CN106090110B - Electro-rheological fluid damper - Google Patents
Electro-rheological fluid damper Download PDFInfo
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- CN106090110B CN106090110B CN201610748306.4A CN201610748306A CN106090110B CN 106090110 B CN106090110 B CN 106090110B CN 201610748306 A CN201610748306 A CN 201610748306A CN 106090110 B CN106090110 B CN 106090110B
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- damping
- damping fin
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- adjusting set
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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
- F16F9/532—Electrorheological [ER] fluid dampers
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- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Electromagnetism (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
- Fluid-Damping Devices (AREA)
Abstract
The invention discloses a kind of electro-rheological fluid damper, including cylinder barrel, piston rod, piston assembly and damping adjustment device, piston assembly to be arranged in the inner chamber body of cylinder barrel, piston assembly and with allowing multiple throttle orifices that ER fluid passes through.Piston rod is disposed through cylinder barrel and piston assembly, and is connected with piston assembly.Damping adjustment device includes being rotatably arranged on the first damping fin and the second damping fin for the throttling hole number that the state that is turned on and off is in inside piston assembly and for regulation, the frequency damping adjustment device being connected with the first damping fin and amplitude damping adjusting means being connected with the second damping fin.The electro-rheological fluid damper of the present invention, first damping fin and the second damping fin are set in piston assembly, the quantity in the throttle orifice being turned on and off under state by the first damping fin and the regulation of the second damping fin, so that the damping force of damper is also changed, reaches the purpose of regulation damping.
Description
Technical field
The invention belongs to damper technique field, and specifically, the present invention relates to a kind of electro-rheological fluid damper.
Background technology
At present, the electro-rheological fluid damper applied in suspension systems mainly has three kinds of structures：Single pole single cylinder structure, double-rod are double
Cylinder structure and rotational structure.The electro-rheological fluid damper of these three structures can be according to different road conditions by changing its damping force
Size improves the ride comfort of automobile and control stability, but all can not to adjust damping force according to suspension amplitude well big
It is small.In practical engineering application, when electro-rheological fluid damper works, just to quickly consume vibrational energy, suspension is not accounted for
Amplitude feature (small amplitude-frequency is fast, and large amplitude frequency is slow), this produces heat when damper can be caused to work, and then can influence interior
The ER fluid performance in portion, makes suspension system service behaviour not reach most preferably.Therefore need to solve electro-rheological fluid damper can not basis
The various amplitude of suspension and the problems such as cause service behaviour and cooling, increase damper adjustable range.
The content of the invention
It is contemplated that at least solves one of technical problem present in prior art.Therefore, the present invention provides a kind of electricity
Rheological damper, it is therefore an objective to realize that damping force is adjustable.
To achieve these goals, the technical scheme taken of the present invention is：Electro-rheological fluid damper, including：
Cylinder barrel, its inside have ER fluid；
Piston assembly, it is arranged in cylinder barrel, and with allowing multiple throttle orifices that ER fluid passes through；
Piston rod, it is disposed through cylinder barrel and piston assembly, and is connected with piston assembly；And
Damping adjustment device, it includes being rotatably arranged on inside piston assembly and is turned on and off for adjusting to be in
The first damping fin and the second damping fin of the throttling hole number of state, the frequency damping adjustment device being connected with the first damping fin with
And the amplitude damping adjusting means being connected with the second damping fin.
The frequency damping adjustment device includes for being sheathed on the piston rod and being connected with first damping fin
One adjusting set and be connected with the first adjusting set and for provide make its rotate driving force the first power-generating assembly.
The first damping fin setting is multiple, and multiple first damping fins are circumferentially uniform in first adjusting set
Distribution.
First power-generating assembly includes motor, the first transmission mechanism and the second transmission mechanism being sequentially connected,
Second transmission mechanism is connected with first adjusting set.
Second transmission mechanism is cylindrical gear mechanism, and the driving gear of the second transmission mechanism passes through adjustable in length
Power transmission shaft is connected with described first transmission mechanism, and the driven gear of the second transmission mechanism is connected with first adjusting set.
First power-generating assembly also includes the first signal acquisition mechanism, and the first signal acquisition mechanism includes signal
Gear, with the coaxially connected ratchet of signal gear, be sheathed on piston rod fixed cover, be rotatably arranged on fixed cover and
Tooth for stirring ratchet rotation refers to and the speed probe for detection signal gear rotational speed.
The amplitude damping adjusting means includes for being sheathed on the piston rod and being connected with second damping fin
Two adjusting sets and be connected with the second adjusting set and for provide make its rotate driving force the second power-generating assembly.
The rocking arm of second power-generating assembly including rotatable setting, the driver being connected with one end of rocking arm and with
The semicolumn rack of the other end connection of rocking arm, the outer surface of second adjusting set are provided with the outer spiral shell engaged with semicolumn rack
Line.
The amplitude damping adjusting means also includes secondary signal collecting mechanism, and the secondary signal collecting mechanism includes setting
Buffer spring below the piston rod and the displacement transducer for detecting piston rod displacement.
The piston assembly include the first piston half portion that is oppositely arranged and second piston half portion and with second piston half
The 3rd damping fin that portion connects with the piston rod.
The electro-rheological fluid damper of the present invention, the first damping fin and the second damping fin are set in piston assembly, passes through first
The quantity of damping fin and the regulation of the second damping fin in the throttle orifice being turned on and off under state, so that the damping of damper
Power is also changed, and reaches the purpose of regulation damping.
Brief description of the drawings
This specification includes the following drawings, and shown content is respectively：
Fig. 1 is the structural representation of electro-rheological fluid damper of the present invention；
Fig. 2 is the sectional view of damper body；
Fig. 3 is the decomposing schematic representation of piston assembly；
Fig. 4 is the structural representation of the first adjusting set；
Fig. 5 is the structural representation of the second adjusting set；
Fig. 6 is the decomposing schematic representation of the first adjusting set, the second adjusting set and piston assembly；
Fig. 7 is the structural representation of damping adjustment device；
Fig. 8 is the installation diagram of frequency damping adjustment device and piston rod；
Fig. 9 is the structural representation of the first signal acquisition mechanism；
Figure 10 is the decomposing schematic representation of power transmission shaft；
Figure 11 is the structural representation of amplitude damping adjusting means；
Figure 12 is the partial structural diagram of amplitude damping adjusting means；
Figure 13 is the structural representation of secondary signal collecting mechanism；
Figure 14 is the structure diagram of magnetic valve；
Figure 15 is the force diagram of second set of figure；
In figure mark for：
1st, cylinder barrel；
2nd, piston rod；
3rd, piston assembly；31st, first piston block；32nd, the first side wall；33rd, second piston block；34th, second sidewall；35th, save
Discharge orifice；36th, the 3rd damping fin；
4th, frequency damping adjustment device；41st, the first adjusting set；42nd, the first driving gear；43rd, the first driven gear；44、
Second driving gear；45th, the second driven gear；46th, motor；47th, the first axle body；48th, the second axle body；49th, first support；
410th, ratchet；411st, signal gear；412nd, speed probe；413rd, tooth refers to；414th, fixed cover；415th, first base；416th, lead
Line；
5th, amplitude damping adjusting means；51st, the second adjusting set；52nd, second base；53rd, bearing；54th, rocking arm；55th, semicircle
Post rack；56th, driver；57th, buffer spring；58th, displacement transducer；59th, the 3rd base；510th, hydraulic pump；511st, bearing pin；
512nd, magnetic valve；513rd, liquid reserve tank；514th, the first oilhole；515th, the second oilhole；
6th, the first damping fin；7th, the second damping fin；8th, the first end cap；9th, the second end cap；10th, sealing ring；11st, controller.
Embodiment
Below against accompanying drawing, by the description to embodiment, embodiment of the invention is made further details of
Explanation, it is therefore an objective to help those skilled in the art to have more complete, accurate and deep reason to design of the invention, technical scheme
Solution, and contribute to its implementation.
As depicted in figs. 1 and 2, the invention provides a kind of electro-rheological fluid damper, including cylinder barrel 1, piston rod 2, piston are total
Into 3 and damping adjustment device.Cylinder barrel 1 is the cylindrical tube of inner hollow, and the internal void of cylinder barrel 1, which is divided into, stores electric current change
The cylindrical inner chamber body of liquid.Piston assembly 3 is arranged in the inner chamber body of cylinder barrel 1, piston assembly 3 and with allowing ER fluid to lead to
The multiple throttle orifices 35 crossed.Piston rod 2 is disposed through cylinder barrel 1 and piston assembly 3, and is connected with piston assembly 3.Damping regulation
Device includes being rotatably arranged on the inside of piston assembly 3 and for adjusting the quantity of throttle orifice 35 in the state that is turned on and off
The first damping fin 6 and the second damping fin 7, the frequency damping adjustment device 4 that is connected with the first damping fin 6 and with the second damping
The amplitude damping adjusting means 5 that piece 7 connects.
Specifically, as shown in Figures 2 and 3, the piston assembly 3 in cylinder barrel 1 is provided with one, and piston assembly 3 includes relative
The first piston half portion and second piston half portion of setting and the 3rd damping fin being connected with second piston half portion and piston rod 2
36, the inside of piston assembly 3 has the cavity for accommodating the first damping fin 6, the second damping fin 7 and the 3rd damping fin 36.First piston
Half portion includes first piston block 31 and the first side wall 32 being connected with first piston block 31, and first piston block 31 is circular block shape knot
Structure, the first side wall 32 are cirque structure, the overall diameter of the first side wall 32 it is equal in magnitude with the overall diameter of first piston block 31 and
Both are to be fixedly and coaxially connected.Have at the center of first piston block 31 and allow the manhole that piston rod 2 passes through, throttle orifice 35 exists
Line is uniformly distributed circumferentially multiple, throttle orifice 35 and for along the centered on the axis of first piston block 31 on first piston block 31
The thickness direction of one piston block 31 is through the through hole set.The structure of the structure of second piston half portion and first piston half portion is basic
Identical, second piston half portion includes second piston block 33 and the second sidewall 34 being connected with second piston block 33, second piston block
33 be circular block shape structure, and second sidewall 34 is cirque structure, and the overall diameter of second sidewall 34 is outer with second piston block 33
Diameter is equal and both is are fixedly and coaxially connected, the overall diameter of first piston block and the overall diameter size of second piston block 33
Equal and both are parallel, one end of the first side wall 32 is connected with first piston block 31, the other end of the first side wall 32 and second
The end of sidewall 34 is fixedly connected, and the inner chamber of piston assembly 3 is closed.Have at the center of second piston block 33 and allow piston rod 2
The manhole passed through, line is circumferentially uniform centered on the axis of second piston block 33 on second piston block 33 for throttle orifice 35
Be distributed it is multiple, throttle orifice 35 and for along the thickness direction of second piston block 33 through the through hole set, and first piston block 31
On each throttle orifice 35 respectively with a throttle orifice 35 on second piston block 33 to be coaxially disposed.
As shown in Figures 2 and 3, the 3rd damping fin 36 is the fan-shaped flake being arranged in the inner chamber of piston assembly 3, and the 3rd hinders
Buddhist nun's piece 36 and centered on the axis of piston assembly 3 line be circumferentially uniformly arranged in the inside of piston assembly 3 it is multiple, each 3rd
One end of damping fin 36 is fixedly connected with piston rod 2, and the other end is fixedly connected with second sidewall 34, i.e., in piston assembly 3
On axial direction, the 3rd damping fin 36 is distributed between first piston block 31 and second piston block 33, and the 3rd damping fin 36 and first is lived
There is gap between chock 31 and second piston block 33, there is space in the circumferential between two neighboring 3rd damping fin 36, should
Space, which connects with the throttle orifice 35 on first piston block 31 and second piston block 33 and forms the damping for allowing ER fluid to pass through, to be led to
Road, damp channel enable the upper chamber in the inner chamber body of cylinder barrel 1 to be connected with lower chambers.Due to the aperture of the damp channel of formation
Smaller, for ER fluid when flowing through damp channel, damp channel can produce damping.
As shown in Fig. 2, Fig. 3 and Fig. 6, the first damping fin 6 is located to be surrounded in the annular cavity formed by the first side wall 32,
Positioned at being surrounded by second sidewall 34 in the annular cavity formed, the first damping fin 6 and the second damping fin 7 divide second damping fin 7
Not Wei Yu the 3rd damping fin 36 side, the basic phase of shape of the first damping fin 6 and the second damping fin 7 and the 3rd damping fin 36
Together, also it is fan-shaped flake, two sides of the first damping fin 6 damp with the circular inner wall face of first piston block 31 and the 3rd respectively
Piece 36 is bonded, and two sides of the second damping fin 7 are pasted with the circular inner wall face of second piston block 33 and the 3rd damping fin 36 respectively
Close, the first damping fin 6 and the second damping fin 7 can cover respectively on first piston block 31 and second piston block 33 be located at it is adjacent
The throttle orifice 35 of clearance position alignment between two the 3rd damping fins 36, control opening and closing and the place of the throttle orifice 35 of this opening position
In opening or the quantity of the throttle orifice 35 of closed mode, and then realize the regulation of damp channel aperture size.
As shown in figs. 4 and 7, frequency damping adjustment device 4 includes being sheathed on piston rod 2 and with the first damping fin 6 connecting
The first adjusting set 41 for connecing and it is connected with the first adjusting set 41 and the first power for providing the driving force for rotating it produces
Component.First adjusting set 41 is both ends open, the circular tube shaped component of inner hollow, and the first adjusting set 41 is from first piston block 31
Center at pass through and insert inside piston assembly 3, one end of the first adjusting set 41 is fixedly connected with the first damping fin 6, another
End is connected positioned at the outside of cylinder barrel 1 and the end with the first power-generating assembly.First power-generating assembly produces driving force, makes first
Adjusting set 41 can rotate on piston rod 2, and the first adjusting set 41 drives the synchronous rotary of the first damping fin 6, and then can adjust
The position of first damping fin 6, realizes the regulation of damp channel aperture size.
As shown in Figure 7 to 9, the first power-generating assembly on the outside of damper body is electronic including being sequentially connected
Machine 46, the first transmission mechanism and the second transmission mechanism and first base 415, the relative position between first base 415 and cylinder barrel 1
Fixation is put, the second transmission mechanism is connected with the first adjusting set 41.Motor 46 is arranged in first base 415, the first driver
Structure is bevel gear mechanism, and the second transmission mechanism is cylindrical gear mechanism, and the first transmission mechanism includes the first driving tooth being meshed
The driven gear 43 of wheel 42 and first, the first driving gear 42 are arranged on the motor shaft of motor 46, and the first driven gear 43 can
Rotation is arranged in first base 415, and the second transmission mechanism includes the second driving gear 44 and the second driven tooth being meshed
Wheel 45, the second driving gear 44 of the second transmission mechanism is connected by the power transmission shaft of adjustable in length with the first driven gear 43,
Second driven gear 45 is fixedly installed in the first adjusting set 41.Motor 46 operates, and caused power is through the first transmission mechanism
The first adjusting set 41 is transferred to the second transmission mechanism, rotates the first adjusting set 41, and then rotates the first damping fin 6, is entered
The regulation that line position is put.
As shown in Figure 7 to 10, power transmission shaft is telescopic component, the length direction of power transmission shaft and the axis phase of cylinder barrel 1
Parallel, power transmission shaft is made up of the first axle body 47 and the second axle body 48, and the second axle body 48 is sheathed on the first axle body 47, the second axle
The inside of body 48 has the square opening for allowing the first axle body 47 to insert, and the part that the first axle body 47 is inserted in square opening is cross section in side
The sliding part of shape, in square sliding part insertion square opening, the first axle body 47 can be avoided relative to 48 turns of the second axle body
It is dynamic, it is ensured that the first axle body 47 and the second axle body 48 are only capable of doing relative rectilinear movement along its length, realize the tune of propeller shaft length
Section.The lower end of the second axle body 48 is connected with the first driven gear 43, and the second driving gear 44 is arranged on the first axle body 47, transmission
Axle makes the first driven gear 43 and the synchronous rotary of the second driving gear 44.Because the first adjusting set 41 is only capable of turning on piston rod 2
It is dynamic, therefore the upper end of the first axle body 47 is connected by first support 49 with piston rod 2, first support 49 is horizontal in the second driver
The top of structure, one end of first support 49 are sheathed on piston rod 2, and the other end of first support 49 is sheathed on the first axle body 47
On, the first axle body 47 and piston rod 2 are only capable of rotating relative to first support 49, therefore piston rod 2 is when being axially moveable, can be with
The first axle body 47 is driven synchronously to move along a straight line by first support 49.
As shown in figure 9, the first power-generating assembly also includes the first signal acquisition mechanism, the first signal acquisition mechanism bag
Include the signal gear 411 being rotatably arranged in first base 415 and the coaxially connected ratchet 410 of signal gear 411, set
Fixed cover 414 on piston rod 2, it is rotatably arranged on fixed cover 414 and the tooth for stirring the rotation of ratchet 410 refers to
413 and the speed probe 412 for the rotating speed of detection signal gear 411.Fixed cover 414 is fixedly connected with piston rod 2, and tooth refers to
Axis perpendicular and with the axis of ratchet 410 and signal gear 411 parallel, rotating speed of 413 rotation centerline with piston rod 2
Sensor 412 and motor 46 are connected with controller.It is to be connected by pin with fixed cover 414 that tooth, which refers to 413, and fixed cover
There is limitation tooth to refer to the position limiting structures of 413 rotational angles, when piston rod 2 drives fixed cover 414 towards close to cylinder barrel 1 on 414
When direction is moved, now tooth refers to 413 length direction and the fixations for referring to 413 in the state and tooth stretched out towards the outside of fixed cover 414
The axis perpendicular of set 414 and piston rod 2, the end that tooth refers to 413 contacts with ratchet 410, revolved so as to stir ratchet 410
Turn.Tooth refer to 413 separated with ratchet 410 after, piston rod 2 drive fixed cover 414 be directed away from cylinder barrel 1 direction movement when, when
Tooth refers to 413 and is moved to when being contacted with ratchet 410, and tooth, which refers to 413, to be overturn towards piston rod 2, and now tooth, which refers to 413, will not make ratchet
410 rotate, until when piston rod 2 drives fixed cover 414 again towards being moved close to the direction of cylinder barrel 1 next time, tooth refers to 413
Ratchet 410 can be stirred again to rotate in the same direction.
When there is vibration, the up-down vibration of piston rod 2, fixed cover 414 and tooth thereon refer to 413 and also moved up and down therewith, tooth
Refer to 413 in upward motion process the gear teeth meshing with ratchet 410 successively, so as to which driving pawl 410 rotates.Ratchet 410 and letter
Number gear 411 is fixed on the both ends of same axle, synchronizes rotation, the rotating speed of signal gear 411 is entered by speed probe 412
Row measurement, speed probe 412 are transmitted to controller using the rotating speed of signal gear 411 as input signal again, and controller is according to letter
The direction of motion, rotating speed and the working time of the size control motor 46 of number rotating speed of gear 411, (controller will be according to gear not
Same rotating speed is the direction of motion, rotating speed and the working time that the different vibration frequency control motor 46 of piston rod 2 rotates, most
The first damping fin 6 is set to rotate different angle eventually), motor 46 drives the first driving gear 42 to move, the band of the first driving gear 42
Dynamic first driven gear 43 operates, and the first driven gear 43 drives the second driving gear 44 to operate by power transmission shaft, and second actively
Gear 44 drives the second driven gear 45 to operate, and then drives the first damping fin 6 to rotate by the first adjusting set 41, passes through first
Damping fin 6 blocks throttle orifice 35 in piston assembly 3, increases ER fluid circulating resistance, and then the vibration that decays.When vibrating
When, the vibration frequency of damper is high, and the rotating speed of signal gear 411 will become big, otherwise the rotating speed of signal gear 411 diminishes；It is logical
The rotating speed size of the measurement of speed probe 412 is crossed, when controller will control the direction of motion, rotating speed and the work of motor 46
Between；When there is dither, motor 46 quickly moves, and quickly promotes the first adjusting set 41 to rotate by transmission mechanism, makes
First damping fin 6 is opened to rapidly maximum angle, and then covers most throttle orifices 35, quickly consumes vibrational energy；Work as vibration
When frequency is gradually reduced, motor 46, which will invert, reduces damping fin shielded area, and when vibration is wholly absent, damping fin is multiple
Position.When not vibrating, the first damping fin 6 is overlapping with the 3rd damping fin 36 in piston assembly 3.
As shown in figs. 2 and 11, amplitude damping adjusting means 5 includes being sheathed on piston rod 2 and with the second damping fin 7 connecting
The second adjusting set 51 for connecing and it is connected with the second adjusting set 51 and the second power for providing the driving force for rotating it produces
Component.As shown in figure 5, the second adjusting set 51 is both ends open, the circular tube shaped component of inner hollow, the second adjusting set 51 from second
Pass through and inserted inside piston assembly 3 at center on piston block 33, one end of the second adjusting set 51 is fixed with the second damping fin 7
Connection, the other end is located at the outside of cylinder barrel 1 and the end is connected with the second power-generating assembly.Second power-generating assembly produces driving
Power, the second adjusting set 51 is set to be rotated on piston rod 2, the second adjusting set 51 drives the synchronous rotary of the second damping fin 7, and then
The position of the second damping fin 7 can be adjusted, realizes the regulation of damp channel aperture size.
As is illustrated by figs. 11 and 12, the second power-generating assembly on the outside of damper body include second base 52,
The bearing 53 that is arranged in second base 52, the Rocker arm 54 being rotatably arranged on bearing 53, it is connected with one end of Rocker arm 54
Driver 56 and the semicolumn rack 55 that is connected by bearing pin 511 with the other end of Rocker arm 54, the appearance of the second adjusting set 51
Face is provided with the external screw thread that is engaged with semicolumn rack 55, the axis of bearing pin 511 and the rotation centerline of Rocker arm 54 it is parallel and with
The axis perpendicular of piston rod 2.Semicolumn rack 55 is arranged on the end of Rocker arm 54 by bearing pin 511, semicolumn rack 55
Set tooth and the external screw thread in the second adjusting set 51 are at a fully engaged on outer surface, can be driven when semicolumn rack 55 moves up and down
Dynamic second adjusting set 51 rotates to an angle (the cooperation transmission of semicolumn rack and the second adjusting set and rack drives worm mechanism
It is similar, but semicolumn rack have to be larger than angle of friction with the lead angle that the second adjusting set engages, and prevent in both motion processes
Generation self-locking, it is 7 full opening of angle of the second damping fin that semicolumn rack 55, which drives the maximum angle of the second adjusting set 51 rotation,
Degree), and then the second damping fin 7 is rotated, carry out the regulation of position.
As shown in figure 15, semicolumn rack and the second adjusting set be in transmission process, the second adjusting set engaging portion P points by
Power is analyzed as follows, and rack concentrates the normal load F acted at sleeve node PnThree mutually perpendicular component can be decomposed into,
That is force of periphery Ft, radial load FrAnd axial force Fa。
When disregarding frictional force, each power size is as follows：
Ft=Fn cosαn sinθ (1)
Fa=Fn cosαn cosθ (2)
Fr=Fn sinαn (3)
M=Ftr (4)
FnThe normal load acted at the node P in the second adjusting set, unit are concentrated for rack：N；
FtFor the force of periphery, unit：N；
FrFor radial load, unit：N；
FaFor axial force, unit：N；
F is coefficient of friction；
fFnFor frictional force, the frictional force fF of circumference force direction can be decomposed intonThe cos θ and frictional force fF of axial directionnSin θ,
Unit：N；
M be the second adjusting set circumference torque, unit：N*m；
αnFor pressure angle, unit：rad；
θ be the second adjusting set on externally threaded lead angle, unit：rad.
As force of periphery FtCaused torque is more than circumferencial direction friction moment, the rotation of the adjusting set of semicolumn rack drives second
Turn, i.e.,
M>frFncosθ (5)
Avoid that self-locking occurs in semicolumn rack and the second adjusting set motion process, lead angle θ have to be larger than angle of friction β
(β=arctanf), i.e.,
θ>β (6)
It can show that the condition that semicolumn rack moves with the second adjusting set is by (1)~(6) formula：
Note：Pressure angle αnTypically take
As preferable, driver 56 is the double acting hydraulic cylinder being arranged in second base 52, the cylinder body of hydraulic cylinder with
Second base 52 is rotatablely connected, and the piston rod 2 of hydraulic cylinder is rotatablely connected with the end of Rocker arm 54, and the end of second base 52 is arranged
In relative position is fixed on piston rod 2 and between second base 52 and piston rod 2, the second adjusting set 51 is relative to second base 52
It is only capable of rotating, piston rod 2 can drive its part thereon of second base 52 synchronously to move along a straight line when being axially moveable.
As illustrated in figures 11 and 13, amplitude damping adjusting means 5 also includes secondary signal collecting mechanism, and the secondary signal is adopted
Collecting mechanism includes the 3rd base 59, the buffer spring 57 being arranged on the 3rd base 59 and is arranged on the 3rd base 59 and is used for
The displacement transducer 58 of the displacement of piston rod 2 is detected, with piston rod 2 to be coaxially disposed, buffer spring 57 presss from both sides buffer spring 57
Between the 3rd base 59 and the end of piston rod 2, buffer spring 57, which is used to apply piston rod 2, makes it be directed away from the 3rd bottom
The elastic acting force of the direction movement of seat 59.Displacement transducer 58 is connected with controller, the phase between the 3rd base 59 and cylinder barrel 1
Position is fixed, displacement transducer 58 is mainly to measure the distance between end and the 3rd base 59 of piston rod 2.
As shown in Figure 11, Figure 13 and Figure 14, amplitude damping adjusting means 5 also includes the hydraulic pressure being arranged on the 3rd base 59
Pump 510, magnetic valve 512 and liquid reserve tank 513, the oil inlet of hydraulic pump 510 are connected with liquid reserve tank 513, and driver 56 is double acting
Hydraulic cylinder, magnetic valve 512 are two-position four-way solenoid valve, and the cylinder body of hydraulic cylinder, which is provided with, to be used for into the fuel-displaced He of the first oilhole 514
Second oilhole 515, the oil-out of hydraulic pump 510 are connected with the oil inlet of magnetic valve 512, the oil-out and liquid storage of magnetic valve 512
Case 513 connects, and two other working hole of magnetic valve 512 connects with the first oilhole 514 of hydraulic cylinder and the second oilhole 515 respectively
Connect, form circulation hydraulic circuit, hydraulic pump 510 is used to provide driver 56 in hydraulic oil, and magnetic valve 512 is used to control oil circuit to change
It is connected to and with controller, controller controls the opening and closing of magnetic valve 512.
The operation principle of amplitude damping adjusting means 5 is as follows：
Displacement transducer 58 is mainly to measure the lower end of piston rod 2 and the distance of the 3rd base 59,2 one motion weeks of piston rod
Displacement signal of the interim minimum range as controller control hydraulic pump 510.Here we provide piston assembly 3 in cylinder barrel 1
Meta is set to starting point (first stage), and piston assembly 3 is moved downwardly to minimum point (second stage), piston assembly from middle starting point
3 move up to highest from the centre position that minimum point is moved upwards (phase III), then piston assembly 3 from centre position again
Locate (fourth stage), finally from the centre position that highest point moves downward (the 5th stage), above-mentioned motion process is piston rod 2
One period of motion of (piston assembly 3 be integrally fixed at piston rod 2 together with).Each cycle is more each by fluid controller
The bottom of step piston bar 2 and the size of the distance of the 3rd base 59, it regard the distance of minimum as this period offset DT as displacement signal
Signal.Controller first according to the displacement signal (i.e. the minimum range of the bottom of piston rod 2 and mounting seat) of a cycle and
The pump oil amount of Numerical Control hydraulic pump 510 of displacement signal, adjust damping fin aperture, hereafter the displacement signal in each cycle with it is upper
A cycle displacement signal is compared, by judging its size, to control the unfolding mode of magnetic valve 512, and according to both
Size of the difference changes the pump oil amount of hydraulic pump 510, controls the aperture of damping fin.If this cycle will than upper period offset DT signal
Greatly, damping fin aperture accordingly reduces, conversely, damping fin aperture accordingly increases.
When not vibrating, the second damping fin 7 overlaps with the 3rd damping fin 36；When vibrating, piston rod 2 moves
During a cycle, by the lower end of piston rod 2 that displacement transducer 58 detects and the distance signal of the 3rd base 59, and signal is passed
Controller is passed, controller makes hydraulic pump 510 work by displacement signal, and hydraulic oil flows to magnetic valve by hydraulic pump 510
512, now magnetic valve a ends be powered, hydraulic oil flows to the first oilhole 514 by magnetic valve, and hydraulic oil enters hydraulic cylinder, hydraulic cylinder
Elongation produces driving force, and then makes semicircle stud wheel drive the second adjusting set 51 to rotate, and the second damping fin 7 rotates with opening,
Now controller makes hydraulic pump 510 be stopped, and remains on the second damping fin 7, and section is covered by the second damping fin 7
Discharge orifice 35, increase ER fluid circulating resistance, and then the vibration that decays.Hereafter the period of motion of piston, displacement transducer 58 detect
Displacement signal compared with upper period offset DT signal, if this cycle displacement signal than upper period offset DT signal will
Small, control oil circuit is identical with the period 1, by controlling the pump oil amount of hydraulic pump 510 to increase damping fin aperture, and keeps aperture to enter
Enter next cycle；If this cycle displacement signal is bigger than upper period offset DT signal, the controller of hydraulic pump 510 is believed according to displacement
Number data start and hydraulic pump 510 and change its pump oil amount, and control magnetic valve b ends to be powered, make hydraulic oil through the second oilhole
515 enter hydraulic cylinder, shrink hydraulic cylinder, and then make semicolumn rack 55 drive the second adjusting set 51 to reversely rotate, and make second
The aperture of damping fin 7 reduces, and hydraulic pump 510 is stopped, and the second damping fin 7 keeps the aperture, reduces damping force.Through repeatedly adjusting
Section, makes vibration disappearance, and damping fin resets.Hydraulic system can be vibrated according to various amplitude, make the difference of running of hydraulic power oil amount, change
The aperture of variable damping piece is that it blocks the quantity of throttle orifice 35, so that changing damping force, vibration is faded away.
As preferable, the first damping fin 6 sets multiple, and multiple first damping fins 6 are edge in the first adjusting set 41
Circumferentially it is uniformly distributed.Second damping fin 7 be also provided with it is multiple, and multiple second damping fins 7 in the second adjusting set 51 for circumferentially
It is uniformly distributed.The quantity of first damping fin 6 and the second damping fin 7 is equal, and the quantity of the 3rd damping fin 36 is the He of the first damping fin 6
The quantity sum of second damping fin 7, each damping fin 7 of first damping fin 6 and second are respectively used to per the two neighboring 3rd resistance
Gap between Buddhist nun's piece 36 is worked, and the material of the first damping fin 6, the second damping fin 7 and the 3rd damping fin 36 is preferably to steep
Foam metal.In the present embodiment, as shown in Figures 3 to 6, the first damping fin 6 and the second damping fin 7 are respectively provided with two, the 3rd resistance
Buddhist nun's piece 36 sets four.First damping fin 6 and the second damping fin 7 can rotate freely in the inner chamber of piston assembly 3.It is being not required to
When adjusting damping force, two the first damping fins 6 overlap with two the 3rd damping fins 36, two the second damping fins 7 with
Two the 3rd damping fins 36 overlap, so as to not hinder damping fluid to flow through throttle orifice 35, when needing to adjust damping force, the
One damping fin 6 and the second damping fin 7 are rotated a certain angle, and block throttle orifice 35, the throttle orifice for making ER fluid circulate
35, which tail off, increases damping force, and then consumes vibrational energy.
As depicted in figs. 1 and 2, the one end open of cylinder barrel 1 is provided with the first end cap 8, and another end opening is provided with the second end
Lid 9, the first end cap 8 and the second end cap 9 respectively close one end of cylinder barrel 1, and have at the center of the first end cap 8 and allow first
The through hole that adjusting set 41 passes through, has at the center of the second end cap 9 and allows the through hole that the second adjusting set 51 passes through, and piston rod 2 passes through
First adjusting set 41 and the both ends of the second adjusting set 51 and piston rod 2 extend out to the first adjusting set 41 and the second adjusting set 51 respectively
Outside.First end cap 8 and the second end cap 9 need to be separately energized, and in two end caps, when one of end cap is uniformly distributed just
During electric charge, another end cap is uniformly distributed negative electrical charge, so as to form electric field in the inner chamber of cylinder barrel 1.When not vibrating, first
The no power of 8 and second end cap of end cap 9, ER fluid can pass freely through the throttle orifice 35 of piston assembly 3；When there is vibration, the
One end cap 8 and the second end cap 9 are powered, and the electric field that two end caps are formed changes electric-field intensity with oscillation intensity, becomes ER fluid
It is sticky, there is during the throttle orifice 35 for flowing through piston assembly 3 resistance, produced inside ER fluid and with the friction of the inwall of cylinder barrel 1
Heat energy, and then consume vibrational energy.
When the electro-rheological fluid damper of the present invention is used on automobile, the top of piston rod 2 is arranged on vehicle frame, cylinder barrel 1 with
First base 415 and second base 52 are placed in vehicle bridge, during work, the motion for the buffer spring 57 that piston rod 2 passes through bottom,
Relative motion can be produced with cylinder barrel 1.
The present invention is exemplarily described above in association with accompanying drawing.Obviously, present invention specific implementation is not by above-mentioned side
The limitation of formula.As long as employ the improvement of the various unsubstantialities of inventive concept and technical scheme of the present invention progress；Or not
It is improved, the above-mentioned design of the present invention and technical scheme are directly applied into other occasions, in protection scope of the present invention
Within.
Claims (10)
1. electro-rheological fluid damper, it is characterised in that including：
Cylinder barrel, its inside have ER fluid；
Piston assembly, it is arranged in cylinder barrel, and with allowing multiple throttle orifices that ER fluid passes through；
Piston rod, it is disposed through cylinder barrel and piston assembly, and is connected with piston assembly；And
Damping adjustment device, it includes being rotatably arranged on inside piston assembly and is turned on and off state for adjusting to be in
Throttling hole number the first damping fin and the second damping fin, the frequency damping adjustment device that is connected with the first damping fin and with
The amplitude damping adjusting means of second damping fin connection；
Wherein, the frequency damping adjustment device includes for being sheathed on the piston rod and being connected with first damping fin
One adjusting set and be connected with the first adjusting set and for provide make its rotate driving force the first power-generating assembly；
First power-generating assembly includes motor, the first transmission mechanism, the second transmission mechanism and first being sequentially connected
Signal acquisition mechanism, the second transmission mechanism are connected with first adjusting set, the first signal acquisition mechanism include signal gear, with
The coaxially connected ratchet of signal gear, the fixed cover being sheathed on piston rod, it is rotatably arranged on fixed cover and for dialling
The tooth of dynamic ratchet rotation refers to and the speed probe for detection signal gear rotational speed；
The amplitude damping adjusting means includes the second tune for being sheathed on the piston rod and being connected with second damping fin
Section covers and is connected with the second adjusting set and makes the second power-generating assembly of its driving force rotated for offer；
Second power-generating assembly includes rocking arm, the driver and and rocking arm being connected with one end of rocking arm of rotatable setting
Other end connection semicolumn rack, the outer surface of second adjusting set is provided with the external screw thread engaged with semicolumn rack.
2. electro-rheological fluid damper according to claim 1, it is characterised in that first adjusting set is both ends open, interior
The hollow circular tube shaped component in portion, the first adjusting set are inserted inside piston assembly, and one end of the first adjusting set is consolidated with the first damping fin
Fixed connection, the other end is located on the outside of cylinder barrel and the end is connected with the first power-generating assembly.
3. electro-rheological fluid damper according to claim 2, it is characterised in that first damping fin sets multiple and more
Individual first damping fin is to be uniformly distributed circumferentially in first adjusting set.
4. electro-rheological fluid damper according to claim 2, it is characterised in that first transmission mechanism is bevel gear machine
Structure, the first transmission mechanism include the first driving gear and the first driven gear being meshed, and the first driving gear is arranged at electronic
On the motor shaft of machine, the first driven gear is rotatably arranged in first base, the relative position between first base and cylinder barrel
Put fixation.
5. electro-rheological fluid damper according to claim 4, it is characterised in that second transmission mechanism is Cylinder Gear turbine
Structure, the driving gear of the second transmission mechanism are connected by the power transmission shaft of adjustable in length with first transmission mechanism, and second passes
The driven gear of motivation structure is connected with first adjusting set.
6. electro-rheological fluid damper according to claim 5, it is characterised in that the fixed cover is fixedly connected with piston rod,
Signal gear is is rotatably arranged in first base, the rotation centerline and the axis perpendicular of piston rod that tooth refers to and and spine
Wheel is parallel with the axis of signal gear；It is to be connected by pin with fixed cover that tooth, which refers to, and there is limitation tooth to refer to angle of rotation on fixed cover
The position limiting structure of degree, when piston rod drives fixed cover, towards close to during the movement of the direction of cylinder barrel, it is in towards fixed cover that now tooth, which refers to,
The length direction that the state and tooth that outside is stretched out refer to and fixed cover and the axis perpendicular of piston rod, the end that tooth refers to connects with ratchet
Touch, to stir ratchet rotation.
7. electro-rheological fluid damper according to claim 1, it is characterised in that second adjusting set is both ends open, interior
The hollow circular tube shaped component in portion, the second adjusting set are inserted inside piston assembly, and one end of the second adjusting set is consolidated with the second damping fin
Fixed connection, the other end is located on the outside of cylinder barrel and the end is connected with the second power-generating assembly.
8. electro-rheological fluid damper according to claim 7, it is characterised in that second power-generating assembly includes revolving
Turn rocking arm, the driver being connected with one end of rocking arm and the semicolumn rack being connected with the other end of rocking arm set, described the
The outer surface of two adjusting sets is provided with the external screw thread engaged with semicolumn rack, and semicolumn rack passes through bearing pin and the other end of rocking arm
Connection, the axis of the bearing pin and rotation centerline of rocking arm is parallel and axis perpendicular with piston rod, semicolumn rack
Set tooth and the external screw thread in the second adjusting set are at a fully engaged on outer surface, and the can be driven when semicolumn rack moves up and down
Two adjusting sets rotate to an angle, and then rotate the second damping fin, carry out the regulation of position.
9. electro-rheological fluid damper according to claim 8, it is characterised in that the amplitude damping adjusting means also includes the
Binary signal collecting mechanism, the secondary signal collecting mechanism include being arranged at buffer spring below the piston rod and for detecting
The displacement transducer of piston rod displacement.
10. electro-rheological fluid damper according to any one of claims 1 to 9, it is characterised in that the piston assembly includes relative
The first piston half portion and second piston half portion of setting and the 3rd damping being connected with second piston half portion and the piston rod
Piece.
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| CN201610748306.4A CN106090110B (en) | 2016-08-29 | 2016-08-29 | Electro-rheological fluid damper |
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| CN201610748306.4A CN106090110B (en) | 2016-08-29 | 2016-08-29 | Electro-rheological fluid damper |
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| CN106090110B true CN106090110B (en) | 2017-12-22 |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| US10274040B2 (en) * | 2017-04-06 | 2019-04-30 | GM Global Technology Operations LLC | Active damper for torsional vibration and noise mitigation in a driveline |
| CN107606042B (en) * | 2017-11-13 | 2018-10-26 | 西格迈股份有限公司 | A kind of automobile shock stored energy mechanism |
| CN110124325B (en) * | 2019-05-22 | 2020-10-02 | 浙江榜榜实业有限公司 | Protection seat for playground |
| CN114909423A (en) * | 2022-06-21 | 2022-08-16 | 集美大学 | Novel magnetorheological suspensions attenuator |
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| JPH0257521A (en) * | 1988-08-24 | 1990-02-27 | Toyo Seikan Kaisha Ltd | Liquefied gas flowing apparatus |
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| US4516606A (en) * | 1983-02-16 | 1985-05-14 | Exxon Research And Engineering Co. | Variable orifice valve assembly |
| CN201475233U (en) * | 2009-08-03 | 2010-05-19 | 常州昊邦汽车零部件有限公司 | Adjustable damper |
| CN201547166U (en) * | 2009-09-10 | 2010-08-11 | 浙江吉利控股集团有限公司 | Electrorheological fluid vibration damper |
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| CN106090110A (en) | 2016-11-09 |
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Effective date of registration: 20201218 Address after: No.99, Weier Road, Quanjiao Economic Development Zone, Chuzhou City, Anhui Province Patentee after: CHUZHOU BOJIE TECHNOLOGY Co.,Ltd. Address before: 241000 No. 8 Beijing Middle Road, Jiujiang District, Wuhu City, Anhui Province Patentee before: ANHUI POLYTECHNIC University |
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Denomination of invention: ER Damper Effective date of registration: 20211108 Granted publication date: 20171222 Pledgee: Quanjiao enterprise financing Company limited by guarantee Pledgor: CHUZHOU BOJIE TECHNOLOGY CO.,LTD. Registration number: Y2021980011943 |
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Date of cancellation: 20220621 Granted publication date: 20171222 Pledgee: Quanjiao enterprise financing Company limited by guarantee Pledgor: CHUZHOU BOJIE TECHNOLOGY CO.,LTD. Registration number: Y2021980011943 |
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