CN114877007A - Asymmetric damping force vibration absorber piston assembly and magneto-rheological vibration absorber - Google Patents
Asymmetric damping force vibration absorber piston assembly and magneto-rheological vibration absorber Download PDFInfo
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- CN114877007A CN114877007A CN202210498441.3A CN202210498441A CN114877007A CN 114877007 A CN114877007 A CN 114877007A CN 202210498441 A CN202210498441 A CN 202210498441A CN 114877007 A CN114877007 A CN 114877007A
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- 238000013016 damping Methods 0.000 title claims abstract description 116
- 239000006096 absorbing agent Substances 0.000 title claims abstract description 90
- 238000007667 floating Methods 0.000 claims abstract description 17
- 230000005284 excitation Effects 0.000 claims abstract description 13
- 238000007789 sealing Methods 0.000 claims description 25
- 239000012530 fluid Substances 0.000 claims description 22
- 239000000725 suspension Substances 0.000 claims description 9
- 239000011261 inert gas Substances 0.000 claims description 4
- 230000002093 peripheral effect Effects 0.000 claims description 4
- 239000003638 chemical reducing agent Substances 0.000 claims 1
- 230000035939 shock Effects 0.000 abstract description 63
- 238000007906 compression Methods 0.000 abstract description 35
- 230000006835 compression Effects 0.000 abstract description 35
- 230000005291 magnetic effect Effects 0.000 abstract description 19
- 238000011084 recovery Methods 0.000 abstract description 15
- 230000005426 magnetic field effect Effects 0.000 abstract description 3
- 238000000034 method Methods 0.000 description 10
- 230000009471 action Effects 0.000 description 8
- 238000010586 diagram Methods 0.000 description 8
- 238000005265 energy consumption Methods 0.000 description 6
- 238000004088 simulation Methods 0.000 description 6
- 230000008569 process Effects 0.000 description 5
- 230000008859 change Effects 0.000 description 2
- 238000009434 installation Methods 0.000 description 2
- 238000011160 research Methods 0.000 description 2
- 230000003313 weakening effect Effects 0.000 description 2
- 230000009286 beneficial effect Effects 0.000 description 1
- 238000006243 chemical reaction 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
- 239000011148 porous material Substances 0.000 description 1
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- 230000004044 response Effects 0.000 description 1
- 230000002441 reversible effect Effects 0.000 description 1
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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
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- Electromagnetism (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention relates to an asymmetric damping force vibration absorber piston assembly and a magneto-rheological vibration absorber adopting the same, wherein the vibration absorber is integrally of a single-cylinder single-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 vibration absorber has the advantages that: the output of the damping force of the whole shock absorber is controlled by adjusting the magnetic field intensity of the excitation coil and the relative position of the middle baffle and the piston sleeve, and the adjustable range of the damping force is large; the compression damping force and the recovery damping force can be adjusted according to the actual working condition, and the asymmetric mechanical property is realized; the double coils are connected with the incongruous current, 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
The vibration absorber is mainly a hydraulic vibration absorber, and the working principle of the hydraulic vibration absorber is that when the frame (or the vehicle body) and the axle vibrate and move relatively, a piston in the vibration absorber moves up and down, a medium in a cavity of the vibration absorber repeatedly flows into another cavity from one cavity through different pores, and at the moment, the friction between a hole wall and the medium and the internal friction between medium molecules form damping force on the vibration.
The damping process of the shock absorber can be divided into two stages of compression damping and rebound damping, as the name suggests, the compression damping is the damping force borne by the shock absorber piston when the shock absorber piston descends, the corresponding rebound damping force is the damping force borne by the shock absorber when the piston ascends, different road conditions correspond to different shock absorber piston movement speeds in the running process of the automobile, for example, when the automobile passes through a bump road surface, a deceleration strip and a bumpy road surface, the high-speed impact is carried out on the vehicle, the piston carries out middle-high speed movement, the damping force of the shock absorber mainly influences the smoothness of the automobile at the moment, the smoothness is better when the damping coefficient is smaller, wherein the influence of the compression damping force on the smoothness is larger than the rebound damping force, under the working condition that the automobile turns around obstacles or meets ditches, the shock absorber piston carries out low-speed movement, at the moment, the damping coefficient of the shock absorber mainly influences the roll degree of the automobile, and the increase of the damping coefficient of the shock absorber can reduce the roll degree of the automobile, the compression damping force and the recovery damping force of the existing shock absorber cannot be adjusted in a self-adaptive manner according to working conditions.
The current mainstream shock absorbers on the market are divided according to the angle of a damping medium, the shock absorbers mainly comprise hydraulic shock absorbers, pneumatic shock absorbers and magnetorheological shock absorbers, wherein the magnetorheological shock absorbers can realize the adjustment of the damping force of the shock absorbers by controlling the reversible conversion of the magnetorheological fluid between Newtonian fluid and Bingham fluid, have the advantages of high response speed, continuous adjustable damping force and the like, and are very suitable for being applied to semi-active suspensions of automobiles. The damping force can be adjusted, so that the shock absorber has better adjusting performance, and the research of the magneto-rheological shock absorber is more and more a hot problem in the field of automobile suspensions.
At present, the structure design of the magneto-rheological shock absorber is mainly carried out on the basis of the purpose of increasing the damping force of the shock absorber, the maximum damping force of the magneto-rheological shock absorber is improved, meanwhile, the minimum damping force of the magneto-rheological shock absorber is also improved, and when a piston moves at a high speed, better vehicle smoothness can be brought by smaller damping force, particularly by compressing the damping force. When the shock absorber moves at a high speed, the damping force proportioning mode of low compression and high restoration brings better vehicle smoothness and can ensure higher energy consumption efficiency, however, researches on the structure of the magneto-rheological shock absorber with asymmetric damping force of shock absorber compression and restoration are rare, and therefore, a novel magneto-rheological shock absorber structure capable of solving the problems is urgently needed.
Disclosure of Invention
The technical problem to be solved by the present invention is to provide an asymmetric damping force damper piston assembly for a hydraulic shock absorber and a magnetorheological shock absorber using the piston to operate, wherein the asymmetric damping force damper piston assembly is used for realizing the asymmetry of a compression damping force and a recovery damping force, so that a suspension on which the magnetorheological shock absorber is mounted can give consideration to the driving smoothness of a bump road surface and the low-side inclination during turning, and simultaneously, the problem that the minimum damping force is increased while the maximum damping force is increased during structural design of the current magnetorheological shock absorber is solved, and the damping force adjustable interval of the magnetorheological shock absorber is expanded.
In order to achieve the purpose, the invention provides the following technical scheme: asymmetric damping force vibration absorber piston assembly, including piston rod and the piston body who is connected with the piston rod, its characterized in that: the piston body comprises a piston sleeve and a middle baffle arranged in the piston sleeve, an upper pressure plate and a bottom plate are respectively arranged at the two axial ends of the piston sleeve corresponding to the middle baffle, at least one through hole corresponding to the axial position is respectively arranged on the upper pressure plate and the bottom plate, two layers of fan-shaped inner turbulent flow blocks are arranged at the two axial sides of the piston sleeve corresponding to the middle baffle, at least one inner notch is arranged between the inner turbulent flow blocks with the same cross section, the positions of the inner notches correspond to the positions of the through holes, a rotating space for the middle baffle to rotate around an axis is formed between the two inner turbulent flow blocks corresponding to the axial direction, at least one outer turbulent flow block and an outer notch are arranged on the outer peripheral surface of the middle baffle, a fan-ring gap is reserved between the outer turbulent flow block and the inner turbulent flow blocks, and a damping channel for a medium to be communicated through the two axial ends of the piston body is formed between the through holes and the inner notches, the outer turbulent flow blocks are provided with fillets at one ends facing the bottom plate, the middle baffle is provided with a reset elastic piece, when the reset elastic piece is in a normal state, the reset elastic piece drives the outer turbulent flow blocks to stay on the damping channel, and when the flow velocity of a medium rises to enable the circumferential force generated by the middle baffle to be higher than the pre-tightening force of the reset elastic piece, the middle baffle rotates around a shaft to enable the conduction surface of the outer notch and the inner notch to be gradually increased.
By adopting the technical scheme, the medium flowing in through the bottom plate can generate a force tangential to the middle baffle plate along the circumference when flowing through the fillet on the lower side of the middle baffle plate, the direction of the force is opposite to the direction of the pretightening force applied to the middle baffle plate by the reset elastic part, the higher the compression stroke speed of the shock absorber is, the larger the force applied to the middle baffle plate by the medium is, when the speed exceeds the set threshold value, the tangential force is larger than the pretightening force applied by the reset elastic part, the middle baffle plate rotates around a shaft to enable the positions of the outer notch, the inner notch and the through hole to correspond to each other 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 shock absorber is reset under the pretightening force of the reset elastic part, the positions of the inner notch and the outer turbulence block correspond to each other, and the cross section area formed by matching with the sector ring gap is small, the damping channel with large damping force further enables the piston assembly to have asymmetric mechanical characteristics, when the piston assembly is applied to the shock absorber, only a certain speed between the high speed and the low speed in the shock absorber is selected as a speed threshold value, so that the smoothness and the high energy consumption efficiency of an automobile passing through a bump road surface and other bumpy roads can be realized, and the lower roll angle of the automobile can be ensured under the working conditions of obstacle-detouring and groove-meeting, namely, the compression force and the recovery force of the damper can be independently controlled, and under the working conditions of compression and recovery, the required damping force values are different, especially when the recovery 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 recovery force according to the working condition is solved, the independence of the compression force and the recovery force is realized, and simultaneously when the piston assembly is applied to the shock absorber, the piston assembly can be matched with current combined control, the suspension with the magneto-rheological shock absorber can give consideration to the driving smoothness of a bump road surface and the low-side inclination during turning, simultaneously solves the problem that the maximum damping force is increased and the minimum damping force is also increased during structural design of the current magneto-rheological shock absorber, and enlarges the damping force adjustable range of the magneto-rheological shock absorber, wherein the reset elastic element can be an elastic element such as a spring, a torsion spring, rubber and the like.
The piston assembly of the asymmetric damping force damper may be further configured to: the axial direction is corresponding all is equipped with a stopper between two interior turbulent flow pieces, the stopper sets up in rotating the space, and does not set up in interior breach, when the elastic component that resets is in the normality, the elastic component that resets drive radius angle and stopper counterbalance, when the velocity of flow of medium risees and makes the circumference that intermediate baffle produced be higher than the pretightning force of elastic component that resets, intermediate baffle will rotate around the axle and make outer breach and interior breach conducting surface progressively increase, and the one end that the radius angle was kept away from to outer turbulent flow piece offsets with the stopper.
Adopt above-mentioned technical scheme, through setting up the stopper, inject the rotation range of baffle in the middle of the elastic component drive that resets, avoid the elastic component that resets deformation excessively can't reset, or the pretightning force is too big, and it is excessive to reset, and then improves the control power of baffle to the damping passageway in the middle of.
The piston assembly of the asymmetric damping force vibration absorber can be further configured as follows: the reset elastic piece is a torsion spring which is arranged on the peripheral surface of the middle baffle plate, so that the torsion arm is abutted against the middle baffle plate, and the upper and lower torsion spring feet 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 the torsion springs with different pretightening forces are selected to adapt to the vehicles under different working conditions.
The piston assembly of the asymmetric damping force damper may be further configured to: the quantity of through-hole 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 will interior spoiler piece upper and lower two-layer equal divide into 3 interior spoiler pieces, the outer spoiler piece and the outer breach quantity of middle baffle are 3, the quantity of stopper is 3, through-hole, interior spoiler piece, outer spoiler piece all encircle piston rod equidistance and distribute, make 3 damping passageways between through-hole and the interior breach.
By adopting the technical scheme, when the number of the structural components in the piston body is as above, the piston sleeve and the middle baffle are 3 fan-shaped structures which are mutually corresponding or are arranged in a staggered mode, 3 damping channels are further realized, 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 during structural design of the current magneto-rheological shock absorber is solved, the damping force adjustable interval of the magneto-rheological shock absorber is expanded, and the problem that the service life of the shock absorber is too short due to asymmetric damping force during single channel is avoided.
The piston assembly of the asymmetric damping force damper may be further 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 excitation coils, the coil grooves are arranged on two axial sides of the middle baffle, the excitation 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 magneto-rheological damper, the coil assembly is only required to be additionally arranged in the piston body, so that the magnet exciting coil is wound on the coil groove and is connected with the power supply through the hole of the piston rod, the ECU of the vehicle is convenient to control the current to work, and the semi-active suspension is matched with the magneto-rheological fluid to realize the vibration reduction of the semi-active suspension.
The utility model provides a magneto-rheological shock absorber, includes working cylinder and piston assembly, piston assembly is asymmetric damping force shock absorber piston assembly, install the seal cover between piston rod and the working cylinder, and then form airtight chamber with the working cylinder, the axial both sides that airtight chamber corresponds the piston body all are filled with magneto-rheological fluid, magneto-rheological fluid circulates in piston body both sides through the damping passageway.
By adopting the technical scheme, the piston assembly is an asymmetric damping force vibration absorber piston assembly, so that when magnetorheological fluid flowing in through a bottom plate flows through a fillet on the lower side of an intermediate baffle in the compression stroke of the vibration absorber, circumferential tangential force can be generated on the intermediate baffle, the force direction is opposite to the pretightening force applied to the intermediate baffle by a torsion spring, the higher the compression stroke speed of the vibration absorber is, the larger the force applied to the intermediate 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 intermediate baffle rotates around a shaft to a non-fillet side to contact a limiting block, at the moment, an outer notch, an inner notch and an arc-shaped through hole correspond in position, 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 vibration absorber is reset to a position with the fillet end contacting the limiting block under the action of the torsion spring, at the moment, the inner notch corresponds to the outer turbulence block in position, the cross section area of the sector ring gap is small, the damping force is large, so that the magneto-rheological damper has asymmetric mechanical characteristics, a certain speed between the high speed and the low speed in the damper is selected as a speed threshold value, the smoothness and the high energy consumption efficiency of an automobile passing through a bump road surface and other bumpy roads can be ensured, the automobile can also be ensured to have low lateral inclination when the automobile passes through an obstacle-detouring working condition or meets a ditch working condition, the damping force of the magneto-rheological fluid in a recovery channel or a compression channel can be changed by controlling current, the compression force and the recovery force of the damper can be independently controlled, and the problems that the damper is difficult to adaptively adjust the limit of the compression force and the recovery force and the control algorithm of the magneto-rheological damper is extremely complex under the conditions of compression and recovery, particularly under the working condition that the recovery force is larger than the working condition of the compression force in the prior art are solved, the independent and combined control of the compression force and the restoring force is realized.
The above magnetorheological damper may further be configured as follows: the two excitation coils are electrified with currents in opposite directions.
By adopting the technical scheme, the double-coil conduction anisotropic current can more fully utilize the magnetic field effect of the middle part of the two coils, and compared with the condition of conduction isotropic current, the adjustable damping force interval is larger.
The above magnetorheological damper may further be configured as follows: and a floating piston is arranged at one end of the working cylinder, which is far away from the sealing sleeve, and is connected with the working cylinder through a floating piston spring, and high-pressure inert gas is filled between the floating piston and the bottom of the working cylinder.
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 inside the working cylinder caused by the fact that the piston rod extends into the working cylinder for different lengths.
The above magnetorheological damper may further comprise: the coil groove sets up respectively in the axial both sides of middle baffle to through top board, bottom plate and piston bush cooperation restriction at this internally at the piston, the wire connecting hole has all been seted up on the coil groove, the wire connecting hole switches on with piston rod wire hole, interior turbulent flow piece upside and lower floor interior turbulent flow piece downside have all been processed the chamfer.
Adopt above-mentioned technical scheme, the coil groove sets up the both sides at middle baffle respectively to set up the wire connecting hole and switch on with piston rod direction hole, make things convenient for excitation coil erection joint, avoid magnetorheological suspensions to contact excitation coil, improve stability, two excitation coils realize the two coil to lead to the incorgruous electric current simultaneously, further enlarged the adjustable interval of magnetorheological damper damping force, simultaneously all processed the chamfer at interior turbulent flow piece upside and lower floor interior turbulent flow piece downside, be used for the installation of torsional spring, stability when improving the torsional spring installation.
The above magnetorheological damper may further be configured as follows: the upper end of the working cylinder is provided with a clamping groove for installing a sealing sleeve, the circle centers of the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle are all provided with connecting holes, the diameter of each connecting hole is equal to that 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, the magnetorheological fluid is prevented from overflowing, the piston rod is inserted into the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle through the connecting hole, and then the piston body is connected with the piston rod.
Compared with the prior art, the invention has the beneficial effects that:
1. the invention can realize the effect of asymmetric compression and recovery of damping force of the shock absorber by matching tangential force along the circumference borne by the fillet of the middle baffle plate with the pretightening force of the torsion spring, realize the self-adaption to generate asymmetric damping, ensure the smoothness and higher energy consumption efficiency of the automobile passing through bumpy pavements and other bumpy pavements, ensure lower side inclination of the automobile during turning, and improve the damping force adjustable interval by two damping force adjusting modes of mechanical adjustment and electromagnetic adjustment of the middle baffle plate when the shock absorber is applied to the magneto-rheological shock absorber.
2. According to the invention, the length and the cross-sectional area of the damping channel are changed due to the rotation of the middle baffle plate, so that the maximum damping force is improved while the minimum damping force is reduced, and the adjustable damping force interval of the shock absorber is enlarged.
3. Compared with the excitation coil with the same current direction, although the magnetic field intensity at the outer sides of the two coils is weakened under the action of opposite magnetic fields, the magnetic field intensity in 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 adjustable range of the damping force of the magneto-rheological shock absorber is further expanded.
The invention is further described below with reference to the accompanying drawings.
Drawings
Fig. 1 is a sectional view of a piston assembly according to embodiment 1 of the present invention.
Fig. 2 is a schematic view of parts of a piston assembly according to embodiment 1 of the present invention.
Fig. 3 is a schematic structural view of a piston body in embodiment 1 of the present invention.
Fig. 4 is a schematic structural view of a piston bush according to embodiment 1 of the present invention.
Fig. 5 is a schematic diagram showing the relative positions of the intermediate baffle and the piston sleeve when the intermediate baffle is rotated to a low damping condition in example 1 of the present invention.
Fig. 6 is a schematic diagram showing the relative positions of the intermediate baffle and the piston sleeve when the intermediate baffle is rotated to a high damping condition in example 1 of the present invention.
Fig. 7 is a medium direction diagram when the intermediate baffle rotates to a low damping condition in embodiment 1 of the present invention.
Fig. 8 is a medium course diagram in case of the middle baffle plate rotating to a large damping condition in embodiment 1 of the present invention.
FIG. 9 is a cross-sectional view of a magnetorheological damper in accordance with embodiment 2 of the invention.
Fig. 10 is a schematic diagram of a two-dimensional simulation structure of femm (finished Element Method magnetics) in embodiment 2 of the present invention.
Fig. 11 is a schematic diagram of FEMM simulation results of magnetic field distribution in the piston when two coils are energized with currents in the same direction in case of large damping in embodiment 2 of the present invention.
Fig. 12 is a schematic diagram of FEMM simulation results of magnetic field distribution in the piston when two coils are energized with different currents under a large damping condition in embodiment 2 of the present invention.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the drawings in the embodiments of the present invention, and it is obvious that the described embodiments are only a part of the embodiments of the present invention, and not all of the embodiments. All other embodiments, which can be obtained by a person skilled in the art without making any creative effort based on the embodiments in the present invention, belong to the protection scope of the present invention.
In the description of the present invention, it should be noted that the terms "upper", "lower", "inner", "outer", "front", "rear", "both ends", "one end", "the other end", and the like indicate orientations or positional relationships based on those shown in the drawings, and are only for convenience of description and simplicity of description, but do not indicate or imply that the referred device or element must have a specific orientation, be constructed in a specific orientation, and be operated, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first" and "second" 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 is to be noted that, unless otherwise explicitly specified or limited, the terms "mounted," "disposed," "connected," and the like are to be construed broadly, such as "connected," which may be fixedly connected, detachably connected, or integrally connected; can be mechanically or electrically connected; they may be connected directly or indirectly through intervening media, or they may be interconnected between two elements. The specific meanings of the above terms in the present invention can be understood in specific cases to those skilled in the art.
Example 1
As shown in fig. 1 to 8, the asymmetric damping force damper piston assembly includes a piston rod 1 and a piston body 4 connected to the piston rod 1, where the piston body 4 includes a piston sleeve 42 and a middle baffle 43 disposed in the piston sleeve 42, the piston sleeve 42 is provided with an upper pressure plate 41 and a bottom plate 12 corresponding to two axial ends of the middle baffle 43, the upper pressure plate 41 and the bottom plate 12 are respectively provided with three arc-shaped through holes 121 corresponding to the axial positions, two layers of fan-shaped inner turbulence blocks 423 are disposed on two axial sides of the piston sleeve 4 corresponding to the middle baffle 43, three inner notches 424 are disposed between the inner turbulence blocks 423 with the same cross section, so as to divide the upper layer and the lower layer of the inner turbulence blocks 423 into three inner turbulence blocks 423, the inner notches 424 correspond to the positions of the arc-shaped through holes 121, a rotation space a for the middle baffle to rotate around the piston rod 1 is formed between the two inner turbulence blocks 423 corresponding to the axial direction, the outer circumferential surface of the middle baffle 43 is provided with three outer turbulence blocks 431 and three outer gaps 433, a fan-shaped gap 48 is reserved between the outer turbulence blocks 431 and the inner turbulence blocks 423, the arc-shaped through holes 121, the inner turbulence blocks 423 and the outer turbulence blocks 431 are all distributed around the piston rod 1 at equal intervals, so that three damping channels b for medium to pass through two axial ends of the piston body 4 and then to be conducted are formed between the arc-shaped through holes 121 and the inner gaps 424, one ends of the outer turbulence blocks 431 facing the bottom plate 12 are all provided with a rounded corner 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, so that a torsion arm 451 is abutted against the middle baffle 43, upper and lower torsion spring feet 452 are respectively clamped in the arc-shaped through holes 121 (411) of the upper pressure plate 41 and the bottom plate 12, when the torsion spring 45 is in a normal state, the torsion spring 45 drives the outer turbulence blocks 431 to stay on the damping channels b, and when the flow velocity of the medium rises, the circumferential force generated by the middle baffle 43 is higher than the pre-tightening 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 two inner turbulence blocks 423 corresponding to the axial direction, the number of the limiting blocks 422 is three, the limiting blocks 422 are arranged in the rotating space a and are not arranged in the inner gap 424, when the torsion spring 45 is in a normal state, the torsion spring 45 drives the fillet 432 to abut against the limiting blocks 422, when the flow rate of a 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, far away from the fillet 432, of the outer turbulence block 431 abuts against the limiting blocks 422, the piston assembly can be suitable for a hydraulic shock absorber and a magneto-rheological shock absorber, namely the medium can be hydraulic oil or magneto-rheological fluid, so that self-adaption to generate asymmetric damping is realized, but when the piston assembly is used on the hydraulic shock absorber, the compression force and the restoring force of the damper can be controlled independently, the problem that the conventional shock absorber is difficult to adjust the limit of the compression force and the restoring force in a self-adaptive mode according to the working condition under the condition that the required damping force value is different under the compression working condition and the restoring working condition, particularly when the restoring force is larger than the working condition requirement of the compression force is solved, when the magneto-rheological shock absorber is used, the damping force of magneto-rheological fluid in a restoring channel or a compression channel can be changed by controlling the current only by configuring the magnet exciting coil capable of adjusting the current, and the independent and combined control of the compression force and the restoring force is realized.
Example 2
As shown in fig. 1-10, a magnetorheological damper comprises a working cylinder 3 and a piston assembly, the piston assembly is an asymmetric damping force damper piston assembly, a sealing sleeve 2 is installed between the piston rod 1 and the working cylinder 3 to form a closed cavity c with the working cylinder, magnetorheological fluid is filled in both axial sides of a closed cavity hammer c corresponding to a piston body 4, the magnetorheological fluid circulates on both sides of the piston body 4 through a damping channel b, a piston rod lead 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 slots 46 and two excitation coils 44, the coil slots 46 are installed on both axial sides of a middle baffle 43 and are limited in the piston body 4 through the cooperation of an upper pressure plate 41, a bottom plate 12 and a piston sleeve 42, the excitation coils 44 are wound on the coil slots 46, the current directions of the two magnet exciting coils 44 are opposite, one end of the working cylinder 3, which is far away from the sealing sleeve 2, is provided with a floating piston 5, the floating piston 5 is connected with the working cylinder 3 through a floating piston spring 6, high-pressure inert gas is filled between the bottom of the floating piston 5 and the bottom of the working cylinder 3, a wire connecting hole 461 is formed in the coil groove 46, the wire connecting hole 461 is communicated with a piston rod wire hole 11, and chamfers 421 are processed on the upper side of the inner turbulent block 423 and the lower side of the lower-layer inner turbulent block 423.
As shown in fig. 9, in the magnetorheological shock absorber with asymmetric mechanical properties of the present invention, magnetorheological fluids are 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 for the change of the total volume inside the working cylinder 3 caused by the difference of the length of the piston rod 1 extending 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 mounting the sealing sleeve 2, the upper pressing plate 41, the coil groove 46 and the center of circle of the middle baffle 43 are provided with connecting holes 47, the diameter of each connecting hole 47 is equal to that of the piston rod 1, the sealing sleeve 2 is used for mounting the piston body 4, the sealing sleeve 2 and the working cylinder 3 are fixedly sealed between the sealing sleeve 2 and the piston rod 1, the inner walls of the piston body 4, the floating piston 5 and the working cylinder 3 are all subjected to sliding sealing treatment, and the sealing sleeve 2 also plays a role in guiding the axial movement of the piston rod 1.
As shown in fig. 4-8, chamfers 421 are formed on the upper side of the upper inner turbulence block 423 and the lower side of the lower inner turbulence block 423 for mounting the torsion spring 45, a rounded corner 432 is formed on the right side below the outer turbulence block 431 of the middle baffle 43, when magnetorheological fluid flowing in through the bottom plate 12 flows through the rounded corner 432 on the lower side of the middle baffle 43 in a compression stroke of the shock absorber, a circumferential tangential force is generated on the middle baffle 43, the direction of the force is opposite to the pre-tightening force applied to the middle baffle 43 by the torsion spring 45, the higher the speed of the compression stroke of the shock absorber is, the larger the force applied by the magnetorheological fluid to the middle baffle 43 is, when the speed exceeds a set threshold value, the tangential force is larger than the pre-tightening force applied by the torsion spring 45, the middle baffle 43 rotates to the non-rounded-side to contact the limit block 422, the positions of the outer gap 433, the inner gap 424 and the arc-shaped through hole correspond, the path of the magnetorheological fluid damping channel 47 is, enter the first layer inner gap 424 through the bottom plate arc through hole 121, then directly enter the outer gap 433, enter the second layer inner gap 424, flow out through the upper press plate arc channel 411, the whole damping channel 47 has short length, large cross-sectional area and small damping force, as shown in fig. 3 and 5. When the restoring stroke or the compression speed does not reach a set threshold value, the magnetorheological damper is reset to a contact limiting block 422 with a fillet end under the action of the pre-tightening force of the torsion spring 45, the inner notch 424 corresponds to the outer turbulence block 431, the path of the magnetorheological fluid damping channel 47 is that the magnetorheological fluid enters the inner notch 424 of the first layer through the arc-shaped through hole 121 of the bottom plate, then enters the outer notch 433 through the fan-shaped ring gap 48, enters the inner notch 424 of the second layer through the fan-shaped ring gap 48 of the second layer, and flows out through the arc-shaped channel 411 of the upper pressure plate, the integral damping channel 47 is long, wherein the cross-sectional 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 selects a certain speed between high speed and low speed in the shock absorber as a speed threshold value, so that the smoothness and the energy consumption efficiency of the automobile when the automobile passes through bumpy roads and other bumpy roads are higher, and the automobile can be ensured to have lower lateral inclination when the automobile turns around obstacles or meets the working condition of 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 without affecting the simulation result, and a specific simulation two-dimensional graph is shown in fig. 10. The number of turns of the coil is set to be 100 turns, the two groups of coils have 200 turns, the current is 2A, and simulation results are shown in fig. 11 and 12. It is obvious from the magnetic field distribution diagram that when the current in the same direction is applied, the action directions of the magnetic fields generated by the two coils between the coils, namely the middle baffle 43 in the figure, are opposite, the magnetic field intensity is weakened, and the weakening degree is serious. The action directions of the magnetic fields of the two coils on the upper side and the lower side are the same, and the magnetic field intensity is enhanced. When the opposite current is conducted, the action directions of the magnetic fields generated by the two coils at the middle baffle 43 in the figure are the same, the magnetic field intensity is enhanced, the action directions of the magnetic fields of the two coils at the upper side and the lower side are opposite, the magnetic field intensity is weakened, and the weakening degree is slight. The conclusion can be drawn that the double-coil induced anisotropic current can more fully utilize the magnetic field effect of the middle part of the two coils, and compared with the condition of induced isotropic current, the adjustable damping force interval is larger.
In conclusion, the magneto-rheological shock absorber with asymmetric mechanical characteristics provided by the invention realizes the asymmetric structural design of compression damping force and recovery damping force; the magneto-rheological damper structure can better ensure the driving smoothness and high energy consumption efficiency of an automobile passing through a bump road surface or a bumpy road surface; the vehicle can be ensured to have lower side inclination when the vehicle turns around obstacles or meets the working condition of a ditch; and the adjustable damping force interval is further increased by adopting a method of introducing a counter current into the 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 an … …" does not exclude the presence of other identical 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 attributes 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 (10)
1. Asymmetric damping force vibration absorber piston assembly, including piston rod and the piston body who is connected with the piston rod, its characterized in that: the piston body comprises a piston sleeve and a middle baffle arranged in the piston sleeve, an upper pressure plate and a bottom plate are respectively arranged at the two axial ends of the piston sleeve corresponding to the middle baffle, at least one through hole corresponding to the axial position is respectively arranged on the upper pressure plate and the bottom plate, two layers of fan-shaped inner turbulent flow blocks are arranged at the two axial sides of the piston sleeve corresponding to the middle baffle, at least one inner notch is arranged between the inner turbulent flow blocks with the same cross section, the positions of the inner notches correspond to the positions of the through holes, a rotating space for the middle baffle to rotate around an axis is formed between the two inner turbulent flow blocks corresponding to the axial direction, at least one outer turbulent flow block and an outer notch are arranged on the outer peripheral surface of the middle baffle, a fan-ring gap is reserved between the outer turbulent flow block and the inner turbulent flow blocks, and a damping channel for a medium to be communicated through the two axial ends of the piston body is formed between the through holes and the inner notches, the outer turbulent flow blocks are provided with fillets at one ends facing the bottom plate, the middle baffle is provided with a reset elastic piece, when the reset elastic piece is in a normal state, the reset elastic piece drives the outer turbulent flow blocks to stay on the damping channel, and when the flow velocity of a medium rises to enable the circumferential force generated by the middle baffle to be higher than the pre-tightening force of the reset elastic piece, the middle baffle rotates around a shaft to enable the conduction surface of the outer notch and the inner notch to be gradually increased.
2. The asymmetric damping force absorber piston assembly of claim 1, wherein: the axial direction is corresponding all is equipped with a stopper between two interior turbulent flow pieces, the stopper sets up in rotating the space, and does not set up in interior breach, when the elastic component that resets is in the normality, the elastic component that resets drive radius angle and stopper counterbalance, when the velocity of flow of medium risees and makes the circumference that intermediate baffle produced be higher than the pretightning force of elastic component that resets, intermediate baffle will rotate around the axle and make outer breach and interior breach conducting surface progressively increase, and the one end that the radius angle was kept away from to outer turbulent flow piece offsets with the stopper.
3. The asymmetric damping force absorber piston assembly of claim 2, wherein: the reset elastic piece is a torsion spring which is arranged on the peripheral surface of the middle baffle plate, so that the torsion arm is abutted against the middle baffle plate, and the upper and lower torsion spring feet are respectively clamped in the through holes of the upper pressing plate and the bottom plate.
4. The asymmetric damping force absorber piston assembly of claim 3, wherein: the quantity of through-hole 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 will interior spoiler piece upper and lower two-layer equal divide into 3 interior spoiler pieces, the outer spoiler piece and the outer breach quantity of middle baffle are 3, the quantity of stopper is 3, through-hole, interior spoiler piece, outer spoiler piece all encircle piston rod equidistance and distribute, make 3 damping passageways between through-hole and the interior breach.
5. The asymmetric damping force absorber piston assembly of any of claims 1-4, 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 excitation coils, the coil grooves are arranged on two axial sides of the middle baffle, the excitation coils are wound on the coil grooves, and the medium is magnetorheological fluid.
6. A magneto-rheological damper comprises a working cylinder and a piston assembly, and is characterized in that: the piston assembly is the asymmetric damping force vibration reducer piston assembly of claim 5, install the seal cover between piston rod and the working cylinder, and then form airtight chamber with the working cylinder, the axial both sides that the airtight chamber corresponds the piston body all are filled with magnetorheological suspensions, magnetorheological suspensions circulate in piston body both sides through the damping passageway.
7. The magnetorheological damper of claim 6, wherein: the directions of currents conducted by the two excitation coils are opposite.
8. The magnetorheological damper of claim 7, wherein: and a floating piston is arranged at one end of the working cylinder, which is far away from the sealing sleeve, and is connected with the working cylinder through a floating piston spring, and high-pressure inert gas is filled between the floating piston and the bottom of the working cylinder.
9. The magnetorheological damper of claim 8, wherein: the coil groove sets up respectively in the axial both sides of middle baffle to through top board, bottom plate and piston bush cooperation restriction at this internally at the piston, the wire connecting hole has all been seted up on the coil groove, the wire connecting hole switches on with piston rod wire hole, interior turbulent flow piece upside and lower floor interior turbulent flow piece downside have all been processed the chamfer.
10. The magnetorheological damper of claim 9, wherein: the upper end of the working cylinder is provided with a clamping groove for installing a sealing sleeve, the circle centers of the sealing sleeve, the upper pressing plate, the coil groove and the middle baffle are all provided with connecting holes, the diameter of each connecting hole is equal to that 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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