CN104565178A - Hydraulic shock absorber with active adjustable damping - Google Patents
Hydraulic shock absorber with active adjustable damping Download PDFInfo
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- CN104565178A CN104565178A CN201310515706.7A CN201310515706A CN104565178A CN 104565178 A CN104565178 A CN 104565178A CN 201310515706 A CN201310515706 A CN 201310515706A CN 104565178 A CN104565178 A CN 104565178A
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- oil
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- hydraulic motor
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
- F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
- F16F9/32—Details
- F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
- F16F9/512—Means responsive to load action, i.e. static load on the damper or dynamic fluid pressure changes in the damper, e.g. due to changes in velocity
- F16F9/5126—Piston, or piston-like valve elements
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- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
- Vibration Prevention Devices (AREA)
Abstract
The invention relates to a hydraulic shock absorber with active adjustable damping. The hydraulic shock absorber comprises an oil cylinder, a piston, a one-way valve, a hydraulic motor, a flywheel, a dual-acting hydraulic cylinder, a dual-acting hydraulic cylinder piston, a push rod, a sliding resistor, an electromagnet A, an electromagnet B and a friction plate, wherein the oil cylinder is divided into an upper oil cavity and a lower oil cylinder by the piston; the upper oil cavity is connected with the lower oil cavity through a pipeline and the hydraulic motor; the hydraulic motor is fixedly connected with the flywheel, and is in contact with the friction plate; the dual-acting hydraulic cylinder piston is tightly connected with the dual-acting hydraulic cylinder; the dual-acting hydraulic cylinder is divided into a left cylinder and a right cylinder by the dual-acting hydraulic cylinder piston; the push rod is connected with the dual-acting hydraulic cylinder piston, and protrudes out from two ends of the left cylinder and the right cylinder; the electromagnet A and the electromagnet B are arranged in a manner of opposite polarity; the electromagnet B is connected with the friction plate; the push rod can change the size of the sliding resistor, and changes the action force between the electromagnet A and the electromagnet B to change the friction force between the friction plate and the flywheel; finally the oil fluid resistance in the pipeline caused by the hydraulic motor is changed. According to the hydraulic shock absorber, real-time active adjustable damping of the shock absorber can be achieved.
Description
Technical field
The present invention relates to a kind of damper means, refer in particular to the dydraulic shock absorber that a kind of damping is initiatively adjustable.
Background technique
Vehicle shock absorber is arranged between vehicle frame and vehicle bridge, can decay to the vibration of vehicle body.The working principle of tradition vibration damper is: when automotive suspension high compression, vibration damper compresses thereupon, and damper piston moves down, and lower oil chamber's oil pressure raises, and flowing valve and compression valve are opened and carried out off-load; When automotive wheel moves downward away from vehicle frame, absorber, damper piston moves, and upper chamber oil pressure raises, and rebound valve and recuperation valve are opened and carried out off-load.
Traditional resistance of shock absorber value is fixed, and does not have damping this function variable.
At present, the dydraulic shock absorber design that existing multiple damping is adjustable is open.The dydraulic shock absorber (declaring the patent No. 02111068.9) that vehicle suspension damping as rich in, Zhejiang University Wang Qing is initiatively adjustable.But still there is following problem in these designs: one is that in vibration damper working procedure, hydraulic fluid temperature raises, and vibration damper performance reduces; Two is complex structures, and manufacture cost is high, is difficult to promote.
Summary of the invention
For solving the problem, the present invention aims to provide a kind of damper means, and for solving, traditional damper means unstable properties, damping are non-adjustable, complex structure, manufacture cost is high wait not enough.
The technical solution used in the present invention:
The present invention includes oil cylinder, floating piston, one-way valve is some, oil hydraulic motor, flywheel, double-acting hydraulic cylinder, swept resistance, electromagnet A, electromagnet B, friction plate.Vibration damper utilizes oil hydraulic motor pressure at two ends poor, promote the side-to-side movement of double-acting hydraulic cylinder piston, push rod drives adaptive damping bar to change the size of adaptive damping put in circuit, circuital current is changed, electromagnet A, the repulsive force between electromagnet B changes thereupon, thus changes the frictional force between friction plate and flywheel, final change oil hydraulic motor, to the resistance of pipeline oil, makes the damping of vibration damper change with road conditions.
The resistance that oil hydraulic motor puts on pipeline oil changes, thus reaches the function becoming resistance of shock absorber.The vibrational energy of vibration damper is converted into mechanical energy, and consumes so that form of thermal energy is loose eventually through friction, reaches reduction oil liquid temperature, makes vibration damper keep the function of premium properties.
Beneficial effect of the present invention
1, vibration damper is by the connection of pipeline and oil hydraulic motor, the vibrational energy of vibration damper is converted into mechanical energy, and by the friction of friction plate and oil hydraulic motor flywheel, is that form of thermal energy dissipates by changes mechanical energy, avoid because hydraulic fluid temperature raises, and affect the situation of vibration damper performance;
2, the present invention requires low, reliable performance to performer, due to the pressure difference feedback characteristics at oil hydraulic motor two ends, makes it can adapt to various road conditions on a large scale, can realize damping initiatively adjustable, have most of function of automatically controlled semi-active suspension;
3, the non-application sensors of the present invention and high-performance microprocessor, make cost greatly reduce, and can be used as vibration damping and the insulator of various vehicle and mechanical device.
Accompanying drawing explanation
Structure for a more complete understanding of the present invention and working principle, be described in further detail the present invention with embodiment in conjunction with the following drawings.
Fig. 1 is the plan view of the initiatively adjustable vibration damper of damping;
Fig. 2 is the partial front elevation view of the initiatively adjustable vibration damper of damping;
Fig. 3 is the partial right side view of the initiatively adjustable vibration damper of damping;
Fig. 4 is pipeline d tetra-branch roads d1, d2, d3, the schematic diagram of d4;
Pipeline d inner fluid glide path when Fig. 5 is compression stroke;
Pipeline d inner fluid glide path when Fig. 6 is extension stroke.
In figure: 1, oil cylinder, 2, floating piston, 3, piston; 4, piston rod, 5,13,14,15, one-way valve, 6, oil hydraulic motor; 7, flywheel, 8, double-acting hydraulic cylinder, 9, double-acting hydraulic cylinder piston; 10, push rod, 11, variable resistance arm, 12, spring; 16, variable resistor, 17, power supply, 18, protective resistance; 19, electromagnet A, 20, electromagnet B, 21, friction plate.
Embodiment
Fig. 1 is the plan view of the initiatively adjustable vibration damper of damping.
As shown in Figure 2, vibration damper comprises oil cylinder 1, floating piston 2, piston 3 and piston rod 4.Oil cylinder 1 is divided into compressed air cell a, upper oil cavitie b and lower oil cavitie c by floating piston 2 and piston 3.Described floating piston 2 diameter is identical with oil cylinder 1, can freely slide axially along oil cylinder 1, forms an airtight cavity, be filled with high-pressure air in closed chamber with oil cylinder 1 one end, ensures that oil cylinder 1 inner fluid does not contact with air.Floating piston 2 and piston 3 all contact with oil cylinder 1 inner wall sealing.Piston rod 4 is connected with piston 3, and protrudes from the lower end of oil cylinder 1.Compressed air cell a effectively can reduce wheel and receive the dither produced when impacting suddenly, and compensates because piston rod 4 enters in oil cylinder 1, the reduction of oil cylinder 1 oil storage volume.Fluid between upper oil cavitie b with lower oil cavitie c is connected by pipeline d, one-way valve (5,13,14,15) and oil hydraulic motor (6).As shown in Figure 4, pipeline d is made up of four branch roads (d1, d2, d3, d4), and branch road d1 head end is connected with oil cylinder 1, is communicated with upper oil cavitie b, and tail end is connected with oil hydraulic motor 6 top, and centre is connected with one-way valve 14; Branch road d2 head end is connected by three-dimensional flowing valve with branch road d1, and tail end is connected by three-dimensional flowing valve with branch road d4, and centre is connected with one-way valve 13; Branch road d3 head end is connected by three-dimensional flowing valve with branch road d1, and tail end is connected by three-dimensional flowing valve with branch road d4, and centre is connected with one-way valve 15; Branch road d4 head end is connected with oil cylinder 1, is communicated with lower oil cavitie c, and tail end is connected with oil hydraulic motor 6 bottom, and centre is connected with one-way valve 5.Fluid in pipeline d flows through oil hydraulic motor 6, drives oil hydraulic motor 6 to rotate.Four one-way valves (5,13,14,15) are divided into two groups, one-way valve (5,14) is first group of one-way valve, lower oil cavitie c is flowed into after allowing the fluid of upper oil cavitie b to flow through described oil hydraulic motor 6, one-way valve (13,15) is second group of one-way valve, flows into upper oil cavitie b after allowing the fluid of lower oil cavitie c to flow through oil hydraulic motor 6.Due to the effect of one-way valve (5,13,14,15), the fluid in pipeline d is made to flow through oil hydraulic motor 6 from top to bottom all the time.As shown in Figure 5, when compression stroke, piston 3 moves upward, upper oil cavitie b fluid flows through one-way valve 14, oil hydraulic motor 6, and one-way valve 5 to lower oil cavitie c, due to now, one-way valve 15 upper end oil liquid pressure is greater than lower end, one-way valve 13 right-hand member oil liquid pressure is greater than left end, and therefore, fluid can not pass through one-way valve (13,15); As shown in Figure 6, when extension stroke, piston 3 moves downward, lower oil cavitie c fluid flows through one-way valve 13, oil hydraulic motor 6, one-way valve 15 to upper oil cavitie b, because now one-way valve 14 right-hand member oil liquid pressure is greater than left end, one-way valve 5 left end oil liquid pressure is greater than right-hand member, therefore, fluid can not pass through one-way valve (5,14).So the fluid in pipeline d flows through oil hydraulic motor 6 from top to bottom all the time.Flywheel 7 is fixedly linked with the output shaft of oil hydraulic motor 6, thus flywheel 7 rotates around same direction.
As shown in Figure 2, pipeline (e, f) to be communicated with by three-dimensional flowing valve with lower pipeline on oil hydraulic motor 6, and to lead to the left cylinder g of double-acting hydraulic cylinder 8 and right cylinder h.Double-acting hydraulic cylinder piston 9 seals with double-acting hydraulic cylinder 8 and contacts, and is divided into left cylinder g, right cylinder h.Push rod 10 is connected with double-acting hydraulic cylinder piston 9 and protrudes from left cylinder g, right cylinder h two ends.Owing to doing work to it when in pipeline d, fluid flows through oil hydraulic motor 6, and oil hydraulic motor 6 upper pipeline oil pressure is greater than lower pipeline all the time, and therefore in left cylinder g, oil pressure is greater than right cylinder h all the time.Spring 12 is on push rod 10 and be arranged in right cylinder h, and spring 12 not only makes up the pressure difference of left and right cylinder, also for double-acting hydraulic cylinder piston 9 provides restoring force left.Push rod 10 is connected with variable resistance arm 11, can promote variable resistance arm 11 and horizontally slip.
As shown in Figure 3, circuit comprises variable resistor 16, power supply 17, protective resistance 18, electromagnet A19, electromagnet B20.Electromagnet A19 is contrary with electromagnet B20 polarity to be installed, and because energising direction is contrary, thus produces repulsive force.Electromagnet B20 left end is connected with friction plate 21, and along with the adjustment of variable resistor 16 can move around, electromagnet A19 is fixed on vehicle bridge rigid location, irremovable.Friction plate 21 and flywheel 7 are fitted, and press to flywheel 7, because frictional force is directly proportional to pressure, so have variable frictional force between friction plate 21 and flywheel 7, thus the mechanical energy of flywheel 7 dissipates with form of thermal energy by friction.And by oil hydraulic motor 6 for the fluid in pipeline d provides resistance, form the damping of vibration damper.By horizontally slipping of variable resistance arm 11, the resistance value in variable resistor 16 put in circuit also changes, thus changes size of current.When variable resistance arm 11 drawn stem 10 retrain slide to the right time, resistance value in circuit becomes large, electric current reduces, thus the repulsive force of electromagnet A19, electromagnet B20 reduces, and makes friction plate 21 put on the pressure also corresponding reduction of flywheel 7, so the frictional force between friction plate 21 and flywheel 7 reduces, now, in oil hydraulic motor 6 couples of pipeline d, the resistance of fluid also reduces, thus the deattenuation of vibration damper; When variable resistance arm 11 drawn stem 10 retrain slide left time, resistance value in circuit diminishes, electric current increases, thus electromagnet A19, the repulsive force of electromagnet B20 increases, and makes the also corresponding increase of the frictional force between friction plate 21 to flywheel 7, now, in oil hydraulic motor 6 couples of pipeline d, the resistance of fluid also increases, thus the damping of vibration damper increases.During equilibrium position, variable resistance arm 11 is positioned at variable resistor 16 midpoint, when fluid flows, because the left cylinder g pressure of double-acting hydraulic cylinder 8 is greater than right cylinder h all the time, so variable resistance arm is only subject to push rod 10 thrust to the right, thus during equilibrium position, the resistance value of put in circuit is maximum.Protective resistance 18 provides short-circuit protection for circuit.
Working principle
When road conditions are excellent, the excitation of road surface to vibration damper is less, in pipeline d, oil flow is slower, thus the pressure difference being reflected in oil hydraulic motor 6 two ends is also less, the thrust that pressure difference acts on double-acting hydraulic cylinder piston 9 is equal with the power of spring 12, and now double-acting hydraulic cylinder piston 9 is in equilibrium position fluctuation.Variable resistance arm 11 is positioned at variable resistor 16 midpoint, and circuit is big current, electromagnet A19, between electromagnet B20, repulsive force is larger, the frictional force that friction plate 21 puts on flywheel 7 is comparatively large, thus oil hydraulic motor 6 provides large flow resistance for fluid in pipeline d, and vibration damper has large damping.Now meet the requirement to travelling comfort and Security of vehicle under good road conditions travel.
When road conditions are severe, road surface is very large to the excitation of vibration damper, in pipeline d, oil flow is very fast, thus the pressure difference being reflected in oil hydraulic motor 6 two ends also raises, now because the left and right cylinder pressure difference of double-acting hydraulic cylinder 8 becomes large, the thrust that pressure difference acts on double-acting hydraulic cylinder piston 9 increases, thus the power that promotion double-acting hydraulic cylinder piston 9 overcomes spring 12 moves right.Due to the constraint of push rod 10, variable resistance arm 11 slides to the right, and access resistance value in circuit and become large, electric current reduces.Electromagnet A19, the repulsion between electromagnet B20 is corresponding reduction also, and the frictional force of friction plate 21 pairs of flywheels 7 reduces, thus the flow resistance that oil hydraulic motor 6 pairs of pipeline d inner fluids provide reduces, and resistance of shock absorber reduces.Now meet the requirement to travelling comfort and Security of vehicle under severe road conditions travel.
During different road conditions, because oil hydraulic motor 6 pressure at two ends difference is different, the damping of final vibration damper is not identical yet, and vehicle can be made according to travelling the quality adjustable suspension damping adaptively size of road conditions to realize the optimal control of semi-active suspension.The vibrational energy of vibration damper is converted into mechanical energy, and consumes so that form of thermal energy is loose eventually through friction, reaches reduction oil liquid temperature, makes vibration damper keep the function of premium properties.
Claims (6)
1. the dydraulic shock absorber that a damping is initiatively adjustable, it is characterized in that: comprise oil cylinder (1), floating piston (2), piston (3), one-way valve (5,13,14,15), oil hydraulic motor (6), flywheel (7), double-acting hydraulic cylinder piston (9), push rod (10), variable resistor (16), electromagnet A (19), electromagnet B (20), friction plate (21); Described oil cylinder (1) is divided into compressed air cell a, upper oil cavitie b and downstream cavity c by floating piston (2) and piston (3); Described floating piston (2) one end contacts with fluid, and one end is sealing gas chamber; Described one-way valve (5,13,14,15) is installed in a specific way; Described flywheel (7) is fixedly linked with the output shaft of oil hydraulic motor (6), and contacts with friction plate (21); Described double-acting hydraulic cylinder piston (9) promotes variable resistance arm (11) and horizontally slips; Described electromagnet B (20) is connected with friction plate (21).
2. the dydraulic shock absorber that a kind of damping according to claim 1 is initiatively adjustable, it is characterized in that: described oil cylinder (1) is isolated into upper oil cavitie b and downstream cavity c by piston (3), upper oil cavitie b is connected by pipeline d, one-way valve (5,13,14,15) and oil hydraulic motor (6) with downstream cavity c.
3. the dydraulic shock absorber that a kind of damping according to claim 1 is initiatively adjustable, it is characterized in that: it is inner that described floating piston (2) is installed on oil cylinder (1), diameter is identical with oil cylinder (1), can freely slide axially along oil cylinder (1), an airtight cavity is formed with oil cylinder (1) one end, be filled with high-pressure air in closed chamber, ensure that oil cylinder (1) inner fluid does not contact with air.
4. the dydraulic shock absorber that a kind of damping according to claim 1 is initiatively adjustable, is characterized in that: described electromagnet A (19) is contrary with electromagnet B (20) polarity installs.
5. the dydraulic shock absorber that a kind of damping according to claim 1 is initiatively adjustable, it is characterized in that: described double-acting hydraulic cylinder piston (9) seals with double-acting hydraulic cylinder (8) and contacts, and be divided into left cylinder g, right cylinder h, push rod 10 is connected with double-acting hydraulic cylinder piston 9 and protrudes from left cylinder g, right cylinder h two ends, described push rod (10) is connected with variable resistance arm (11), can promote variable resistance arm (11) and horizontally slip.
6. the dydraulic shock absorber that a kind of damping according to claim 2 is initiatively adjustable, it is characterized in that: described pipeline d is made up of four branch roads (d1, d2, d3, d4), branch road d1 head end is connected with oil cylinder 1, be communicated with upper oil cavitie b, tail end is connected with oil hydraulic motor 6 top, and centre is connected with one-way valve 14; Branch road d2 head end is connected by three-dimensional flowing valve with branch road d1, and tail end is connected by three-dimensional flowing valve with branch road d4, and centre is connected with one-way valve 13; Branch road d3 head end is connected by three-dimensional flowing valve with branch road d1, and tail end is connected by three-dimensional flowing valve with branch road d4, and centre is connected with one-way valve 15; Branch road d4 head end is connected with oil cylinder 1, is communicated with lower oil cavitie c, and tail end is connected with oil hydraulic motor 6 bottom, and centre is connected with one-way valve 5.Fluid in pipeline d flows through oil hydraulic motor 6, drives oil hydraulic motor 6 to rotate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
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| CN201310515706.7A CN104565178A (en) | 2013-10-21 | 2013-10-21 | Hydraulic shock absorber with active adjustable damping |
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| Application Number | Priority Date | Filing Date | Title |
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| CN201310515706.7A CN104565178A (en) | 2013-10-21 | 2013-10-21 | Hydraulic shock absorber with active adjustable damping |
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| CN104565178A true CN104565178A (en) | 2015-04-29 |
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| CN201310515706.7A Pending CN104565178A (en) | 2013-10-21 | 2013-10-21 | Hydraulic shock absorber with active adjustable damping |
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Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN105276063A (en) * | 2015-10-26 | 2016-01-27 | 青岛理工大学 | Energy feedback hydraulic shock absorber system with damping force capable of being accurately controlled |
| 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 |
| TWI588378B (en) * | 2015-04-30 | 2017-06-21 | Liu li-qun | Buffer storage device |
| CN110397695A (en) * | 2019-07-17 | 2019-11-01 | 重庆大学 | Magnetorheological half active variable damping and the suspension damper mechanism for actively becoming used appearance |
Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3939485A1 (en) * | 1989-11-29 | 1990-04-05 | Rainer Dipl Ing Daumann | Motor vehicle shock absorber - has device to increase damping force as load on vehicle increases |
| CN1699781A (en) * | 2005-06-24 | 2005-11-23 | 浙江大学 | Vehicle hydraulic damper with actively adjustable damping for semiactive suspension |
| CN102345701A (en) * | 2011-10-17 | 2012-02-08 | 江苏大学 | Vehicle oil gas spring with adjustable rigidity and damping |
| CN103322112A (en) * | 2013-06-25 | 2013-09-25 | 苏州唐氏机械制造有限公司 | Operating method of buffer unit which adjusts motion of piston according to impact pressure |
| CN103423363A (en) * | 2013-08-12 | 2013-12-04 | 江苏大学 | Hydraulic damper with actively-adjustable damping |
| CN203477160U (en) * | 2013-05-17 | 2014-03-12 | 盐城纺织职业技术学院 | Hydraulic shock absorber with active adjustable damping |
-
2013
- 2013-10-21 CN CN201310515706.7A patent/CN104565178A/en active Pending
Patent Citations (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3939485A1 (en) * | 1989-11-29 | 1990-04-05 | Rainer Dipl Ing Daumann | Motor vehicle shock absorber - has device to increase damping force as load on vehicle increases |
| CN1699781A (en) * | 2005-06-24 | 2005-11-23 | 浙江大学 | Vehicle hydraulic damper with actively adjustable damping for semiactive suspension |
| CN102345701A (en) * | 2011-10-17 | 2012-02-08 | 江苏大学 | Vehicle oil gas spring with adjustable rigidity and damping |
| CN203477160U (en) * | 2013-05-17 | 2014-03-12 | 盐城纺织职业技术学院 | Hydraulic shock absorber with active adjustable damping |
| CN103322112A (en) * | 2013-06-25 | 2013-09-25 | 苏州唐氏机械制造有限公司 | Operating method of buffer unit which adjusts motion of piston according to impact pressure |
| CN103423363A (en) * | 2013-08-12 | 2013-12-04 | 江苏大学 | Hydraulic damper with actively-adjustable damping |
Cited By (5)
| 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 |
| CN105276063A (en) * | 2015-10-26 | 2016-01-27 | 青岛理工大学 | Energy feedback hydraulic shock absorber system with damping force capable of being accurately controlled |
| CN105276063B (en) * | 2015-10-26 | 2017-06-06 | 青岛理工大学 | Energy feedback hydraulic shock absorber system with damping force capable of being accurately controlled |
| CN110397695A (en) * | 2019-07-17 | 2019-11-01 | 重庆大学 | Magnetorheological half active variable damping and the suspension damper mechanism for actively becoming used appearance |
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Free format text: CORRECT: ADDRESS; FROM: 224005 YANCHENG, JIANGSU PROVINCE TO: 212013 ZHENJIANG, JIANGSU PROVINCE Free format text: CORRECT: INVENTOR; FROM: CHEN ANZHU SU HONGLIN WANG YIJUN LUO WENHUA TO: LI ZHONGXING CHEN WANG WU YUE JU LONGYU |
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