CN103423364A - Hydraulic damper with adjustable damping - Google Patents
Hydraulic damper with adjustable damping Download PDFInfo
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- CN103423364A CN103423364A CN201310346937XA CN201310346937A CN103423364A CN 103423364 A CN103423364 A CN 103423364A CN 201310346937X A CN201310346937X A CN 201310346937XA CN 201310346937 A CN201310346937 A CN 201310346937A CN 103423364 A CN103423364 A CN 103423364A
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Abstract
The invention discloses a hydraulic damper with adjustable damping. The hydraulic damper is arranged on an automobile. A hydraulic loop d is connected between an upper oil cavity b and a lower oil cavity c. An oil pressure cavity is arranged on the hydraulic loop d and comprises an oil pressure chamber, a piston valve core and two springs. The piston valve core and the two springs are arranged in the oil pressure chamber. The piston valve core divides the oil pressure cavity into a chamber e and a chamber f. Two through holes are formed in the piston valve core. The front end of a pipeline d1 is connected with the upper oil cavity b, and the tail end of the pipeline d1 is connected with the oil pressure cavity and is connected with a pipeline d3 in a bypass mode. The pipeline d3 is connected with the chamber f. A pipeline d6 is connected with the chamber f and the lower oil cavity c. The front end of a pipeline d5 is connected with the lower oil cavity c, and the tail end of the pipeline d5 is connected with the oil pressure cavity and is connected with a pipeline d4 in a bypass mode. The pipeline d4 is connected with the chamber e. A pipeline d2 is connected with the chamber e and the upper oil cavity b. Pressure difference between the two ends of the oil pressure chamber is used for pushing the piston valve core to move, so that the communication area of an oil pipe and the piston valve core is changed, the speed of oil liquid is changed when the oil liquid passes through the piston valve core, so that damping is changed, and accordingly a damping value is automatically adjusted according to road conditions in real time.
Description
Technical field
The present invention relates to a kind of vibration damper be arranged on automobile, refer in particular to the adjustable dydraulic shock absorber of a kind of damping.
Background technique
For accelerating the decay of vehicle frame and body vibrations, to improve the smoothness of automobile running, in the suspension system inside of most of automobiles, vibration damper all is housed.The basic principle of vibration damper is to utilize damping to consume the energy produced in vibration to realize vibration damping.Hydraulic shock absorber is to utilize the fluid damping technology of orifice restriction to realize the damping behavior of suspension system, its action principle is when vehicle frame and vehicle bridge are done reciprocal relative movement, piston in hydraulic shock absorber is also reciprocating in cylinder barrel, make the fluid in housing flow into another inner chamber from an inner chamber hole narrow by some repeatedly, now, in friction between hole wall and fluid and fluid molecule, friction just forms the damping force to vibration, make the vibrational energy of vehicle body and vehicle frame be converted into heat energy and be absorbed by fluid and housing, then fall apart in atmosphere.At present, the existing adjustable dydraulic shock absorber of multiple damping, a kind of adaptive transmission control that for example application number is 91201256.0 announcements, its characteristics are to comprise the piston rod, rotary valve core bar of hollow type etc., and stepper motor is placed in dust-proof cover, and the stepper motor live axle connects rotary valve, its shortcoming is that stepper motor is for a long time in vibrational state, life-span is not high, and device volume is excessive, and the hollow piston rod mechanical strength is low.The minicar magnetic current intelligent vibration damper that is also 200510060298.6 announcements just like application number, thereby the viscosity of magnetic liquid is controlled in the magnetic field that it produces by the size of current change hot-wire coil that changes hot-wire coil, finally reach the variable purpose of damping, but magnetic rheological liquid easily precipitates, after outage or change electric current, original magnetic fields can not eliminated immediately, and damping property is unstable.
Summary of the invention
For addressing the above problem, the invention provides the adjustable dydraulic shock absorber of a kind of damping, be intended to solve the problem such as traditional vibration damper unstable properties, complex structure, life-span be low.
The technical solution used in the present invention: comprise cylinder body, floating piston and piston, floating piston and piston are divided into the compressed air cell a on top, the upper oil cavitie b of centre and the lower oil cavitie c of bottom by cylinder body, in the cylinder body outside, connecting fluid hydraulic circuit d between upper oil cavitie b and lower oil cavitie c, oil hydraulic circuit d is provided with the oil pressure chamber; The oil pressure chamber comprises the oil pressure chamber and is positioned at piston valve core and two springs of oil pressure chamber, and piston valve core is divided into chamber e and chamber f by the oil pressure chamber, respectively is supported with a spring in chamber e and chamber f; Have two through holes on piston valve core; Oil hydraulic circuit d consists of 6 fluid pipeline d1, d2, d3, d4, d5, d6, pipeline d1 head end is connected with the b of upper chamber, centre is provided with the second one-way valve, end is connected with the oil pressure chamber and the other road d3 that takes over, pipeline d3 is connected with chamber f, and pipeline d6 directly connects chamber f and lower chambers c; Pipeline d5 head end is connected with lower chambers c, centre is provided with the first one-way valve, end is connected with the oil pressure chamber and the other road d4 that takes over, and pipeline d4 connects chamber e, and pipeline d2 directly connects chamber e and the b of upper chamber; When piston moves upward, the second one-way valve opens, the first one-way valve closure, fluid promotes piston valve core to chamber e motion, and the first through hole on piston valve core is gradually over against pipeline d1 and pipeline d6; When piston moves downward, the first one-way valve opens, the second one-way valve closure, fluid promotes piston valve core to chamber f motion, and the second through hole on piston valve core is gradually over against pipeline d2 and pipeline d3.
The invention has the beneficial effects as follows:
1, it is poor that the present invention utilizes the interior pressure at two ends of oil pressure chamber, promote the piston valve core side-to-side movement, make oil guide pipe change with the area that is communicated with of piston valve core, thereby change the speed of fluid through piston valve core, change damping, make the damping value of vibration damper change with road conditions.The present invention is lower to the requirement of executive component, reliable performance, and because the oil pressure that directly relies on the cylinder body upper and lower cavity is poor, restriction is controlled, make it not only can adapt to various road conditions, can also be according to the real-time automatic damping adjusting of road conditions, needs and the various roads situation of various vehicles in various operating modes be can meet, the travelling comfort taken and the Security of driving improved.
2, the present invention does not apply the devices such as extra sensor, stepper motor, and cost reduces greatly, energy-conservation reliable; Simple in structure, cheap for manufacturing cost, for ease of maintenaince promote.
The accompanying drawing explanation
In order more fully to explain structure of the present invention and working principle, with embodiment, the present invention is described further in conjunction with the following drawings.
Fig. 1 is that the master of damper structure of the present invention looks sectional view;
Fig. 2 is the internal structure enlarged view in oil pressure chamber 5 in Fig. 1;
Fig. 3 is the axonometric drawing of piston valve core 9 in Fig. 2;
Fig. 4 is composition and the connection diagram thereof of oil hydraulic circuit d in Fig. 1;
Fig. 5 is the fluid flow schematic diagram of vibration damper of the present invention when compression stroke;
Fig. 6 is vibration damper of the present invention fluid flow schematic diagram when extension stroke;
In figure: 1. cylinder body; 2. floating piston; 3. piston; 4,6. one-way valve; 5. oil pressure chamber; 7. oil pressure chamber; 8,10. spring; 9. piston valve core; 10. through hole; 11. guide rail.
Embodiment
As shown in Figure 1, the adjustable vibration damper of damping of the present invention comprises cylinder body 1, floating piston 2, piston 3.Wherein floating piston 2, in cylinder body 1, is positioned at the top of piston 3, with cylinder body 1 inner wall sealing, contacts.The piston rod of piston 3 bottoms reaches outside cylinder body 1 from the bottom in cylinder body 1, and the normal open hole of 1mm is arranged on piston 3, and the top of piston 3 contacts with cylinder body 1 inner wall sealing.Floating piston 2 and piston 3 are divided into three chambers by cylinder body 1, are respectively the compressed air cell a on top, the upper oil cavitie b of centre and the lower oil cavitie c of bottom.Compressed air cell a be used for compensating piston 3 move upward (compression stroke) enter in cylinder body 1, the reduction of cylinder body 1 oil storage volume.In cylinder body 1 outside, between upper oil cavitie b and lower oil cavitie c, with oil hydraulic circuit d, be connected, oil pressure chamber 5 is installed on oil hydraulic circuit d, the upper one-way valve 6 of installing of the oil hydraulic circuit d between oil pressure chamber 5 and upper oil cavitie b, the upper one-way valve 4 of installing of the oil hydraulic circuit d between oil pressure chamber 5 and lower oil cavitie c.
As shown in Figure 2, oil pressure chamber 5 comprises oil pressure chamber 7, piston valve core 9 and two springs 8,10, and piston valve core 9 and two springs 8,10 are installed in oil pressure chamber 7, and piston valve core 9 outer side walls contact with oil pressure chamber 7 inner wall sealings.Piston valve core 9 is divided into two chambers by oil pressure chamber 5, is respectively chamber e and chamber f.A spring is installed in a chamber, a spring supporting between an end and oil pressure chamber 7 of piston valve core 9, i.e. mounting spring 8 in chamber e, in chamber f, mounting spring 10.Spring 8 and spring 10 are pressed against on an end and oil pressure chamber 7 of piston valve core 9.
As shown in Figure 3, a guide rail 11 respectively is set on the outer wall of the both sides of piston valve core 9, respectively has a groove on the inwall of the both sides of oil pressure chamber 7, guide rail 11 and groove match, and guide rail 11 can be free to slide in groove, piston valve core 9 can be free to slide in oil pressure chamber 7.Have two through holes 10 on piston valve core 9, two through holes 10 are aimed on oil pressure chamber 7 hole for connecting fluid hydraulic circuit d in upholding and compressing two working procedure, the degrees of freedom of guide rail 11 on can also limited piston spool 9 sense of rotation, guarantee that two holes offering on piston valve core 9 can aim at the hole on oil pressure chamber 7 all the time.
As shown in Figure 4, oil hydraulic circuit d consists of 6 fluid pipeline d1, d2, d3, d4, d5, d6, on this oil hydraulic circuit d, is provided with oil pressure chamber 5.Pipeline d1 head end is connected with cylinder body 1, is connected in the b of upper chamber of cylinder body 1, in the middle of pipeline d1, one-way valve 6 is housed, and pipeline d1 end is connected with oil pressure chamber 5, and at the other road d3 that takes over of its end.Pipeline d3 connects the chamber f in oil pressure chamber 5, so just pipeline d1 is connected with the inner chamber in oil pressure chamber 5, and chamber f is communicated with by pipeline d1 and pipeline d3 with the b of upper chamber of cylinder body 1.Chamber f directly is connected by pipeline d6 with the lower chambers c of cylinder body 1.The pipeline diameter of pipeline d1, d3, d6 is identical.Pipeline d5 head end is connected with cylinder body 1, and the lower chambers c of cylinder body 1 is equipped with one-way valve 4 in the middle of pipeline d5, and pipeline d5 end is connected with oil pressure chamber 5, and at the other road d4 that takes over of pipeline d5 end.Pipeline d4 connects the chamber e in oil pressure chamber 5, so just pipeline d5 is connected with another chamber of 5 inside, oil pressure chamber, and chamber e is communicated with by pipeline d4 and pipeline d5 with the lower chambers c of cylinder body 1.Chamber e directly is connected by pipeline d2 with the b of upper chamber of cylinder body 1.The pipeline diameter of pipeline d2, d4, d5 is identical.Pipeline d1, d3 and d6 are compression stroke fluid circulation pipeline, and pipeline d2, d4 and d5 are extension stroke fluid circulation pipeline.In the double barreled dydraulic shock absorber, the damping in the damping ratio extension stroke in compression stroke is little, therefore the pipeline diameter of pipeline d1, d3, d6 is larger than the pipeline diameter of pipeline d2, d4, d5.
As shown in Figure 5, the piston 3 in cylinder body 1 moves upward, and vibration damper is done compression movement, and one-way valve 6 is opened, and one-way valve 4 closures, fluid, by pipeline d1 circulation, flows to chamber f through pipeline d3.The oil liquid pressure of chamber f is greater than the oil liquid pressure of chamber e, fluid promotes piston valve core 9 and moves to chamber e, the first through hole 10 on piston valve core 9 is gradually over against the position of pipeline d1 and pipeline d6, make the first through hole 10 and pipeline d1 circulation area on piston valve core 9 become large, liquid flows through the speed quickening from the first through hole 10 of pipeline d1 and piston valve core 9, through pipeline d6, is passed to lower chambers c.When automobile is subject to larger excitation, piston 3 compression strokes are apart from increase, make in the b of upper chamber pressure larger, make pressure in chamber f become large simultaneously, promote piston valve core 9 to chamber e motion, make piston valve core 9 and pipeline d1 circulation area become large, damping diminishes; Otherwise, while being subject to less excitation, it is large that damping becomes.
As shown in Figure 6, when the piston 3 in cylinder body 1 moves downward, vibration damper is done stretching exercise, and one-way valve 4 is opened, one-way valve 6 closures, and fluid, by pipeline d5 circulation, flows to chamber e through pipeline d4.Oil liquid pressure in chamber e is greater than the oil liquid pressure in chamber f, fluid promotes piston valve core 9 and moves to chamber f, the second through hole 10 on piston valve core 9 is gradually over against the position of pipeline d2 and pipeline d3, make the second through hole 10 and pipeline d5 circulation area on piston valve core 9 become large, liquid flows through the speed quickening from the second through hole 10 of pipeline d5 and piston valve core 9, through pipeline d2, is passed to the b of upper chamber.When automobile is subject to larger excitation, piston 3 extension stroke are apart from increase, make in lower chambers c pressure larger, make pressure in chamber e become large simultaneously, promote piston valve core 9 to chamber f motion, make piston valve core 9 and branch road d5 circulation area become large, damping diminishes; Otherwise, while being subject to less excitation, it is large that damping becomes.
Claims (3)
1. the dydraulic shock absorber that damping is adjustable, comprise cylinder body (1), floating piston (2) and piston (3), floating piston (2) and piston (3) are divided into the compressed air cell a on top, the upper oil cavitie b of centre and the lower oil cavitie c of bottom by cylinder body (1), it is characterized in that: in cylinder body (1) outside, connecting fluid hydraulic circuit d between upper oil cavitie b and lower oil cavitie c, oil hydraulic circuit d is provided with oil pressure chamber (5); Oil pressure chamber (5) comprises oil pressure chamber (7) and is positioned at piston valve core (9) and two springs of oil pressure chamber (7), and piston valve core (9) is divided into chamber e and chamber f by oil pressure chamber (5), respectively is supported with a spring in chamber e and chamber f; Have two through holes (10) on piston valve core (9); Oil hydraulic circuit d consists of 6 fluid pipeline d1, d2, d3, d4, d5, d6, pipeline d1 head end is connected with the b of upper chamber, centre is provided with the second one-way valve (6), end is connected with oil pressure chamber (5) and the other road d3 that takes over, pipeline d3 is connected with chamber f, and pipeline d6 directly connects chamber f and lower chambers c; Pipeline d5 head end is connected with lower chambers c, centre is provided with the first one-way valve (4), end is connected with oil pressure chamber (5) and the other road d4 that takes over, and pipeline d4 connects chamber e, and pipeline d2 directly connects chamber e and the b of upper chamber; When piston (3) moves upward, the second one-way valve (6) is opened, the first one-way valve (4) closure, and fluid promotes piston valve core (9) to chamber e motion, and the first through hole (10) on piston valve core (9) is gradually over against pipeline d1 and pipeline d6; When piston (3) moves downward, the first one-way valve (4) is opened, the second one-way valve (6) closure, and fluid promotes piston valve core (9) to chamber f motion, and the second through hole (10) on piston valve core (9) is gradually over against pipeline d2 and pipeline d3.
2. the adjustable dydraulic shock absorber of a kind of damping according to claim 1, it is characterized in that: the pipeline diameter of pipeline d2, d4, d5 is identical, the pipeline diameter of pipeline d1, d3, d6 is identical, and the pipeline diameter of pipeline d1, d3, d6 is greater than the pipeline diameter of pipeline d2, d4, d5.
3. the adjustable dydraulic shock absorber of a kind of damping according to claim 1, it is characterized in that: a guide rail respectively is set on the both sides outer wall of piston valve core (9), respectively has a groove on the both sides inwall of oil pressure chamber (7), guide rail and groove match.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310346937.XA CN103423364B (en) | 2013-08-12 | 2013-08-12 | The dydraulic shock absorber that a kind of damping is adjustable |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN201310346937.XA CN103423364B (en) | 2013-08-12 | 2013-08-12 | The dydraulic shock absorber that a kind of damping is adjustable |
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| Publication Number | Publication Date |
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| CN103423364A true CN103423364A (en) | 2013-12-04 |
| CN103423364B CN103423364B (en) | 2015-08-05 |
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| CN201310346937.XA Expired - Fee Related CN103423364B (en) | 2013-08-12 | 2013-08-12 | The dydraulic shock absorber that a kind of damping is adjustable |
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Cited By (15)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105546016A (en) * | 2016-03-07 | 2016-05-04 | 吉林大学 | Passive damper in similar semi-active control |
| CN106195099A (en) * | 2016-07-12 | 2016-12-07 | 嘉兴学院 | A kind of vapour vehicle shock-absorbing device |
| CN106481728A (en) * | 2015-08-31 | 2017-03-08 | 南京英剑机电科技有限公司 | A kind of passive hydraulic type inertia force generating meanss |
| CN106678484A (en) * | 2016-11-17 | 2017-05-17 | 国家电网公司 | High-energy pipeline impact power absorber in power planning |
| TWI588378B (en) * | 2015-04-30 | 2017-06-21 | Liu li-qun | Buffer storage device |
| CN106934089A (en) * | 2015-12-31 | 2017-07-07 | 沪东重机有限公司 | A kind of damped coefficient check method of fluid pressure type longitudinal vibration damper |
| CN106958619A (en) * | 2017-04-28 | 2017-07-18 | 台州职业技术学院 | A kind of adjustomatic shock absorber |
| CN108167375A (en) * | 2018-02-23 | 2018-06-15 | 四川大学 | Variable damping vibration isolator and railway roadbed vibrating isolation system |
| CN108397504A (en) * | 2018-03-29 | 2018-08-14 | 青岛理工大学 | External adjustable variable damping viscous damping devices |
| CN108533659A (en) * | 2018-05-11 | 2018-09-14 | 南京林业大学 | A kind of mechanical automatic adjustment pressure fluid linking damper |
| CN109296694A (en) * | 2018-11-27 | 2019-02-01 | 严胜平 | A kind of magnetic resistance piston |
| CN109972696A (en) * | 2019-04-18 | 2019-07-05 | 上海人民企业集团水泵有限公司 | Installation is stablized and the non-negative pressure method of water supply remote supervisory and control(ling) equipment case with safeguard function |
| WO2020024654A1 (en) * | 2018-08-01 | 2020-02-06 | 陈刚 | Liquid gas supporting shock absorber and vehicle using same |
| CN112460181A (en) * | 2020-11-30 | 2021-03-09 | 重庆理工大学 | Impact-resistant buffer based on permanent magnet excitation |
| CN112576672A (en) * | 2020-12-30 | 2021-03-30 | 邵阳兴达精密机械制造有限公司 | Low-resilience return stroke controllable nitrogen spring and operation method |
Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1362588A (en) * | 2000-12-29 | 2002-08-07 | 梅特罗株式会社 | Shock-absorbing buffer |
| CN1628223A (en) * | 2001-11-06 | 2005-06-15 | 科尼公司 | Shock absorber with frequency-dependent damping |
| CN201021704Y (en) * | 2004-09-17 | 2008-02-13 | 尤利乌斯·布卢姆有限公司 | Flow damper |
| JP2009287653A (en) * | 2008-05-28 | 2009-12-10 | Showa Corp | Damping-force adjusting structure of hydraulic damper |
-
2013
- 2013-08-12 CN CN201310346937.XA patent/CN103423364B/en not_active Expired - Fee Related
Patent Citations (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1362588A (en) * | 2000-12-29 | 2002-08-07 | 梅特罗株式会社 | Shock-absorbing buffer |
| CN1628223A (en) * | 2001-11-06 | 2005-06-15 | 科尼公司 | Shock absorber with frequency-dependent damping |
| CN201021704Y (en) * | 2004-09-17 | 2008-02-13 | 尤利乌斯·布卢姆有限公司 | Flow damper |
| JP2009287653A (en) * | 2008-05-28 | 2009-12-10 | Showa Corp | Damping-force adjusting structure of hydraulic damper |
Cited By (18)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| TWI588378B (en) * | 2015-04-30 | 2017-06-21 | Liu li-qun | Buffer storage device |
| CN106481728A (en) * | 2015-08-31 | 2017-03-08 | 南京英剑机电科技有限公司 | A kind of passive hydraulic type inertia force generating meanss |
| CN106934089A (en) * | 2015-12-31 | 2017-07-07 | 沪东重机有限公司 | A kind of damped coefficient check method of fluid pressure type longitudinal vibration damper |
| CN105546016A (en) * | 2016-03-07 | 2016-05-04 | 吉林大学 | Passive damper in similar semi-active control |
| CN106195099B (en) * | 2016-07-12 | 2019-01-11 | 嘉兴学院 | A kind of automobile damping device |
| CN106195099A (en) * | 2016-07-12 | 2016-12-07 | 嘉兴学院 | A kind of vapour vehicle shock-absorbing device |
| CN106678484A (en) * | 2016-11-17 | 2017-05-17 | 国家电网公司 | High-energy pipeline impact power absorber in power planning |
| CN106958619A (en) * | 2017-04-28 | 2017-07-18 | 台州职业技术学院 | A kind of adjustomatic shock absorber |
| CN108167375A (en) * | 2018-02-23 | 2018-06-15 | 四川大学 | Variable damping vibration isolator and railway roadbed vibrating isolation system |
| CN108397504A (en) * | 2018-03-29 | 2018-08-14 | 青岛理工大学 | External adjustable variable damping viscous damping devices |
| CN108533659A (en) * | 2018-05-11 | 2018-09-14 | 南京林业大学 | A kind of mechanical automatic adjustment pressure fluid linking damper |
| WO2020024654A1 (en) * | 2018-08-01 | 2020-02-06 | 陈刚 | Liquid gas supporting shock absorber and vehicle using same |
| CN109296694A (en) * | 2018-11-27 | 2019-02-01 | 严胜平 | A kind of magnetic resistance piston |
| CN109296694B (en) * | 2018-11-27 | 2024-03-29 | 严胜平 | Reluctance piston |
| CN109972696A (en) * | 2019-04-18 | 2019-07-05 | 上海人民企业集团水泵有限公司 | Installation is stablized and the non-negative pressure method of water supply remote supervisory and control(ling) equipment case with safeguard function |
| CN112460181A (en) * | 2020-11-30 | 2021-03-09 | 重庆理工大学 | Impact-resistant buffer based on permanent magnet excitation |
| CN112576672A (en) * | 2020-12-30 | 2021-03-30 | 邵阳兴达精密机械制造有限公司 | Low-resilience return stroke controllable nitrogen spring and operation method |
| CN112576672B (en) * | 2020-12-30 | 2024-04-30 | 邵阳兴达精密机械制造有限公司 | Low-resilience-quantity return-stroke controllable nitrogen spring and operation method |
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| CN103423364B (en) | 2015-08-05 |
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