CN102979849B - Active-type piezoelectric hydraulic damper - Google Patents
Active-type piezoelectric hydraulic damper Download PDFInfo
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- CN102979849B CN102979849B CN201210541583.XA CN201210541583A CN102979849B CN 102979849 B CN102979849 B CN 102979849B CN 201210541583 A CN201210541583 A CN 201210541583A CN 102979849 B CN102979849 B CN 102979849B
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- 238000013016 damping Methods 0.000 claims abstract description 23
- 239000012530 fluid Substances 0.000 abstract description 23
- 239000006096 absorbing agent Substances 0.000 abstract 1
- 230000035939 shock Effects 0.000 abstract 1
- 230000000694 effects Effects 0.000 description 12
- 230000001105 regulatory effect Effects 0.000 description 6
- 238000010586 diagram Methods 0.000 description 4
- 230000033228 biological regulation Effects 0.000 description 2
- 230000001629 suppression Effects 0.000 description 2
- 230000008878 coupling Effects 0.000 description 1
- 238000010168 coupling process Methods 0.000 description 1
- 238000005859 coupling reaction Methods 0.000 description 1
- 230000008030 elimination Effects 0.000 description 1
- 238000003379 elimination reaction Methods 0.000 description 1
- 238000005265 energy consumption Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 238000005429 filling process Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 230000002093 peripheral effect Effects 0.000 description 1
- 238000005086 pumping Methods 0.000 description 1
- 230000005855 radiation Effects 0.000 description 1
- 239000000725 suspension Substances 0.000 description 1
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Abstract
The invention relates to an active-type piezoelectric hydraulic damper, belonging to shock absorbers. The active-type piezoelectric hydraulic damper is characterized in that an end cover is fixedly arranged on a cylinder body, and a cavity of the cylinder body is partitioned into an upper cylinder cavity and a lower cylinder cavity by a big piston; a balance spring is pressed in the lower cylinder cavity by the big piston, and a piston rod flange is fixedly arranged on the big piston; a piezoelectric stack is arranged in a piston rod and is used for pressing a small piston, a valve core and a reset spring in the cavity of the big piston; a disc spring is pressed between the small piston and the piston rod flange; a valve spring and a valve ball are crimped in a cavity of the piston core in sequence by the small piston to form a one-way valve; the cavity of the valve core is communicated with an upper valve cavity, a lower valve cavity and an annular slot in the valve core; and the annular slot is communicated with a left runner and a right runner in the big piston to form a damper valve, and the left runner and the right runner are further communicated with the upper cylinder cavity and the lower cylinder cavity. The active-type piezoelectric hydraulic damper has the advantages of simple structure, small size, no leakage and or electromagnetic interference and wide damping adjusting range because the piezoelectric stack in the piston rod drives an additional fluid cavity piston to adjust the damper value in the piston.
Description
Technical field
The invention belongs to antivibration area, be specifically related to a kind of Active-type piezoelectric hydraulic damper, be applicable to vibration suppression and the elimination of the traffic tool, machinery etc.
Background technique
Hydraulic damper is widely used in the vibration control field of the traffic tool, machinery etc.Early stage passive type hydraulic damper structure is simple, cost is low, technology is more ripe, but because damping is non-adjustable, the adaptability of its effectiveness in vibration suppression and environment is poor, be unsuitable for some and require the good occasion of vibration control effect, as motor car engine and vehicle frame suspension, Large-Scale Precision Instrument and Equipment vibration damping etc.Therefore, there has been proposed active, semi-active type hydraulic damper with adjustable, namely utilize motor-driven hydraulic pumps to provide power and carried out the active adjustable damper that controls by electromagnetic switch/overflow/reduction valve, as Chinese invention patent CN1367328A, CN101392809A etc.Ratio in the non-adjustable hydraulic damper of passive type, the control effects of active hydraulic damper with adjustable is good, vibration environment adaptable, succeeded application in automobile active engine mount etc.; But existing active hydraulic damper mostly needs larger pumping plant carry out driving and jointly control in conjunction with multiple solenoid valve, therefore systems bulky, connection and control more complicated, energy consumption is high, reliability is lower, application on have some limitations.In view of problems such as existing active hydraulic damper self structure, control ability and the supplies of dependence outside energy, claimant once proposed a kind ofly to carry out the semi-active type self energizing adjustable damper of damping adjustment based on piezoelectric stack transducer and fluid coupling recovered energy, i.e. Chinese patent 201110275849.6, can solve some drawback of conventional active hydraulic damper to a certain extent; But regulate because this damper utilizes piezoelectric stack Direct driver spool to realize damping, and the flexible ability of piezoelectric stack under voltage effect is extremely limited, only micron order, therefore damping regulating power is low, is unsuitable for the occasion that regulation range is larger.
Summary of the invention
The present invention proposes a kind of Active-type piezoelectric hydraulic damper, with solve damping regulating power existing for existing active hydraulic damper and piezo-stack type self-energized adjustable hydraulic damper low, be unsuitable for the larger occasion problem of regulation range.
The technological scheme that the present invention takes is: end cap is fixed by screws on cylinder body, and large piston sleeve is connected in inner chamber of cylinder block and by inner chamber of cylinder block and is separated into upper cylinder half chamber and lower cylinder chamber; Balance spring is crimped in lower cylinder chamber by large piston, and the flange of piston rod end is fixed by screws on large piston; Piezoelectric stack is placed in the inner chamber of piston rod, and is crimped in the ladder-type inner chamber of large piston by small piston, spool and Returnning spring successively; Belleville spring is crimped with and small piston upper shoulder leans on the flange of piston rod end between small piston and the flange of piston rod end; Jointly form uuper valve chamber between small piston and large piston and spool, jointly form lower valve chamber between spool and large piston, uuper valve chamber is communicated with accumulator by pipeline; Valve spring and valve ball are crimped in the inner chamber of spool by small piston successively, and the inner chamber of spool, valve spring and valve ball form one-way valve jointly; The inner chamber of spool is communicated with uuper valve chamber by the translot of spool upper end, is communicated with by the vertical hole on spool with lower valve chamber, is also communicated with the annular groove on spool by the vertical hole on spool and cross-drilled hole; Left runner on described annular groove and large piston and right flow passage, described left runner and right runner are also communicated with lower cylinder chamber with described upper cylinder half chamber respectively; Described annular groove and described left runner and right runner are configured for the orifice valve that damping regulates jointly.
Be full of fluid in work front damper system, upper and lower cylinder chamber and upper lower valve chamber fluid pressure equal, be accumulator set pressure P
0.During damper inoperative, piezoelectric stack no electric circuit and not by pretightening force effect; Large piston and small piston are in state of equilibrium under the effect of hydrodynamic pressure and each spring, and orifice valve is in normally open, system damping is little.
When needing damping adjusting, piezoelectric stack is energized and extends, and promotes small piston and moves downward, thus make uuper valve chamber fluid pressure increase to P and make one-way valve maintain closed condition; External force F suffered by spool 7 upper end
s=F
t8+ π r
2p is greater than external force F suffered by lower end
x=F
t10+ π r
2p
0time, namely uuper valve chamber fluid pressure increases to P > [F
t10-F
t8+ π r
2p
0]/(π r
2) time, spool starts to move downward, and makes that the flow area of orifice valve reduces, damping increases, in formula: F
t8and F
t10be respectively valve spring and Returnning spring to the active force of spool, r is spool radius; When the elongation of piezoelectric stack under voltage effect is L=V η, then the aperture regulated quantity of amount of movement, the i.e. orifice valve of spool is l=(R/r)
2l=(R/r)
2v η, wherein V is the driving voltage of piezoelectric stack, and η is the coefficient relevant with the physical dimension of piezoelectric stack, belleville spring, Returnning spring and valve spring and hydrodynamic pressure, and R is the radius of large piston; Therefore, when large piston diameter is much larger than small piston diameter, the elongation of piezoelectric stack will be exaggerated n=l/L=(R/r)
2doubly, i.e. the regulating power of the damping of orifice valve is exaggerated n=(R/r)
2doubly.
When piezoelectric stack power-off or driving voltage reduce, piezoelectric stack starts to shrink under himself resilient force, small piston and spool also all move upward under the comprehensive function of fluid and each related springs, thus make that the aperture of orifice valve increases gradually, damping reduces gradually; When the shoulder of small piston leans on the flange of piston rod and spool upper-end surface leans on small piston lower surface, damper returns to original state, and now the aperture of orifice valve is maximum, damping is minimum.
Features and advantages of the present invention is: between piezoelectric stack and spool, 1. increase by one can the additional streams body cavity of fill fluid voluntarily, and being combined with less spool by larger piston increases spool travel amount, thus damping adjustment and control range large; 2. orifice valve and piezoelectric stack are placed in piston and piston rod, and without the need to peripheral unit such as motor, pump, solenoid valves, therefore volume is little, structure is simple, level of integration is high, good airproof performance, and easily adopt longer piezoelectric stack to realize large-scale damping adjustment; 3. be not subject to fluid force effect during piezoelectric stack inoperative, therefore after energising, amount of deformation is large, energy converting between mechanical efficiency is high; 4. adopt non magnetic piezoelectric stack to drive and control valve core movement, do not produce/not by electromagnetic interference, be more suitable for high magnetic fields, strong radiation environment.Therefore, Active-type piezoelectric hydraulic damper of the present invention, except being applicable to the large-scale traffic tool and machine tool, is also suitable for the microsystem such as Aero-Space, intelligent structure and tele-control system.
Accompanying drawing explanation
Structural profile schematic diagram when Fig. 1 is a preferred embodiment of the present invention damper inoperative;
Structural profile schematic diagram when Fig. 2 is the work of a preferred embodiment of the present invention a preferred embodiment of the present invention damper;
Fig. 3 is the I portion enlarged view of Fig. 1;
Fig. 4 is the structural profile schematic diagram of the large piston of a preferred embodiment of the present invention;
Fig. 5 is the structural profile schematic diagram of a preferred embodiment of the present invention spool;
Fig. 6 is the left view of Fig. 5.
Embodiment
End cap 3 is fixed by screws on cylinder body 4, and large piston 5 is socketed in cylinder body 4 inner chamber and by cylinder body 4 inner chamber and is separated into upper cylinder half chamber C11 and lower cylinder chamber C12; Balance spring 10 is crimped in lower cylinder chamber C12 by large piston 5, and the flange 102 of piston rod 1 end is fixed by screws on large piston 5; Piezoelectric stack 2 is placed in the inner chamber 101 of piston rod 1, and is crimped in the ladder-type inner chamber C2 of large piston 5 by small piston 6, spool 7 and Returnning spring 11 successively; Belleville spring 12 is crimped with and the shoulder 601 of small piston 6 leans on the flange 102 of piston rod 1 between the flange 102 of small piston 6 and piston rod 1; Jointly form uuper valve chamber C21 between small piston 6 and large piston 5 and spool 7, spool 7 and jointly form lower valve chamber C22 between piston 5 greatly, uuper valve chamber C21 is communicated with accumulator 13 by pipeline; Valve spring 8 and valve ball 9 are crimped in the inner chamber 705 of spool 7 by small piston 6 successively, and the inner chamber 705 of spool 7, valve spring 8 and valve ball 9 form one-way valve F1 jointly; The inner chamber 705 of spool 7 is communicated with uuper valve chamber C21 by the translot 704 of spool 7 upper end, be communicated with lower valve chamber C22 by the vertical hole 701 on spool 7, be also communicated with the annular groove 703 on spool by the vertical hole 701 on spool 7 and cross-drilled hole 702; Annular groove 703 on spool 7 is communicated with right runner 501 with the left runner 502 on large piston 5, and described left runner 502 is communicated with right runner 501 and is also communicated with lower cylinder chamber C12 with upper cylinder half chamber C11 respectively; Annular groove 703 on spool 7 and the left runner 502 on large piston 5 and right runner 501 are configured for the orifice valve F2 that damping regulates jointly.
Be full of fluid by damper before work, in fluid filling process, one-way valve F1 opens, and fluid enters in uuper valve chamber C21 through one-way valve F2; After fluid filling, the hydrodynamic pressure in upper cylinder half chamber C11, lower cylinder chamber C12, uuper valve chamber C21 and lower valve chamber C22 is equal, is the set pressure P of accumulator 12
0.
During damper inoperative, piezoelectric stack 2 no electric circuit; The fluid force of large piston about 5 both sides is equal, under the effect of vibration mass M and balance spring 10, be in state of equilibrium; Small piston 6 leans on the flange 102 of piston rod 1 under the effect of hydrodynamic pressure, Returnning spring 11 and belleville spring 12, to avoid making piezoelectric stack 2 produce precompression by fluid matasomatism; Suffered by spool about 7 two ends, fluid force is equal, the lower surface at small piston 6 is leaned under the effect of Returnning spring 11 and valve spring 8, to guarantee that orifice valve F2 is in normally open, namely the left runner 502 on large piston 5 is communicated with the annular groove 703 on spool 7 completely with right runner 501, and now the damping of system is little;
When vibration mass M up-down vibration and when need control, piezoelectric stack 2 is energized and extends, promote small piston 6 and move downward, thus uuper valve chamber C21 fluid pressure is increased and makes one-way valve F2 maintain closed condition; The increase of uuper valve chamber C21 fluid pressure makes external force F suffered by spool 7 upper end
s=F
t8+ π r
2p is greater than external force F suffered by lower end
x=F
t10+ π r
2p
0time, namely the pressure of uuper valve chamber C21 inner fluid increases to P > [F
t10-F
t8+ π r
2p
0]/(π r
2) time, spool 7 starts to move downward, and the vertical hole 701 of the fluid in lower valve chamber C22 on spool 7, cross-drilled hole 702 and annular groove 703 escape and enter in the left runner 502 of large piston 5; Spool 7 moves downward and causes the flow area of orifice valve F2 to reduce, thus serves the effect increasing damping, in above-mentioned formula: F
t8and F
t10be respectively the active force of valve spring 8 and Returnning spring 10 pairs of spools, r is spool radius; If the elongation of piezoelectric stack 2 under voltage effect is L=V η, then the aperture regulated quantity of amount of movement, i.e. the orifice valve F2 of spool 7 is l=(R/r)
2l=(R/r)
2v η, wherein: V is the driving voltage of piezoelectric stack 2, η is the coefficient relevant with the physical dimension of piezoelectric stack 2, belleville spring 12, Returnning spring 10 and valve spring 8 and hydrodynamic pressure, and R is the radius of large piston 5; Therefore, when the diameter of large piston 5 is much larger than the diameter, namely of small piston 6
time, the elongation of piezoelectric stack 2 will be exaggerated n=l/L=(R/r)
2doubly, i.e. the regulating power of the damping of orifice valve is exaggerated (R/r)
2doubly;
When piezoelectric stack 2 power-off or driving voltage reduce, piezoelectric stack 2 starts to shrink under himself resilient force, small piston 6 and spool 7 also all move upward under the comprehensive function of fluid and each related springs, thus make that the aperture of orifice valve F2 increases gradually, damping reduces gradually; Meanwhile, lower valve chamber C22 fluid pressure reduces, and fluid enters lower valve chamber C22 from the annular groove 703 of the left runner 502 large piston 5 on spool 7, cross-drilled hole 702 and vertical hole 701; When the shoulder 601 of small piston 6 leans on the flange 102 of piston rod 1 and the upper-end surface of spool 7 leans on the lower surface of small piston 6, damper returns to original state, and now the aperture of orifice valve F2 is maximum, damping is minimum.
Claims (1)
1. an Active-type piezoelectric hydraulic damper, end cap is fixed by screws on cylinder body, and large piston sleeve is connected in inner chamber of cylinder block and by inner chamber of cylinder block and is separated into upper cylinder half chamber and lower cylinder chamber, and the flange of piston rod end is fixed by screws on large piston; Belleville spring is crimped with and the shoulder of small piston leans on the flange of piston rod end between small piston and the flange of piston rod end, uuper valve chamber is communicated with accumulator by pipeline, it is characterized in that: balance spring is crimped in lower cylinder chamber by large piston, piezoelectric stack is placed in the inner chamber of piston rod, and is crimped in the ladder-type inner chamber of large piston by small piston, spool and Returnning spring successively; Jointly form uuper valve chamber between small piston and large piston and spool, jointly form lower valve chamber between spool and large piston, valve spring and valve ball are crimped in the inner chamber of spool by small piston successively, and the inner chamber of spool, valve spring and valve ball form one-way valve jointly; The inner chamber of spool is communicated with uuper valve chamber by the translot of spool upper end, is communicated with by the vertical hole on spool with lower valve chamber, is also communicated with the annular groove on spool by the vertical hole on spool and cross-drilled hole; Left runner on described annular groove and large piston and right flow passage, described left runner and right runner are also communicated with lower cylinder chamber with upper cylinder half chamber respectively; Described annular groove and described left runner and right runner are configured for the orifice valve that damping regulates jointly.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210541583.XA CN102979849B (en) | 2012-12-13 | 2012-12-13 | Active-type piezoelectric hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201210541583.XA CN102979849B (en) | 2012-12-13 | 2012-12-13 | Active-type piezoelectric hydraulic damper |
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|---|---|
| CN102979849A CN102979849A (en) | 2013-03-20 |
| CN102979849B true CN102979849B (en) | 2015-04-01 |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103603914B (en) * | 2013-11-25 | 2015-07-22 | 吉林大学 | Magnetostriction damper |
| CN108071735B (en) * | 2017-12-21 | 2019-06-28 | 重庆厚全科技发展有限公司 | One kind starting machine testing vibration-free tables |
| CN113915285A (en) * | 2021-09-14 | 2022-01-11 | 奇瑞汽车股份有限公司 | Hydraulic vibration isolation device |
| CN114427554B (en) * | 2021-12-28 | 2023-06-20 | 南京航空航天大学 | Slide valve type high-speed switching valve driven by piezoelectric stack and control method |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US5740782A (en) * | 1996-05-20 | 1998-04-21 | Lowi, Jr.; Alvin | Positive-displacement-metering, electro-hydraulic fuel injection system |
| JP3832401B2 (en) * | 2002-08-07 | 2006-10-11 | トヨタ自動車株式会社 | Fuel injection device |
| SG109502A1 (en) * | 2002-09-04 | 2005-03-30 | Panasonic Refrigeration Device | Piezo-electric compressor with displacement amplifier |
| CN102359533B (en) * | 2011-09-18 | 2013-01-02 | 浙江师范大学 | Piezoelectric stack type self-energized adjustable hydraulic damper |
| CN102345702B (en) * | 2011-09-18 | 2012-11-21 | 浙江师范大学 | Piezoelectric stacking type self-energy supply hydraulic buffer |
| CN202992002U (en) * | 2012-12-13 | 2013-06-12 | 浙江师范大学 | Active type piezoelectric hydraulic damper |
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| C06 | Publication | ||
| PB01 | Publication | ||
| C10 | Entry into substantive examination | ||
| SE01 | Entry into force of request for substantive examination | ||
| ASS | Succession or assignment of patent right |
Owner name: ELECTRIC POWER RESEARCH INSTITUTE, STATE GRID JILI Effective date: 20141210 |
|
| C41 | Transfer of patent application or patent right or utility model | ||
| C53 | Correction of patent for invention or patent application | ||
| CB03 | Change of inventor or designer information |
Inventor after: Han Junwu Inventor after: Liu Dianlong Inventor after: Wang Shuyun Inventor after: Zeng Ping Inventor after: Ren Ping Inventor after: Yang Daiyong Inventor before: Han Junwu Inventor before: Yu Li Inventor before: Wang Shuyun Inventor before: Li Yang Inventor before: Liu Dianlong Inventor before: Zeng Ping |
|
| COR | Change of bibliographic data |
Free format text: CORRECT: INVENTOR; FROM: KAN JUNWU YU LI WANG SHUYUN LI YANG LIU DIANLONG CENG PING TO: KAN JUNWU LIU DIANLONG WANG SHUYUN CENG PING REN PING YANG DAIYONG |
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| TA01 | Transfer of patent application right |
Effective date of registration: 20141210 Address after: 321001 Zhejiang province Jinhua City Yingbin Road No. 688 Applicant after: Zhejiang Normal University Applicant after: Electric Power Research Institute, State Grid Jilin Power Co., Ltd. Applicant after: State Grid Corporation of China Address before: 321001 Zhejiang province Jinhua City Yingbin Road No. 688 Applicant before: Zhejiang Normal University |
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| C14 | Grant of patent or utility model | ||
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