CN202992002U - Active type piezoelectric hydraulic damper - Google Patents
Active type piezoelectric hydraulic damper Download PDFInfo
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- CN202992002U CN202992002U CN 201220691049 CN201220691049U CN202992002U CN 202992002 U CN202992002 U CN 202992002U CN 201220691049 CN201220691049 CN 201220691049 CN 201220691049 U CN201220691049 U CN 201220691049U CN 202992002 U CN202992002 U CN 202992002U
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- valve
- spool
- chamber
- spring
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- 238000013016 damping Methods 0.000 claims abstract description 25
- 230000001105 regulatory effect Effects 0.000 claims description 8
- 230000015572 biosynthetic process Effects 0.000 claims description 4
- 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
- 230000033228 biological regulation Effects 0.000 description 4
- 238000010586 diagram Methods 0.000 description 4
- 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
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Abstract
本实用新型涉及一种主动式压电液压阻尼器，属于减振器。端盖固定在缸体上，大活塞将缸体内腔分隔成上下缸腔；平衡弹簧通过大活塞压在下缸腔内，活塞杆法兰固定在大活塞上；压电叠堆置于活塞杆内并将小活塞、阀芯及复位弹簧压在大活塞内腔中；小活塞与活塞杆法兰间压有碟形弹簧；小活塞依次将阀簧和阀球压接在阀芯内腔中并构成单向阀；阀芯内腔与上下阀腔及阀芯上的环槽连通；环槽与大活塞上的左右流道连通并构成阻尼阀，左右流道还分别与上下缸腔连通。优点在于利用活塞杆内的压电叠堆驱动附加流体腔活塞调节活塞内的阻尼阀，故结构简单、体积小、无泄漏和电磁干扰、阻尼调节范围大。
The utility model relates to an active piezoelectric hydraulic damper, which belongs to shock absorbers. The end cover is fixed on the cylinder body, and the large piston separates the cylinder cavity into upper and lower cylinder chambers; the balance spring is pressed into the lower cylinder chamber through the large piston, and the piston rod flange is fixed on the large piston; the piezoelectric stack is placed on the piston rod and press the small piston, valve core and return spring in the inner cavity of the large piston; a disc spring is pressed between the small piston and the piston rod flange; the small piston crimps the valve spring and the valve ball in the inner cavity of the valve core in turn And constitute a one-way valve; the inner chamber of the spool communicates with the upper and lower valve chambers and the annular groove on the spool; the annular groove communicates with the left and right passages on the large piston to form a damping valve, and the left and right passages are also communicated with the upper and lower cylinder chambers respectively. The advantage is that the piezoelectric stack in the piston rod is used to drive the additional fluid chamber piston to adjust the damping valve in the piston, so the structure is simple, the volume is small, there is no leakage and electromagnetic interference, and the damping adjustment range is large.
Description
Technical field
The utility model belongs to antivibration area, is specifically related to a kind of active piezoelectric hydraulic damper, is 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 is simple in structure, cost is low, technology is more ripe, but because of damping non-adjustable, the adaptability of its effectiveness in vibration suppression and environment is relatively poor, be unsuitable for some and require vibration control effect occasion preferably, as motor car engine and vehicle frame suspend, Large-Scale Precision Instrument and Equipment vibration damping etc.Therefore, people have proposed active, semi-active type hydraulic damper with adjustable, the active adjustable damper that namely utilizes motor-driven hydraulic pumps power to be provided and to be controlled by electromagnetic switch/overflow/reduction valve is as Chinese utility model patent CN1367328A, CN101392809A etc.Compare in the non-adjustable hydraulic damper of passive type, the control of active hydraulic damper with adjustable is effective, vibration environment adaptable, application has succeeded at aspects such as automobile active engine mounts; But existing active hydraulic damper mostly needs larger pumping plant to drive and jointly controls in conjunction with a plurality of solenoid valves, therefore systems bulky, connection and control more complicated, energy consumption is high, reliability is lower etc., has certain narrow limitation on using.In view of problems such as existing active hydraulic damper self structure, control ability and the supplies of dependence outside energy, the claimant once proposed a kind of based on piezoelectric stack transducer and fluid coupling recovered energy and carry out the semi-active type self energizing adjustable damper that damping is regulated, be Chinese patent 201110275849.6, can solve to a certain extent some drawback of conventional active hydraulic damper; But realize that because this damper utilizes piezoelectric stack directly to drive spool damping regulates, and the flexible ability of piezoelectric stack under the voltage effect is extremely limited, micron order only, therefore the damping regulating power is low, is unsuitable for the larger occasion of regulation range.
Summary of the invention
The utility model proposes a kind of active piezoelectric hydraulic damper, with solve existing active hydraulic damper and the existing damping regulating power of piezo-stack type self-energized adjustable hydraulic damper low, be unsuitable for the larger occasion problem of regulation range.
The technological scheme that the utility model is taked is: end cap is fixed by screws on cylinder body, and large piston sleeve is connected in inner chamber of cylinder block and inner chamber of cylinder block 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 successively small piston, spool and Returnning spring is crimped in the ladder-type inner chamber of large piston; Being crimped with belleville spring and small piston upper shoulder between the flange of small piston and piston rod end leans on the flange of piston rod end; Common formation uuper valve chamber between small piston and large piston and spool consists of lower valve chamber between spool and large piston jointly, and uuper valve chamber is communicated with accumulator by pipeline; Small piston is crimped on valve spring and valve ball in the inner chamber of spool successively, and the inner chamber of spool, valve spring and valve ball consist of one-way valve jointly; The inner chamber of spool is communicated with uuper valve chamber, is communicated with lower valve chamber, also is communicated with annular groove on spool by the vertical hole on spool and cross-drilled hole by the vertical hole on spool by the translot of spool upper end; Described annular groove is communicated with left runner and right runner on large piston, and described left runner and right runner also are communicated with described upper cylinder half chamber and lower cylinder chamber respectively; Described annular groove and described left runner and right runner are configured for the orifice valve that damping is regulated jointly.
Be full of fluid in work front damper system, cylinder chamber, up and down and upper lower valve chamber fluid pressure equate, are accumulator set pressure P
0During the damper inoperative, piezoelectric stack no electric circuit and be not subjected to the pretightening force effect; Large piston and small piston are in state of equilibrium under the effect of hydrodynamic pressure and each spring, orifice valve is in normally open, system damping is little.
When needing damping adjusting, piezoelectric stack is switched on and is extended, and promotes small piston and moves downward, thereby make the uuper valve chamber fluid pressure increase to P and make non-return valve holds in off position; As the spool 7 suffered external force F in upper end
s=F
t8+ π r
2P is greater than the suffered external force F in lower end
x=F
t10+ π r
2P
0The time, namely the uuper valve chamber fluid pressure increases to P＞[F
t10-F
t8+ π r
2P
0]/(π r
2) time, spool begins to move downward, and the flow area of orifice valve is reduced, damping increases, in formula: F
t8And F
t10Be respectively valve spring and Returnning spring to the active force of spool, r is the spool radius; When the elongation of piezoelectric stack under the voltage effect is L=V η, the amount of movement of spool, be that the regulation amount of orifice valve 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, during much larger than the small piston diameter, the elongation of piezoelectric stack will be exaggerated n=l/L=(R/r) when large piston diameter
2Doubly, namely the regulating power of the damping of orifice valve is exaggerated n=(R/r)
2Doubly.
When piezoelectric stack outage or driving voltage reduce, piezoelectric stack begins to shrink under himself resilient force, small piston and spool also all move upward under the comprehensive function of fluid and each related springs, thereby the aperture of orifice valve are increased gradually, damping reduces gradually; When the shoulder of small piston leans on flange at piston rod and spool upper-end surface when leaning on the small piston lower surface, damper returns to original state, this moment the aperture of orifice valve maximum, damping is minimum.
Features and advantages of the present utility model is: 1. increase an additional streams body cavity of fill fluid voluntarily between piezoelectric stack and spool, the increase spool travel amount that combines with less spool by larger piston is therefore damping adjusting and control range are large; 2. orifice valve and piezoelectric stack are placed in piston and piston rod, need not the peripheral unit such as motor, pump, solenoid valve, therefore volume is little, simple in structure, level of integration is high, good airproof performance, and easily adopt longer piezoelectric stack to realize large-scale damping adjusting; 3. be not subjected to the fluid force effect during piezoelectric stack inoperative, therefore after energising, amount of deformation is large, energy converting between mechanical efficient is high; 4. adopt non magnetic piezoelectric stack to drive and control valve core movement, not producing/be not subjected to electromagnetic interference, more being applicable to high magnetic fields, intense radiation environment.Therefore, active piezoelectric hydraulic damper of the present utility model also is suitable for microsystem and the tele-control systems such as Aero-Space, intelligence structure except being applicable to the large-scale traffic tool and machine tool.
Description of drawings
Structural profile schematic diagram when Fig. 1 is a preferred embodiment damper inoperative of the utility model;
Structural profile schematic diagram when Fig. 2 is a preferred embodiment damper job of preferred embodiment the utility model of the utility model;
Fig. 3 is the I section enlarged view of Fig. 1;
Fig. 4 is the structural profile schematic diagram of a large piston of preferred embodiment of the utility model;
Fig. 5 is the structural profile schematic diagram of a preferred embodiment spool of the utility model;
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 chambers and with cylinder body 4 inner chambers 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 successively small piston 6, spool 7 and Returnning spring 11 is crimped in the ladder-type inner chamber C2 of large piston 5; The shoulder 601 that is crimped with belleville spring 12 and small piston 6 between the flange 102 of small piston 6 and piston rod 1 leans on the flange 102 of piston rod 1; Between small piston 6 and large piston 5 and spool 7, common formation uuper valve chamber C21, consist of lower valve chamber C22 between spool 7 and large piston 5 jointly, and uuper valve chamber C21 is communicated with accumulator 13 by pipeline; Small piston 6 is crimped on valve spring 8 and valve ball 9 in the inner chamber 705 of spool 7 successively, the inner chamber 705 of spool 7, valve spring 8 and the common formation one-way valve of valve ball 9 F1; The inner chamber 705 of spool 7 is communicated with, passes through vertical hole 701 on spool 7 by the translot 704 of spool 7 upper ends and is communicated with, also passes through vertical hole 701 on spool 7 and cross-drilled hole 702 with lower valve chamber C22 and be communicated with annular groove 703 on spool with uuper valve chamber C21; Annular groove 703 on spool 7 is communicated with left runner 502 and right runner 501 on large piston 5, and described left runner 502 and 501 connections of right runner also are communicated with upper cylinder half chamber C11 and lower cylinder chamber C12 respectively; Left runner 502 and right runner 501 on annular groove 703 on spool 7 and large piston 5 are configured for the orifice valve F2 that damping is regulated jointly.
To be full of fluid in damper before work, in the fluid filling process, one-way valve F1 opens, and fluid is in one-way valve F2 enters uuper valve chamber C21; After fluid filling was complete, the hydrodynamic pressure in upper cylinder half chamber C11, lower cylinder chamber C12, uuper valve chamber C21 and lower valve chamber C22 equated, is the set pressure P of accumulator 12
0
During the damper inoperative, piezoelectric stack 2 no electric circuits; The fluid force of large piston both sides Shang Xia 5 equates, is in state of equilibrium under the effect of vibration mass M and balance spring 10; Small piston 6 makes piezoelectric stack 2 be subjected to the fluid effect and produces precompression avoiding on the flange 102 that leans under the effect of hydrodynamic pressure, Returnning spring 11 and belleville spring 12 at piston rod 1; Spool Shang Xia 7 the suffered fluid force in two ends equate, lean the lower surface at small piston 6 under the effect of Returnning spring 11 and valve spring 8, to guarantee that orifice valve F2 is in normally open, being left runner 502 on large piston 5 and right runner 501 is communicated with fully with annular groove 703 on spool 7, and this moment, the damping of system was little;
When the vibration mass M up-down vibration and need control the time, piezoelectric stack 2 is switched on and is extended, and promotes small piston 6 and moves downward, thereby uuper valve chamber C21 fluid pressure is increased and make one-way valve F2 maintain closed condition; The increase of uuper valve chamber C21 fluid pressure makes the spool 7 suffered external force F in upper end
s=F
t8+ π r
2P is greater than the suffered external force F in lower end
x=F
t10+ π r
2P
0The time, 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 begins to move downward, and vertical hole 701, cross-drilled hole 702 and the annular groove 703 of fluid on spool 7 in lower valve chamber C22 escapes 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, thereby has played the effect that increases damping, in above-mentioned formula: F
t8And F
t10Be respectively the active force of valve spring 8 and 10 pairs of spools of Returnning spring, r is the spool radius; If the elongation of piezoelectric stack 2 under the voltage effect is L=V η, the amount of movement of spool 7, be that the regulation amount of orifice valve F2 is l=(R/r)
2L=(R/r)
2V η, wherein: V is the driving voltage of piezoelectric stack 2, and 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 much larger than the diameter of small piston 6, namely
The time, the elongation of piezoelectric stack 2 will be exaggerated n=l/L=(R/r)
2Doubly, namely the regulating power of the damping of orifice valve is exaggerated (R/r)
2Doubly;
When piezoelectric stack 2 outages or driving voltage reduction, piezoelectric stack 2 begins 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, thereby the aperture of orifice valve F2 are increased gradually, damping reduces gradually; Simultaneously, lower valve chamber C22 fluid pressure reduces, and fluid reaches vertical hole 701 from annular groove 703, the cross-drilled hole 702 of left runner 502 on spool 7 on large piston 5 and enters lower valve chamber C22; When the shoulder 601 of small piston 6 leans on flange 102 at piston rod 1 and the upper-end surface of spool 7 when leaning on the lower surface of small piston 6, damper returns to original state, this moment the aperture of orifice valve F2 maximum, damping is minimum.
Claims (1)
1. active piezoelectric hydraulic damper, it is characterized in that: end cap is fixed by screws on cylinder body, and large piston sleeve is connected in inner chamber of cylinder block and inner chamber of cylinder block 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 successively small piston, spool and Returnning spring is crimped in the ladder-type inner chamber of large piston; The shoulder that is crimped with belleville spring and small piston between the flange of small piston and piston rod end leans on the flange of piston rod end; Common formation uuper valve chamber between small piston and large piston and spool consists of lower valve chamber between spool and large piston jointly, and uuper valve chamber is communicated with accumulator by pipeline; Small piston is crimped on valve spring and valve ball in the inner chamber of spool successively, and the inner chamber of spool, valve spring and valve ball consist of one-way valve jointly; The inner chamber of spool is communicated with uuper valve chamber, is communicated with lower valve chamber, also is communicated with annular groove on spool by the vertical hole on spool and cross-drilled hole by the vertical hole on spool by the translot of spool upper end; Described annular groove is communicated with left runner and right runner on large piston, and described left runner and right runner also are communicated with upper cylinder half chamber and lower cylinder chamber respectively; Described annular groove and described left runner and right runner are configured for the orifice valve that damping is regulated jointly.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220691049 CN202992002U (en) | 2012-12-13 | 2012-12-13 | Active type piezoelectric hydraulic damper |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN 201220691049 CN202992002U (en) | 2012-12-13 | 2012-12-13 | Active type piezoelectric hydraulic damper |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| CN202992002U true CN202992002U (en) | 2013-06-12 |
Family
ID=48563185
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| CN 201220691049 Expired - Lifetime CN202992002U (en) | 2012-12-13 | 2012-12-13 | Active type piezoelectric hydraulic damper |
Country Status (1)
| Country | Link |
|---|---|
| CN (1) | CN202992002U (en) |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102979849A (en) * | 2012-12-13 | 2013-03-20 | 浙江师范大学 | Active-type piezoelectric hydraulic damper |
| CN108071734A (en) * | 2017-08-24 | 2018-05-25 | 深圳市罗伯医疗科技有限公司 | Damper and assistant robot |
| CN109210126A (en) * | 2018-10-23 | 2019-01-15 | 清科智能悬架系统（苏州）有限公司 | A kind of external piezoelectric ceramics variable-damp vibration damper |
-
2012
- 2012-12-13 CN CN 201220691049 patent/CN202992002U/en not_active Expired - Lifetime
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN102979849A (en) * | 2012-12-13 | 2013-03-20 | 浙江师范大学 | Active-type piezoelectric hydraulic damper |
| CN108071734A (en) * | 2017-08-24 | 2018-05-25 | 深圳市罗伯医疗科技有限公司 | Damper and assistant robot |
| CN109210126A (en) * | 2018-10-23 | 2019-01-15 | 清科智能悬架系统（苏州）有限公司 | A kind of external piezoelectric ceramics variable-damp vibration damper |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| C14 | Grant of patent or utility model | ||
| GR01 | Patent grant | ||
| AV01 | Patent right actively abandoned |
Granted publication date: 20130612 Effective date of abandoning: 20150401 |
|
| RGAV | Abandon patent right to avoid regrant |