CN114877007B - Asymmetric damping force shock absorber piston assembly and magneto-rheological shock absorber - Google Patents
Asymmetric damping force shock absorber piston assembly and magneto-rheological shock absorber Download PDFInfo
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- CN114877007B CN114877007B CN202210498441.3A CN202210498441A CN114877007B CN 114877007 B CN114877007 B CN 114877007B CN 202210498441 A CN202210498441 A CN 202210498441A CN 114877007 B CN114877007 B CN 114877007B
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- 238000013016 damping Methods 0.000 title claims abstract description 109
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 52
- 230000035939 shock Effects 0.000 title claims abstract description 49
- 238000007667 floating Methods 0.000 claims abstract description 19
- 239000012530 fluid Substances 0.000 claims description 22
- 238000007789 sealing Methods 0.000 claims description 22
- 238000003825 pressing Methods 0.000 claims description 14
- 238000000034 method Methods 0.000 claims description 12
- 230000002093 peripheral effect Effects 0.000 claims description 11
- 230000008569 process Effects 0.000 claims description 7
- 239000011261 inert gas Substances 0.000 claims description 3
- 238000007906 compression Methods 0.000 abstract description 38
- 230000006835 compression Effects 0.000 abstract description 38
- 230000005291 magnetic effect Effects 0.000 abstract description 18
- 230000005426 magnetic field effect Effects 0.000 abstract description 3
- 239000000725 suspension Substances 0.000 description 7
- 238000010586 diagram Methods 0.000 description 6
- 238000005265 energy consumption Methods 0.000 description 6
- 238000004088 simulation Methods 0.000 description 6
- 238000011084 recovery Methods 0.000 description 4
- 230000009471 action Effects 0.000 description 3
- 230000005284 excitation Effects 0.000 description 3
- 230000008859 change Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000005096 rolling process Methods 0.000 description 2
- 230000003313 weakening effect Effects 0.000 description 2
- 230000004888 barrier function Effects 0.000 description 1
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000009977 dual effect Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 239000010720 hydraulic oil Substances 0.000 description 1
- 230000004044 response Effects 0.000 description 1
- 230000002441 reversible effect Effects 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
- F16F9/3207—Constructional features
- F16F9/3214—Constructional features of pistons
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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
- F16F9/36—Special sealings, including sealings or guides for piston-rods
- F16F9/368—Sealings in pistons
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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
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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
Abstract
The invention relates to an asymmetric damping force shock absorber piston assembly and a magnetorheological shock absorber adopting the piston assembly, the shock absorber is of a single-cylinder single-output rod structure, a piston assembly and a floating piston are arranged in a working cylinder, and the piston assembly is fixedly connected with one end of a hollow piston rod, and the shock absorber has the advantages that: the damping force output of the integral shock absorber is controlled by adjusting the magnetic field intensity of the exciting coil and the relative position of the middle baffle plate and the piston sleeve, and the adjustable interval of the damping force is large; the compression and restoration damping force can be adjusted according to the actual working conditions, and the asymmetric mechanical properties are achieved; the double coils are electrified with different current, so that the magnetic field effect of the middle parts of the two coils is effectively utilized, and the damping force output range of the shock absorber is further enlarged.
Description
Technical Field
The invention relates to the field of vibration absorbers, in particular to an asymmetric damping force vibration absorber piston assembly and a magneto-rheological vibration absorber.
Background
In the suspension system, because the elastic element is impacted to generate vibration, the shock absorber is arranged in parallel with the elastic element in the suspension to improve the running smoothness of the automobile, and the shock absorber is mostly a hydraulic shock absorber in order to attenuate vibration.
The damping process of the shock absorber can be divided into two stages of compression damping and rebound damping, as the name implies, the compression damping is the damping force which is resisted when the shock absorber piston descends, the corresponding rebound damping force is the damping force which is resisted when the piston ascends, different road conditions correspond to different motion speeds of the shock absorber piston in the running process of the automobile, for example, when the shock absorber piston passes through a bump road surface, a deceleration strip and a bumpy road surface, the vehicle impacts at a high speed, the piston moves at a medium speed, at the moment, the shock absorber damping force mainly influences the smoothness of the automobile, the smaller the damping coefficient is, the better the smoothness is, the compression damping force has a larger influence on the smoothness than the rebound damping force, the shock absorber piston moves at a low speed when the vehicle turns around or encounters a ditch, at the moment, the shock absorber damping coefficient mainly influences the rolling degree of the automobile, the rolling degree of the vehicle can be reduced by increasing the shock absorber damping coefficient, and the compression damping force and the rebound damping force of the existing shock absorber cannot be adjusted in a self-adaptive mode according to the working conditions.
The main current vibration damper in the market is divided according to the angle of damping medium, the vibration damper mainly comprises a hydraulic vibration damper, a pneumatic vibration damper and a magneto-rheological vibration damper, wherein the magneto-rheological vibration damper can realize the adjustment of the damping force of the vibration damper by controlling the reversible conversion of magneto-rheological fluid between Newton fluid and Bingham fluid, has the advantages of high response speed, continuous adjustable damping force and the like, and is very suitable for being applied to semi-active suspensions of automobiles. The damping force is adjustable, so that the damper has better adjustment performance, and the research of the magnetorheological damper is becoming a hot problem in the field of automobile suspensions.
At present, the structural design of the magnetorheological damper is mainly based on the purpose of increasing the damping force of the damper, the maximum damping force of the magnetorheological damper is increased, and the minimum damping force of the magnetorheological damper is also increased, and when the piston moves at a high speed, better vehicle smoothness can be brought by smaller damping force, particularly compression damping force. While the low compression and high restoration damping force proportioning mode brings better vehicle smoothness and can ensure higher energy consumption efficiency when the damper moves at a high speed, the magneto-rheological damper structure with asymmetric compression and restoration damping force of the damper is freshly researched, and therefore, a novel magneto-rheological damper structure capable of solving the problems is needed.
Disclosure of Invention
The technical problem to be solved by the invention is to provide an asymmetric damping force damper piston assembly which can be used for a hydraulic damper and a magnetorheological damper and the magnetorheological damper working by adopting the piston, wherein the asymmetric damping force damper piston assembly is used for realizing the asymmetry of compression damping force and restoring damping force, so that a suspension carrying the magnetorheological damper can give consideration to the driving smoothness of a bump road surface and the low side inclination in turning, and simultaneously the problem that the current magnetorheological damper increases the minimum damping force while increasing the maximum damping force in structural design is solved, and the damping force adjustable range of the magnetorheological damper is enlarged.
In order to achieve the above purpose, the present invention provides the following technical solutions: the utility model provides an asymmetric damping force shock absorber piston subassembly, includes piston rod and the piston body of being connected with the piston rod, its characterized in that: the piston body comprises a piston sleeve and an intermediate baffle arranged in the piston sleeve, wherein the two axial ends of the piston sleeve corresponding to the intermediate baffle are respectively provided with an upper pressing plate and a bottom plate, at least one through hole corresponding to the axial position is respectively formed in the upper pressing plate and the bottom plate, two layers of fan-shaped inner vortex blocks are arranged on the two axial sides of the piston sleeve corresponding to the intermediate baffle, at least one inner gap is reserved between the inner vortex blocks with the same cross section, the inner gap corresponds to the through hole, a rotating space for the intermediate baffle to rotate around an inner shaft is formed between the two inner vortex blocks corresponding to the axial direction, at least one outer vortex block and an outer gap are formed on the outer peripheral surface of the intermediate baffle, a fan-shaped annular gap is reserved between the outer vortex blocks and the inner vortex blocks, damping channels for media to pass through the two axial ends of the piston body and are formed between the through holes and the inner gap, reset elastic pieces are arranged on the intermediate baffle towards one end of the bottom plate, when the reset elastic pieces are in a normal state, the reset elastic pieces stay on the outer vortex blocks, and the reset elastic pieces are driven by the reset elastic pieces to rotate around the inner vortex blocks, and the peripheral gap is increased by the aid of the peripheral force of the intermediate baffle, and when the peripheral flow velocity of the intermediate baffle is increased by the peripheral force of the intermediate baffle and the peripheral force of the intermediate baffle is increased.
By adopting the technical scheme, the hydraulic damper or the magneto-rheological damper can be suitable for the hydraulic damper or the magneto-rheological damper, when the medium flowing in through the bottom plate flows through the round corners at the lower side of the middle baffle, circumferential tangential force is generated on the middle baffle, the direction of the force is opposite to the pretightening force applied to the middle baffle by the reset elastic piece, the faster the compression stroke speed of the damper is, the larger the force applied to the middle baffle is, when the speed exceeds a set threshold value, the tangential force is larger than the pretightening force applied by the reset elastic piece, the middle baffle rotates around the shaft, so that the positions of the outer notch, the inner notch and the through hole are corresponding to form a damping channel with large cross section area and small damping force, when the reset stroke or the compression speed does not reach the set threshold value, the damper is reset under the pretightening force action of the reset elastic piece, the positions of the inner notch and the outer spoiler are corresponding to form small cross section area by matching with the sector annular gap, when the piston component is applied to the shock absorber, only a certain speed between a high speed and a low speed in the shock absorber is selected as a speed threshold value, so that the smoothness and the higher energy consumption efficiency of the automobile when the automobile passes through a bump road surface and other bumpy road surfaces are realized, the lower side inclination of the automobile can be ensured when the automobile turns around a barrier or meets a ditch working condition, the compression force and the restoring force of the shock absorber can be independently controlled, the condition that the required damping force value is unequal under the compression and restoring working conditions, particularly when the restoring force is larger than the working condition requirement of the compression force, the problem that the shock absorber in the prior art is difficult to adaptively adjust the limitation of the compression force and the restoring force according to the working condition is solved, the independence of the compression force and the restoring force is realized, and meanwhile, when the piston component is applied to the magneto-rheological shock absorber, the current joint control can be matched, the suspension with the magnetorheological damper can give consideration to the driving smoothness of a bump road surface and the low side inclination during turning, meanwhile, the problem that the current magnetorheological damper increases the minimum damping force while increasing the maximum damping force during structural design is solved, and the damping force adjustable section of the magnetorheological damper is enlarged, wherein the reset elastic piece can be an elastic piece such as a spring, a torsion spring, rubber and the like.
The asymmetric damping force shock absorber piston assembly described above may further be configured to: a limiting block is arranged between the two axially corresponding inner vortex blocks, the limiting block is arranged in the rotating space and is not arranged in the inner notch, when the reset elastic piece is in a normal state, the reset elastic piece drives the rounding corner to abut against the limiting block, when the flow speed of the medium is increased, the circumferential force generated by the middle baffle is higher than the pretightening force of the reset elastic piece, the middle baffle rotates around the shaft to enable the conduction surface of the outer notch and the inner notch to be gradually increased until one end, far away from the rounding corner, of the outer vortex block abuts against the limiting block.
By adopting the technical scheme, the limiting block is arranged to limit the rotation range of the middle baffle driven by the reset elastic piece, so that the phenomenon that the reset elastic piece cannot reset due to excessive deformation or the pretightening force is excessive is avoided, the reset is excessive, and the control force of the middle baffle to the damping channel is further improved.
The asymmetric damping force shock absorber piston assembly described above may further be configured to: the reset elastic piece is a torsion spring, and the torsion spring is arranged on the peripheral surface of the middle baffle plate, so that the torsion arm is propped against the middle baffle plate, and the upper torsion spring foot and the lower torsion spring foot are respectively clamped in the through holes of the upper pressing plate and the bottom plate.
By adopting the technical scheme, the reset elastic piece is a torsion spring, and vehicles under different working conditions are adapted by selecting torsion springs with different pretightening forces.
The asymmetric damping force shock absorber piston assembly described above may further be configured to: the quantity of through-holes on top board and the bottom plate is 3, and the through-hole be with the corresponding arc through-hole of interior breach, the quantity of interior breach is 3, and then two-layer all cuts apart into 3 interior vortex piece about with interior vortex piece, the outer vortex piece of middle baffle is 3 with outer breach quantity, the quantity of stopper is 3, through-hole, interior vortex piece, outer vortex piece all encircle the piston rod equidistance and distribute, make 3 damping passageway between through-hole and the interior breach.
By adopting the technical scheme, when the structural components in the piston body are the above quantities, the piston sleeve and the middle baffle are of 3 fan-shaped structures which are mutually corresponding or arranged in a staggered manner, so that 3 damping channels are realized, the self-adaptive adjustment is realized through the torsion spring, the problem that the minimum damping force is increased when the maximum damping force is increased in the structural design of the current magnetorheological damper is solved, the damping force adjustable section of the magnetorheological damper is enlarged, and the problem that the service life of the damper is too short due to the asymmetric damping force in the single channel is avoided.
The asymmetric damping force shock absorber piston assembly described above may further be configured to: the piston rod is internally provided with a piston rod wire hole, the piston body is internally provided with a coil assembly, the coil assembly comprises two coil grooves and two exciting coils, the coil grooves are arranged on two axial sides of the middle baffle, the exciting coils are wound on the coil grooves, and the medium is magnetorheological fluid.
By adopting the technical scheme, when the piston assembly is applied to the magnetorheological damper, the coil assembly is only required to be added in the piston body, so that the exciting coil is wound on the coil groove and is connected with a power supply through the piston rod hole, the vehicle ECU is convenient to control current to work, and the semi-active suspension damping is realized by matching with magnetorheological fluid.
The utility model provides a magnetorheological damper, includes working cylinder and piston assembly, piston assembly is asymmetric damping force damper piston assembly, install the seal cover between piston rod and the working cylinder, and then form airtight chamber with the working cylinder, airtight chamber corresponds the axial both sides of piston body and all fills magnetorheological fluid, magnetorheological fluid circulates in piston body both sides through damping passageway.
By adopting the technical scheme, the piston component is an asymmetric damping force shock absorber piston component, when magnetorheological fluid flowing in through the bottom plate flows through the round corners at the lower side of the middle baffle in the compression stroke of the shock absorber, circumferential tangential force is generated on the middle baffle, the direction of the force is opposite to the direction of the pretightening force applied to the middle baffle by the torsion spring, the faster the compression stroke speed of the shock absorber is, the larger the force applied to the middle baffle by the magnetorheological fluid is, when the speed exceeds a set threshold value, the tangential force is larger than the pretightening force applied by the torsion spring, the middle baffle rotates around the shaft until the round corner-free side contact limiting block, at the moment, the positions of the outer notch, the inner notch and the arc-shaped through hole correspond, the cross sectional area is large, the damping force is small, when the restoring stroke or the compression speed does not reach the set threshold value, the magnetorheological shock absorber is reset to the round corner-end contact limiting block under the pretightening force of the torsion spring, the inner notch corresponds to the outer vortex block, the sector ring has small gap cross section area and large damping force, so that the magnetorheological damper has asymmetric mechanical property, a certain speed between high speed and low speed in the damper is selected as a speed threshold value, the automobile smoothness and higher energy consumption efficiency when the automobile passes through bump road surfaces and other bumpy road surfaces are ensured, the automobile can be ensured to have lower roll degree when in obstacle-detouring or ditch-meeting working conditions, the damping force of magnetorheological fluid in a recovery channel or a compression channel can be changed through controlling current, the compression force and the recovery force of the damper can be independently controlled, and under the conditions that the required damping force values are unequal under compression and recovery working conditions, particularly when the recovery force is greater than the working condition requirement of the compression force, the problems that in the prior art, the shock absorber is difficult to adaptively adjust the limitation of the compression force and the restoring force according to working conditions and the control algorithm of the magnetorheological damper is extremely complex are solved, and independent and combined control of the compression force and the restoring force is realized.
The magnetorheological damper may further be configured as follows: the directions of the currents which are led in by the two exciting coils are opposite.
By adopting the technical scheme, the two coils are led with different currents, so that the magnetic field effect of the middle parts of the two coils can be more fully utilized, and compared with the condition of leading in the same current, the adjustable damping force interval is larger.
The magnetorheological damper may further be configured as follows: the one end that the working cylinder was kept away from the seal cover is equipped with the floating piston, the floating piston passes through the floating piston spring and is connected with the working cylinder, it has high-pressure inert gas to fill between floating piston and the working cylinder bottom.
By adopting the technical scheme, the air chamber formed by the movable piston and the working cylinder is used for compensating the total volume change in the working cylinder caused by different lengths of the piston rod extending into the working cylinder.
The magnetorheological damper may further be configured as follows: the coil groove sets up in the axial both sides of middle baffle respectively to restrict in the piston is originally internal through top board, bottom plate and piston sleeve cooperation, wire connecting hole has all been seted up on the coil groove, wire connecting hole and piston rod wire hole switch on, interior vortex piece upside and the interior vortex piece downside of lower floor all process there is the chamfer.
By adopting the technical scheme, the coil grooves are respectively arranged on two sides of the middle baffle, and the lead connecting holes are formed to be communicated with the guide holes of the piston rod, so that the excitation coils are conveniently installed and connected, the magnetorheological fluid is prevented from contacting the excitation coils, the stability is improved, meanwhile, the two excitation coils realize the double-coil different-direction current, the damping force adjustable interval of the magnetorheological damper is further enlarged, and chamfers are processed on the upper side of the inner spoiler and the lower side of the lower layer inner spoiler simultaneously for the installation of the torsion spring, and the stability of the torsion spring during installation is improved.
The magnetorheological damper may further be configured as follows: the clamping groove for installing the sealing sleeve is formed in the upper end of the working cylinder, connecting holes are formed in the circle centers of the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle, the diameters of the connecting holes are equal to those of the piston rod, a fixed sealing structure is arranged between the sealing sleeve and the working cylinder, and sliding sealing structures are arranged between the sealing sleeve and the piston rod and on the inner walls of the piston assembly, the floating piston and the working cylinder.
By adopting the technical scheme, the sealing sleeve is matched with the clamping groove of the working cylinder to form a closed cavity in the working cylinder, so that overflow of magnetorheological fluid is avoided, and the piston rod is inserted into the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle plate through the connecting hole, so that the piston body is connected with the piston rod.
Compared with the prior art, the invention has the beneficial effects that:
1. according to the invention, the effects of compression and restoring of the damping force asymmetry of the shock absorber can be realized through the cooperation between the tangential force along the circumference of the chamfer angle of the middle baffle and the pretightening force of the torsion spring, the asymmetric damping can be generated in a self-adaptive manner, the smoothness and the high energy consumption efficiency of the automobile passing through bump road surfaces and other bumpy road surfaces can be ensured, the lower roll of the automobile can be ensured during turning, and the damping force adjustable interval can be improved through two modes of mechanical adjustment and electromagnetic adjustment of the middle baffle when the shock absorber is applied to a magneto-rheological shock absorber.
2. According to the invention, the length and the cross section area of the damping channel are changed due to the rotation of the middle baffle, so that the minimum damping force is reduced, the maximum damping force is improved, and the damping force adjustable interval of the shock absorber is enlarged.
3. According to the invention, the two groups of coils are connected with exciting coils with opposite current directions and are compared with the exciting coils with the same current direction, and the magnetic field intensity at the outer sides of the two coils is weakened under the action of opposite magnetic fields, but the magnetic field intensity at the middle area of the two coils is strengthened under the action of the magnetic field with the same direction. The adjustable range of the magnetic field intensity is increased, and the damping force adjustable range of the magnetorheological damper is further enlarged.
The invention is further described below with reference to the accompanying drawings.
Drawings
Fig. 1 is a cross-sectional view of a piston assembly according to embodiment 1 of the present invention.
Fig. 2 is a schematic diagram of the components of a piston assembly according to embodiment 1 of the present invention.
Fig. 3 is a schematic structural diagram of a piston body according to embodiment 1 of the present invention.
Fig. 4 is a schematic structural view of a piston sleeve according to embodiment 1 of the present invention.
FIG. 5 is a schematic view showing the relative positions of the intermediate baffle and the piston sleeve when the intermediate baffle rotates to a low damping condition in accordance with embodiment 1 of the present invention.
FIG. 6 is a schematic view showing the relative positions of the intermediate baffle and the piston sleeve when the intermediate baffle is rotated to a high damping condition in accordance with embodiment 1 of the present invention.
FIG. 7 is a graph showing the media trend of the intermediate baffle of example 1 of the present invention when the intermediate baffle is rotated to a low damping condition.
FIG. 8 is a graph showing the media trend of the intermediate baffle of example 1 of the present invention when the intermediate baffle is rotated to a high damping condition.
FIG. 9 is a cross-sectional view of a magnetorheological damper in accordance with example 2 of the present invention.
FIG. 10 is a schematic diagram of a two-dimensional simulation of example 2FEMM (Finite Element Method Magnetics) of the present invention.
Fig. 11 is a schematic diagram of FEMM simulation results of the magnetic field distribution in the piston when two coils are energized with current in the same direction under the condition of large damping in embodiment 2 of the present invention.
Fig. 12 is a schematic diagram of FEMM simulation results of the magnetic field distribution in the piston when two coils are energized with different currents in the case of large damping according to embodiment 2 of the present invention.
Detailed Description
The following description of the embodiments of the present invention will be made clearly and completely with reference to the accompanying drawings, in which it is apparent that the embodiments described are only some embodiments of the present invention, but not all embodiments. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.
In the description of the present invention, it should be noted that the directions or positional relationships indicated by the terms "upper", "lower", "inner", "outer", "front", "rear", "both ends", "one end", "the other end", etc. are based on the directions or positional relationships shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the devices or elements referred to must have a specific direction, be configured and operated in the specific direction, and thus should not be construed as limiting the present invention. Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying relative importance.
In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "mounted," "provided," "connected," and the like are to be construed broadly, and may be fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium, and can be communication between two elements. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.
Example 1
As shown in fig. 1-8, the piston assembly of the asymmetric damping force shock absorber comprises a piston rod 1 and a piston body 4 connected with the piston rod 1, the piston body 4 comprises a piston sleeve 42 and an intermediate baffle 43 arranged in the piston sleeve 42, an upper pressing plate 41 and a bottom plate 12 are respectively arranged at the two axial ends of the piston sleeve 42 corresponding to the intermediate baffle 43, three arc-shaped through holes 121 corresponding to the axial positions are respectively arranged on the upper pressing plate 41 and the bottom plate 12, two layers of fan-shaped inner spoiler 423 are arranged at the two axial sides of the piston sleeve 4 corresponding to the intermediate baffle 43, three inner notches 424 are respectively arranged between the inner spoiler 423 with the same cross section, the upper layer and the lower layer of the inner spoiler 423 are respectively divided into three inner spoiler 423, the inner notch 424 corresponds to the position of the arc-shaped through holes 121, a rotating space a for the intermediate baffle to rotate around the piston rod 1 is formed between the two axially corresponding inner spoiler 423, the outer circumferential surface of the middle baffle 43 is provided with three outer spoiler 431 and three outer notches 433, fan-shaped annular gaps 48 are reserved between the outer spoiler 431 and the inner spoiler 423, the arc-shaped through holes 121, the inner spoiler 423 and the outer spoiler 431 are all distributed around the piston rod 1 at equal intervals, three damping channels b for medium to pass through the two axial ends of the piston body 4 and further conduct are formed between the arc-shaped through holes 121 and the inner notches 424, one end of the outer spoiler 431, facing the bottom plate 12, of the outer spoiler 431 is provided with a chamfer 432, the middle baffle 43 is provided with a torsion spring 45, the torsion spring 45 is arranged on the outer circumferential surface of the middle baffle 43, the torsion arm 451 is abutted against the middle baffle 43, the upper torsion spring leg 452 and the lower torsion spring leg 452 are respectively clamped in the arc-shaped through holes 121 (411) of the upper pressing plate 41 and the bottom plate 12, when the torsion spring 45 is in a normal state, the torsion spring 45 drives the outer vortex blocks 431 to stay on the damping channel b, when the flow speed of a medium is increased to enable the circumferential force generated by the middle baffle 43 to be higher than the pretightening force of the torsion spring 45, the middle baffle 43 rotates around a shaft to enable the conduction surface of the outer gap 433 and the inner gap 424 to be gradually increased, a limiting block 422 is arranged between the two axially corresponding inner vortex blocks 423, the number of the limiting blocks 422 is three, the limiting block 422 is arranged in a rotating space a and is not arranged in the inner gap 424, when the torsion spring 45 is in a normal state, the torsion spring 45 drives the rounding 432 to be abutted against the limiting block 422, when the flow speed of the medium is higher than the pretightening force of the torsion spring 45, the middle baffle 43 rotates around the shaft to enable the conduction surface of the outer gap 433 and the inner gap 424 to be gradually increased until one end of the outer vortex block 431 far away from the rounding 432 is abutted against the limiting block 422, and the piston assembly can be suitable for a hydraulic damper and a magnetorheological damper, namely the medium can be used as hydraulic oil or a magnetorheological fluid, so that asymmetric damping is generated in a self-adapting mode, but when the hydraulic damper is used on the hydraulic damper, the hydraulic damper can be independently controlled and the compression force is not required to be adjusted, the compression force is only can be adjusted to be different from the compression force of the damping channel, and the compression force is difficult to be adjusted to be in a compression force or the compression force is different from the compression force, and the compression force is required to be adjusted.
Example 2
As shown in fig. 1-10, a magnetorheological damper comprises a working cylinder 3 and a piston assembly, wherein the piston assembly is an asymmetric damping force damper piston assembly, a sealing sleeve 2 is installed between a piston rod 1 and the working cylinder 3, the working cylinder is further formed into a closed cavity c, magnetorheological fluid is filled at two axial sides of the piston body 4 corresponding to the closed cavity c, the magnetorheological fluid circulates at two sides of the piston body 4 through a damping channel b, a piston rod wire hole 11 is formed in the piston rod 1, a coil assembly is arranged in the piston body 4, the coil assembly comprises two coil grooves 46 and two exciting coils 44, the coil grooves 46 are installed at two axial sides of a middle baffle 43 and are limited in the piston body 4 through matching of an upper pressing plate 41, a bottom plate 12 and a piston sleeve 42, the exciting coils 44 are wound on the coil grooves 46, the two exciting coils 44 are opposite in current flowing directions, one ends of the working cylinder 3 far away from the sealing sleeve 2 are provided with floating pistons 5, the floating pistons 5 are connected with the working cylinder 3 through floating piston springs 6, the upper and lower ends of the floating pistons 5 are provided with the upper and lower air guide wire holes 423, and the lower air guide holes 423 are connected with the upper and lower air guide holes 461 are formed in the upper and lower air guide holes 11 and the lower air guide holes 423 are formed in the upper and the lower air guide holes 423.
As shown in fig. 9, the magnetorheological damper with asymmetric mechanical characteristics of the invention is characterized in that magnetorheological fluid is filled between the piston body 4 and the sealing sleeve 2 and between the piston body 4 and the floating piston 5, high-pressure inert gas is filled between the floating piston 5 and the bottom of the working cylinder 3, and an air chamber formed by the floating piston 5 and the working cylinder 3 is used for compensating the total volume change in the working cylinder 3 caused by the difference of the extension lengths of the piston rod 1 into the working cylinder 3.
As shown in fig. 3, 4 and 9, the upper end of the working cylinder 3 is provided with a clamping groove for installing the sealing sleeve 2, an upper pressing plate 41, a coil groove 46 and a connecting hole 47 are respectively arranged at the center of a circle on the middle baffle 43, the diameter of the connecting hole 47 is equal to that of the piston rod 1, the connecting hole is used for installing the piston body 4, the sealing sleeve 2 and the working cylinder 3 are fixedly sealed, the sealing sleeve 2 and the piston rod 1 are fixedly sealed, the piston body 4, the floating piston 5 and the inner wall of the working cylinder 3 are slidably sealed, and the sealing sleeve 2 also plays a guiding role on the axial movement of the piston rod 1.
As shown in fig. 4-8, the upper side of the upper inner spoiler 423 and the lower side of the lower inner spoiler 423 are both provided with chamfers 421 for mounting the torsion spring 45, the right side below the outer spoiler 431 of the middle baffle 43 is provided with chamfers 432, in the compression stroke of the damper, when magnetorheological fluid flowing in through the bottom plate 12 flows through the chamfers 432 on the lower side of the middle baffle 43, a circumferential tangential force is generated on the middle baffle 43, the direction of the force is opposite to the direction of the pretightening force applied to the middle baffle 43 by the torsion spring 45, the faster the compression stroke speed of the damper is, the larger the force applied to the middle baffle 43 is, when the speed exceeds a set threshold value, the tangential force is larger than the pretightening force applied by the torsion spring 45, the middle baffle 43 rotates around the shaft to the non-filleted side contact limiting block 422, at this time, the outer notch 433, the inner notch 424 and the arc through hole position correspond, and the magnetorheological fluid damping channel 47 are in the path, through the bottom plate arc through hole 121, enter the first inner notch 433, enter the second inner notch 424, flow out through the upper arc channel 411, the length of the whole damping channel 47 is short, and the whole damping force is as shown in fig. 3 and small. When the restoring stroke or the compression speed does not reach the set threshold, the magnetorheological damper is reset under the pretightening force of the torsion spring 45 to the rounded-angle-shaped contact limiting block 422, and at the moment, the inner notch 424 and the outer disturbance flow block 431 correspond to each other, the magnetorheological fluid damping channel 47 enters the first-layer notch 424 through the bottom plate arc-shaped through hole 121, then enters the outer notch 433 through the fan-shaped ring gap 48, enters the second-layer notch 424 through the second-layer fan-shaped ring gap 48, and flows out through the upper pressing plate arc-shaped channel 411, the length of the integral damping channel 47 is long, the cross section area of the fan-shaped ring gap 48 is small, and the damping force is large, as shown in fig. 6. The structure of the invention has asymmetric mechanical characteristics, and a certain speed between high speed and low speed in the shock absorber is selected as a speed threshold value, so that the automobile has smoothness and higher energy consumption efficiency when passing through bumpy roads such as bump roads, and the automobile can be ensured to have lower side inclination when turning around obstacles or meeting a ditch.
As shown in fig. 10-12, the present invention utilizes FEMM simulation software to simulate the magnetic field distribution of the dual coils in different current directions. The existing model is simplified under the condition that the simulation result is not affected, and a specific simulation two-dimensional diagram is shown in fig. 10. The number of turns of the coil is set to be 100, the total number of the two groups of coils is 200, the current is 2A, and the simulation results are shown in fig. 11 and 12. As is evident from the magnetic field pattern, when current is applied in the same direction, the two coils act in opposite directions between the coils, i.e. in the middle baffle 43 of the figure, and the strength of the magnetic field is weakened, so that the degree of weakening is serious. The magnetic fields of the upper side and the lower side of the two coils act in the same direction, and the magnetic field strength is enhanced. When the opposite current is led, the magnetic fields generated by the two coils at the middle baffle plate 43 in the figure act in the same direction between the coils, the magnetic field intensity is enhanced, the magnetic fields on the upper side and the lower side of the two coils act in opposite directions, the magnetic field intensity is weakened, and the weakening degree is slight. It can be concluded that the bi-coil passing different current can more fully utilize the magnetic field effect of the middle parts of the two coils, and compared with the condition of passing the same current, the adjustable damping force interval is larger.
In summary, the magneto-rheological shock absorber with asymmetric mechanical characteristics provided by the invention realizes asymmetric structural design of compression damping force and restoring damping force; the magnetorheological damper structure can better ensure the driving smoothness and high energy consumption efficiency of the automobile when passing through a bump road surface or a bump road surface; the vehicle can be ensured to have lower roll degree when the vehicle turns around the obstacle or meets the working condition of a ditch; the adjustable damping force interval is further increased by adopting a method of leading in different current through double coils.
It should be noted that in this document, terms such as "comprises," "comprising," or any other variation thereof, are intended to cover a non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements does not include only those elements but may include other elements not expressly listed or inherent to such process, method, article, or apparatus. Without further limitation, an element defined by the phrase "comprising one … …" does not exclude the presence of other like elements in a process, method, article, or apparatus that comprises the element.
It will be evident to those skilled in the art that the invention is not limited to the details of the foregoing illustrative embodiments, and that the present invention may be embodied in other specific forms without departing from the spirit or essential characteristics thereof. The present embodiments are, therefore, to be considered in all respects as illustrative and not restrictive, the scope of the invention being indicated by the appended claims rather than by the foregoing description, and all changes which come within the meaning and range of equivalency of the claims are therefore intended to be embraced therein. Any reference sign in a claim should not be construed as limiting the claim concerned.
Claims (9)
1. The utility model provides an asymmetric damping force shock absorber piston subassembly, includes piston rod and the piston body of being connected with the piston rod, its characterized in that: the piston body comprises a piston sleeve and an intermediate baffle arranged in the piston sleeve, wherein the two axial ends of the piston sleeve corresponding to the intermediate baffle are respectively provided with an upper pressing plate and a bottom plate, at least one through hole corresponding to the axial position is respectively formed in the upper pressing plate and the bottom plate, two layers of fan-shaped inner vortex blocks are arranged on the two axial sides of the piston sleeve corresponding to the intermediate baffle, at least one inner gap is reserved between the inner vortex blocks with the same cross section, the inner gap corresponds to the through hole, a rotating space for the intermediate baffle to rotate around an inner shaft is formed between the two inner vortex blocks corresponding to the axial direction, at least one outer vortex block and an outer gap are arranged on the outer peripheral surface of the intermediate baffle, a fan-shaped annular gap is reserved between the outer vortex blocks and the inner vortex blocks, damping channels for media to pass through the two axial ends of the piston body and are formed between the through holes and the inner gap, reset elastic pieces are arranged on the intermediate baffle, when the reset elastic pieces are in a normal state, the reset elastic pieces stay on the outer vortex blocks, the reset elastic pieces are driven by the reset elastic pieces to stay on the inner peripheral surface of the torsion spring, and the peripheral surface of the intermediate baffle is increased by the peripheral force of the torsion spring around the intermediate baffle.
2. The asymmetric damping force shock absorber piston assembly of claim 1 wherein: a limiting block is arranged between the two axially corresponding inner vortex blocks, the limiting block is arranged in the rotating space and is not arranged in the inner notch, when the reset elastic piece is in a normal state, the reset elastic piece drives the rounding corner to abut against the limiting block, when the flow speed of the medium is increased, the circumferential force generated by the middle baffle is higher than the pretightening force of the reset elastic piece, the middle baffle rotates around the shaft to enable the conduction surface of the outer notch and the inner notch to be gradually increased until one end, far away from the rounding corner, of the outer vortex block abuts against the limiting block.
3. The asymmetric damping force shock absorber piston assembly of claim 2 wherein: the quantity of through-holes on top board and the bottom plate is 3, and the through-hole be with the corresponding arc through-hole of interior breach, the quantity of interior breach is 3, and then two-layer all cuts apart into 3 interior vortex piece about with interior vortex piece, the outer vortex piece of middle baffle is 3 with outer breach quantity, the quantity of stopper is 3, through-hole, interior vortex piece, outer vortex piece all encircle the piston rod equidistance and distribute, make 3 damping passageway between through-hole and the interior breach.
4. An asymmetric damping force shock absorber piston assembly as claimed in any one of claims 1 to 3, wherein: the piston rod is internally provided with a piston rod wire hole, the piston body is internally provided with a coil assembly, the coil assembly comprises two coil grooves and two exciting coils, the coil grooves are arranged on two axial sides of the middle baffle, the exciting coils are wound on the coil grooves, and the medium is magnetorheological fluid.
5. The utility model provides a magneto rheological damper, includes working cylinder and piston assembly, its characterized in that: the piston assembly is an asymmetric damping force shock absorber piston assembly according to claim 4, a sealing sleeve is arranged between the piston rod and the working cylinder, the working cylinder is further formed into a closed cavity, magnetorheological fluid is filled at two axial sides of the closed cavity corresponding to the piston body, and the magnetorheological fluid circulates at two sides of the piston body through damping channels.
6. The magnetorheological damper of claim 5, wherein: the directions of the currents which are led in by the two exciting coils are opposite.
7. The magnetorheological damper of claim 6, wherein: the one end that the working cylinder was kept away from the seal cover is equipped with the floating piston, the floating piston passes through the floating piston spring and is connected with the working cylinder, it has high-pressure inert gas to fill between floating piston and the working cylinder bottom.
8. The magnetorheological damper of claim 7, wherein: the coil groove sets up in the axial both sides of middle baffle respectively to restrict in the piston is originally internal through top board, bottom plate and piston sleeve cooperation, wire connecting hole has all been seted up on the coil groove, wire connecting hole and piston rod wire hole switch on, interior vortex piece upside and the interior vortex piece downside of lower floor all process there is the chamfer.
9. The magnetorheological damper of claim 8, wherein: the clamping groove for installing the sealing sleeve is formed in the upper end of the working cylinder, connecting holes are formed in the circle centers of the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle, the diameters of the connecting holes are equal to those of the piston rod, a fixed sealing structure is arranged between the sealing sleeve and the working cylinder, and sliding sealing structures are arranged between the sealing sleeve and the piston rod and on the inner walls of the piston assembly, the floating piston and the working cylinder.
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| CN202210498441.3A CN114877007B (en) | 2022-05-09 | 2022-05-09 | Asymmetric damping force shock absorber piston assembly and magneto-rheological shock absorber |
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| CN202210498441.3A CN114877007B (en) | 2022-05-09 | 2022-05-09 | Asymmetric damping force shock absorber piston assembly and magneto-rheological shock absorber |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0939242A2 (en) * | 1998-01-23 | 1999-09-01 | Draftex Industries Limited | Movement-controlling device |
| KR20060121586A (en) * | 2005-05-24 | 2006-11-29 | 부경대학교 산학협력단 | A damper using magneto-rheological fluid for controlling damping performance non-symmetrically |
| CN101915281A (en) * | 2010-07-19 | 2010-12-15 | 谭和平 | Single-rod magnetorheological damper with one-way channel |
| CN103352956A (en) * | 2013-06-19 | 2013-10-16 | 重庆大学 | Magneto-rheological damper with asymmetrical controllable damping characteristic |
| DE202014002228U1 (en) * | 2014-03-14 | 2014-05-06 | Erwin Krüger | Fluid damper for mutually adjustable furniture parts with a relatively adjustable piston guided in a cylinder |
| CN111194388A (en) * | 2017-08-09 | 2020-05-22 | W·黑尔德 | Fluid damper for parts that can be moved relative to one another, comprising a piston that is guided displaceably in a cylinder |
| CN113864381A (en) * | 2021-10-18 | 2021-12-31 | 重庆大学 | Biconical asymmetric force magnetorheological damper |
| CN114321256A (en) * | 2020-09-29 | 2022-04-12 | 汪丽 | Asymmetric damping force magneto-rheological shock absorber piston |
-
2022
- 2022-05-09 CN CN202210498441.3A patent/CN114877007B/en active Active
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| EP0939242A2 (en) * | 1998-01-23 | 1999-09-01 | Draftex Industries Limited | Movement-controlling device |
| KR20060121586A (en) * | 2005-05-24 | 2006-11-29 | 부경대학교 산학협력단 | A damper using magneto-rheological fluid for controlling damping performance non-symmetrically |
| CN101915281A (en) * | 2010-07-19 | 2010-12-15 | 谭和平 | Single-rod magnetorheological damper with one-way channel |
| CN103352956A (en) * | 2013-06-19 | 2013-10-16 | 重庆大学 | Magneto-rheological damper with asymmetrical controllable damping characteristic |
| DE202014002228U1 (en) * | 2014-03-14 | 2014-05-06 | Erwin Krüger | Fluid damper for mutually adjustable furniture parts with a relatively adjustable piston guided in a cylinder |
| CN111194388A (en) * | 2017-08-09 | 2020-05-22 | W·黑尔德 | Fluid damper for parts that can be moved relative to one another, comprising a piston that is guided displaceably in a cylinder |
| CN114321256A (en) * | 2020-09-29 | 2022-04-12 | 汪丽 | Asymmetric damping force magneto-rheological shock absorber piston |
| CN113864381A (en) * | 2021-10-18 | 2021-12-31 | 重庆大学 | Biconical asymmetric force magnetorheological damper |
Non-Patent Citations (3)
| Title |
|---|
| 具有非对称力学特性的汽车磁流变减振器设计与控制;于建强;董小闵;张宗伦;;中国机械工程(第03期);第124-129页 * |
| 适用于非线性主动悬架滑模控制的线性干扰观测器;龙启江等;《吉林大学学报（工学版）》;第第51卷卷(第第4期期);第1230-1240页 * |
| 非对称环形通道对磁流变液减振器阻尼特性的影响;廖昌荣;骆静;李兴;富丽娟;;铁道学报(第01期);第21-25页 * |
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