in that: described cylinder barrel and piston head are made by high permeability material and are also made by high permeability material when positioning disk and piston head are one-body molded; Described shell-like block, piston rod and upper black box are made by non-magnet_conductible material and are also made by non-magnet_conductible material when the independent moulding of positioning disk; Described field coil is by the enameled cable coiled.
CN201310244075.XA 2013-06-19 2013-06-19 The MR damper of asymmetric controllable damping characteristic Active CN103352956B (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
CN201310244075.XA CN103352956B (en) 2013-06-19 2013-06-19 The MR damper of asymmetric controllable damping characteristic

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN201310244075.XA CN103352956B (en) 2013-06-19 2013-06-19 The MR damper of asymmetric controllable damping characteristic

Publications (2)

Publication Number Publication Date
CN103352956A true CN103352956A (en) 2013-10-16
CN103352956B CN103352956B (en) 2015-09-23

Family

ID=49309354

Family Applications (1)

Application Number Title Priority Date Filing Date
CN201310244075.XA Active CN103352956B (en) 2013-06-19 2013-06-19 The MR damper of asymmetric controllable damping characteristic

Country Status (1)

Country Link
CN (1) CN103352956B (en)

Cited By (25)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103557264A (en) * 2013-11-15 2014-02-05 重庆大学 Condition monitoring based passive magneto rheological vibration damper
CN104989774A (en) * 2015-06-17 2015-10-21 芜湖兴众进出口贸易有限公司 Magnetorheological damper with stepless and adjustable damping force
CN105003588A (en) * 2015-06-17 2015-10-28 芜湖兴众进出口贸易有限公司 Automobile collision magneto-rheological shock absorber
CN105864346A (en) * 2016-06-21 2016-08-17 辽宁工业大学 Piston valve of magnetorheological fluid damper and magnetorheological fluid damper
CN106051026A (en) * 2016-07-26 2016-10-26 江西科技学院 Automobile magneto-rheological damper
CN106133383A (en) * 2014-03-18 2016-11-16 Kyb株式会社 Magnetic viscosity fluid buffer
CN108180250A (en) * 2018-01-22 2018-06-19 华东交通大学 A kind of built-in magnet valve improves the two-wire ring MR damper of damping capacity
CN108368723A (en) * 2015-07-21 2018-08-03 因文图斯工程有限公司 Door component with controllable damping mechanism
CN108691944A (en) * 2018-06-18 2018-10-23 重庆大学 Based on the asymmetric MR damper for squeezing enhancement effect
CN110778636A (en) * 2019-11-26 2020-02-11 重庆大学 Bidirectional independent controllable magneto-rheological damper
CN110869573A (en) * 2017-06-29 2020-03-06 压铸及注塑厂海蒂诗有限责任两合公司 Damper
CN111745572A (en) * 2020-08-06 2020-10-09 重庆大学 Self-adaptive flexible clamp
CN111942095A (en) * 2020-07-27 2020-11-17 江苏大学 Vehicle semi-active suspension with magnetic suspension spring and eddy current damper coupled for new energy vehicle
CN112555328A (en) * 2020-12-14 2021-03-26 重庆大学 Parallel radial magnetorheological valve and shock absorber thereof
CN112984028A (en) * 2021-01-21 2021-06-18 浙江师范大学 Design method of magneto-rheological shock absorber
CN113606277A (en) * 2021-05-25 2021-11-05 上海应用技术大学 Vehicle electrorheological fluid shock absorber based on hydraulic adjusting system
CN114458718A (en) * 2022-01-18 2022-05-10 燕山大学 Anti-settling magneto-rheological vibration absorber for high-pressure hydraulic pipeline system and working process of anti-settling magneto-rheological vibration absorber
CN114483862A (en) * 2022-01-04 2022-05-13 株洲时代新材料科技股份有限公司 Magneto-rheological damper
CN114483863A (en) * 2022-01-27 2022-05-13 株洲时代新材料科技股份有限公司 Magneto-rheological damper
CN114718977A (en) * 2022-05-06 2022-07-08 重庆大学 Magnetorheological hydro-pneumatic spring
CN114877007A (en) * 2022-05-09 2022-08-09 温州大学 Asymmetric damping force vibration absorber piston assembly and magneto-rheological vibration absorber
CN115324982A (en) * 2022-08-26 2022-11-11 中国人民解放军海军工程大学 Self-adaptive hydraulic muffler device
CN115370697A (en) * 2022-08-23 2022-11-22 武汉理工大学 Constant magnetic MR damper with Tesla valve and vibration damper
CN115992860A (en) * 2023-03-20 2023-04-21 泰州市荣贵机械制造有限公司 Adjustable damper
CN116025659A (en) * 2023-01-10 2023-04-28 烟台大学 Self-resetting body-building damper based on magnetorheological material

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060121586A (en) * 2005-05-24 2006-11-29 부경대학교 산학협력단 A damper using magneto-rheological fluid for controlling damping performance non-symmetrically
JP2008215406A (en) * 2007-02-28 2008-09-18 Hitachi Ltd Magnetic fluid damper
CN101915281A (en) * 2010-07-19 2010-12-15 谭和平 Single-rod magnetorheological damper with one-way channel
CN201786985U (en) * 2010-09-26 2011-04-06 华侨大学 Magneto-rheological damper with double-coil
CN202251632U (en) * 2011-10-18 2012-05-30 慈溪市正大车业有限公司 Automobile vibration damper
CN202926944U (en) * 2012-11-20 2013-05-08 株洲联诚集团减振器有限责任公司 Oil damper for railroad rolling stock

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
KR20060121586A (en) * 2005-05-24 2006-11-29 부경대학교 산학협력단 A damper using magneto-rheological fluid for controlling damping performance non-symmetrically
JP2008215406A (en) * 2007-02-28 2008-09-18 Hitachi Ltd Magnetic fluid damper
CN101915281A (en) * 2010-07-19 2010-12-15 谭和平 Single-rod magnetorheological damper with one-way channel
CN201786985U (en) * 2010-09-26 2011-04-06 华侨大学 Magneto-rheological damper with double-coil
CN202251632U (en) * 2011-10-18 2012-05-30 慈溪市正大车业有限公司 Automobile vibration damper
CN202926944U (en) * 2012-11-20 2013-05-08 株洲联诚集团减振器有限责任公司 Oil damper for railroad rolling stock

Cited By (38)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN103557264A (en) * 2013-11-15 2014-02-05 重庆大学 Condition monitoring based passive magneto rheological vibration damper
CN106133383A (en) * 2014-03-18 2016-11-16 Kyb株式会社 Magnetic viscosity fluid buffer
CN104989774A (en) * 2015-06-17 2015-10-21 芜湖兴众进出口贸易有限公司 Magnetorheological damper with stepless and adjustable damping force
CN105003588A (en) * 2015-06-17 2015-10-28 芜湖兴众进出口贸易有限公司 Automobile collision magneto-rheological shock absorber
CN108368723B (en) * 2015-07-21 2020-10-09 因文图斯工程有限公司 Door assembly with controllable damping mechanism
CN108368723A (en) * 2015-07-21 2018-08-03 因文图斯工程有限公司 Door component with controllable damping mechanism
CN105864346A (en) * 2016-06-21 2016-08-17 辽宁工业大学 Piston valve of magnetorheological fluid damper and magnetorheological fluid damper
CN105864346B (en) * 2016-06-21 2018-03-23 辽宁工业大学 A kind of magneto-rheological vibration damper piston valve and magneto-rheological vibration damper
CN106051026A (en) * 2016-07-26 2016-10-26 江西科技学院 Automobile magneto-rheological damper
CN106051026B (en) * 2016-07-26 2018-05-25 江西科技学院 A kind of automobile using MR damper
US11230869B2 (en) 2017-06-29 2022-01-25 Druck- Und Spritzgusswerk Hettich GmbH & Co. KG Damper
CN110869573A (en) * 2017-06-29 2020-03-06 压铸及注塑厂海蒂诗有限责任两合公司 Damper
CN110869573B (en) * 2017-06-29 2021-08-03 压铸及注塑厂海蒂诗有限责任两合公司 Damper
CN108180250A (en) * 2018-01-22 2018-06-19 华东交通大学 A kind of built-in magnet valve improves the two-wire ring MR damper of damping capacity
CN108691944B (en) * 2018-06-18 2019-07-26 重庆大学 Based on the asymmetric MR damper for squeezing enhancement effect
CN108691944A (en) * 2018-06-18 2018-10-23 重庆大学 Based on the asymmetric MR damper for squeezing enhancement effect
CN110778636B (en) * 2019-11-26 2021-04-06 重庆大学 Bidirectional independent controllable magneto-rheological damper
CN110778636A (en) * 2019-11-26 2020-02-11 重庆大学 Bidirectional independent controllable magneto-rheological damper
CN111942095A (en) * 2020-07-27 2020-11-17 江苏大学 Vehicle semi-active suspension with magnetic suspension spring and eddy current damper coupled for new energy vehicle
CN111942095B (en) * 2020-07-27 2022-11-01 槃实科技(深圳)有限公司 Vehicle semi-active suspension with magnetic suspension spring and eddy current damper coupled for new energy vehicle
CN111745572A (en) * 2020-08-06 2020-10-09 重庆大学 Self-adaptive flexible clamp
CN112555328B (en) * 2020-12-14 2022-04-08 重庆大学 Parallel radial magnetorheological valve and shock absorber thereof
CN112555328A (en) * 2020-12-14 2021-03-26 重庆大学 Parallel radial magnetorheological valve and shock absorber thereof
CN112984028A (en) * 2021-01-21 2021-06-18 浙江师范大学 Design method of magneto-rheological shock absorber
CN113606277A (en) * 2021-05-25 2021-11-05 上海应用技术大学 Vehicle electrorheological fluid shock absorber based on hydraulic adjusting system
CN114483862A (en) * 2022-01-04 2022-05-13 株洲时代新材料科技股份有限公司 Magneto-rheological damper
CN114458718B (en) * 2022-01-18 2022-10-18 燕山大学 Anti-settling magneto-rheological shock absorber for high-pressure hydraulic pipeline system and working process of shock absorber
CN114458718A (en) * 2022-01-18 2022-05-10 燕山大学 Anti-settling magneto-rheological vibration absorber for high-pressure hydraulic pipeline system and working process of anti-settling magneto-rheological vibration absorber
CN114483863A (en) * 2022-01-27 2022-05-13 株洲时代新材料科技股份有限公司 Magneto-rheological damper
CN114718977A (en) * 2022-05-06 2022-07-08 重庆大学 Magnetorheological hydro-pneumatic spring
CN114718977B (en) * 2022-05-06 2024-01-26 重庆大学 Magnetorheological oil-gas spring
CN114877007A (en) * 2022-05-09 2022-08-09 温州大学 Asymmetric damping force vibration absorber piston assembly and magneto-rheological vibration absorber
CN114877007B (en) * 2022-05-09 2024-01-05 温州大学 Asymmetric damping force shock absorber piston assembly and magneto-rheological shock absorber
CN115370697A (en) * 2022-08-23 2022-11-22 武汉理工大学 Constant magnetic MR damper with Tesla valve and vibration damper
CN115324982A (en) * 2022-08-26 2022-11-11 中国人民解放军海军工程大学 Self-adaptive hydraulic muffler device
CN115324982B (en) * 2022-08-26 2024-03-26 中国人民解放军海军工程大学 Self-adaptive hydraulic silencing device
CN116025659A (en) * 2023-01-10 2023-04-28 烟台大学 Self-resetting body-building damper based on magnetorheological material
CN115992860A (en) * 2023-03-20 2023-04-21 泰州市荣贵机械制造有限公司 Adjustable damper

Also Published As

Publication number Publication date
CN103352956B (en) 2015-09-23

Similar Documents

Publication Publication Date Title
CN103352956A (en) Magneto-rheological damper with asymmetrical controllable damping characteristic
CN104315073A (en) Variable-stiffness variable-damping shock absorber based on magnetorheological damper
CN206429608U (en) A kind of vibration damper with adjustable damping
CN106438813B (en) A kind of vehicle shock absorber
CN103423364A (en) Hydraulic damper with adjustable damping
CN104309438A (en) Vehicle suspension with multiple working conditions
CN203670591U (en) Adjustable electromagnetic shock absorber
CN108561486A (en) A kind of novel anti-settling magnetic rheological liquid damper
CN105909722A (en) Damping-adjustable shock absorber using magnetorheological fluid
CN105003585A (en) Variable-section piston type magnetorheological vibration reducer
CN105240444A (en) Magneto-rheological shock absorber based on parallel structure
CN106015436B (en) A kind of rank becomes magneto-rheological damper
CN104421371A (en) High-pressure oil-control variable damping absorber
CN103423363A (en) Hydraulic damper with actively-adjustable damping
CN108302149A (en) Using external coil and the coefficient double-cylinder type magneto-rheological vibration damper of permanent magnet
CN105889397A (en) Single-piston-rod, double-cylinder and double-coil magneto-rheological absorber
CN2809329Y (en) Magnetic vibration damper
CN201037520Y (en) Magnetorheological fluids vibration damper for automobile engine
CN207454650U (en) A kind of combined type MR vibration damper
CN103758913A (en) Mixed mode magneto-rheological shock absorber
CN204852153U (en) Magnetorheological suspensions shock absorber with highly resistance tensile properties
CN102927191A (en) Coil internally-installed type magnetorheological damper with oil needle
CN104963983A (en) Coil externally-wrapping magnetorheological fluid damper
CN204372028U (en) Amplitude is correlated with damping characteristic vibration damper
CN103291827B (en) Valve-plate-rigidity-adjustable damper piston

Legal Events

Date Code Title Description
C06 Publication
PB01 Publication
C10 Entry into substantive examination
SE01 Entry into force of request for substantive examination
C14 Grant of patent or utility model
GR01 Patent grant