CN118306153B - Valve-controlled constant-damping adjustable fluid inertial-volume suspension device - Google Patents
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- CN118306153B CN118306153B CN202410399662.4A CN202410399662A CN118306153B CN 118306153 B CN118306153 B CN 118306153B CN 202410399662 A CN202410399662 A CN 202410399662A CN 118306153 B CN118306153 B CN 118306153B
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- 238000013016 damping Methods 0.000 title claims abstract description 107
- 239000012530 fluid Substances 0.000 title claims abstract description 82
- 239000000725 suspension Substances 0.000 title claims abstract description 47
- 239000007788 liquid Substances 0.000 claims abstract description 54
- 238000005452 bending Methods 0.000 claims description 6
- 238000006073 displacement reaction Methods 0.000 claims description 6
- 231100000252 nontoxic Toxicity 0.000 claims description 3
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- XLYOFNOQVPJJNP-UHFFFAOYSA-N water Substances O XLYOFNOQVPJJNP-UHFFFAOYSA-N 0.000 claims description 3
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
- B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
- B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
- B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G17/00—Resilient suspensions having means for adjusting the spring or vibration-damper characteristics, for regulating the distance between a supporting surface and a sprung part of vehicle or for locking suspension during use to meet varying vehicular or surface conditions, e.g. due to speed or load
- B60G17/02—Spring characteristics, e.g. mechanical springs and mechanical adjusting means
- B60G17/04—Spring characteristics, e.g. mechanical springs and mechanical adjusting means fluid spring characteristics
- B60G17/056—Regulating distributors or valves for hydropneumatic systems
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Abstract
The invention discloses a valve-controlled constant-damping adjustable fluid inertial volume suspension device, which is based on a double-rod hydraulic cylinder, realizes the switching of two liquid flow pipelines through a high-speed switch valve, and ensures that expected inertial force and damping force are generated when fluid flows through any liquid flow pipeline at high speed through structural parameter design, the adjustment of the inertial force and the damping force are mutually independent, and the damping force is constant. A spiral tube is arranged, and fluid flows from one side of the hydraulic cylinder barrel to the other side of the hydraulic cylinder barrel through the spiral tube to form a first liquid flow pipeline. The fluid flows from one side of the hydraulic cylinder barrel to the other side to form a second liquid flow pipeline through the short straight pipe provided with the damping hole. The invention is suitable for the severe working condition of the suspension device of the military vehicle, can switch two working pipelines through switch control so as to adjust the inertia capacity and damping characteristic of suspension, thereby greatly improving the vibration damping performance of the suspension device and having good application value.
Description
Technical Field
The invention relates to the technical field of vibration reduction and vehicle suspension, in particular to a valve-controlled constant-damping adjustable fluid inertial-volume suspension device.
Background
The university of Cambridge Smith 2002 proposes the concept of an inertial container (Inerter), and thus a novel vibration isolation theory system of inertial capacity-spring-damping is constructed, and the inertial container is helpful for solving the common problem in the vibration reduction and noise reduction field. The concept of a fluid inertial container, which is produced by accelerating the flow of a liquid in a helical channel, with the dynamics of making the axial force proportional to the relative acceleration of the two ends, was proposed as early as 2010. The fluid inertial container not only has enough load bearing capacity, but also has simple structure and high stability, is considered as the inertial container form of the most potential practical mass production, has the advantages of large inertial coefficient, strong impact resistance and the like, and is suitable for the severe working condition of a suspension device of a military vehicle. More importantly, because of various self-contained damping effects generated in the flowing process of the liquid, the liquid has structural expansibility capable of combining various damping and inertia effect into a whole, for example, the damping of different topological structures can be added by utilizing a flow limiting valve and a piston oil hole so as to adjust the inertia and damping characteristics of the suspension, thereby greatly improving the comprehensive performance of the suspension. Therefore, designing a fluid inertial container with a proper structure becomes a research hot spot and an important point in the current inertial container field.
The patent CN201510762454.7 provides a double-pipeline fluid inertial container with variable inertial coefficient, and the on-off of a pipeline is controlled by controlling the on-off of a valve, so that the circulation mode of oil is regulated, the fluid inertial container device with the large, medium and small three-level adjustable inertial coefficients is realized, and the advantages of simple control, easiness in realization and the like are realized. It has been described that various damping effects are produced during the high-speed flow of fluid through the conduit, but as in this patent, the prior art references only consider inertial forces and do not consider the effects of damping forces. However, in engineering practice, when oil flows in pipelines with different pipe diameters or (and) lengths, damping force tends to be different, and when the control valve described in patent CN201510762454.7 is opened and closed at a high speed, the damping force also fluctuates greatly in the process of adjusting the inertia coefficient, and in this case, although the vibration reduction effect can be improved due to the change of the inertia coefficient, the vibration reduction efficiency tends to be reduced due to the large fluctuation of the damping force. Therefore, under certain working conditions, fluctuation of damping force can weaken beneficial effects brought by inertia coefficient adjustment, under certain extreme working conditions, severe fluctuation of damping force can cause incapability of quickly suppressing resonance, even strong impact is generated, so that riding comfort of a vehicle is poor, and problems in terms of steering stability can be caused, so that extremely dangerous working conditions such as instability of the whole vehicle, steering failure and the like are caused.
Disclosure of Invention
Aiming at the defects in the prior art, the invention provides a valve-control constant-damping adjustable fluid inertial-volume suspension device scheme.
The present invention achieves the above technical object by the following means.
A valve-controlled constant-damping adjustable fluid inertial suspension device is based on a double-rod hydraulic cylinder, the double-rod hydraulic cylinder comprises a hydraulic cylinder barrel (11) and a piston rod (12), the hydraulic cylinder barrel (11) outputs force outwards, the left end point of the hydraulic cylinder barrel and the right end point of the piston rod (12) are two interfaces of inertial force, switching of two liquid flow pipelines is achieved through a high-speed switching valve (9), expected inertial force and damping force are generated when fluid flows through any liquid flow pipeline at a high speed through structural parameter design, adjustment of the inertial force and the damping force are independent of each other, the damping force is kept constant, a first liquid flow pipeline is formed by connecting a linear inertial container with a nonlinear damper in parallel, a second liquid flow pipeline is formed by connecting a linear inertial container with the nonlinear damper in parallel, and a nonlinear damper with small hole throttling is overlapped.
Further, a spiral tube (8) is arranged, fluid flows from one side of the hydraulic cylinder barrel (11) to the other side through the spiral tube (8) to form a first liquid flow pipeline, a short straight tube (6) with a damping hole (7) is arranged, and fluid flows from one side of the hydraulic cylinder barrel (11) to the other side through the short straight tube (6) with the damping hole (7) to form a second liquid flow pipeline.
Further, the damping force of the first liquid flow pipeline is changed by changing the bending radius of the spiral pipe, the damping force of the second liquid flow pipeline is changed by changing the radius of the damping hole, the inertial force of the first liquid flow pipeline is changed by changing the length of the spiral pipe pipeline or the inner diameter of the spiral pipe or both the length of the spiral pipe pipeline and the inner diameter of the spiral pipe, and the inertial force of the second liquid flow pipeline is changed by changing the inner diameter of the short straight pipe pipeline or the length of the short straight pipe or both the inner diameter of the short straight pipe pipeline and the length of the short straight pipe.
Further, the method for calculating the damping force F c of the first liquid flow line is as follows:
Wherein,
Z 1 is the displacement of one end point, z 2 is the displacement of the other end point,Relative speed for two endpoints;
sign is a sign function;
ρ is the density of the oil liquid,
L ch is the length of the spiral pipe line,N is the number of turns of the spiral tube, h is the helical pipe pitch;
R c is the inner diameter of the oil cylinder, R r is the radius of the piston rod, R is the bending radius of the spiral tube, and R ch is the inner diameter of the spiral tube.
Further, the method for calculating the damping force F c of the second liquid flow line is as follows:
Wherein,
R c is the inner diameter of the oil cylinder, r r is the radius of the piston rod, C d is the flow coefficient, and r k is the radius of the damping hole;
Mu is dynamic viscosity of fluid, l is length of short straight pipe, and r h is inner diameter of short straight pipe.
Further, the method for calculating the inertia force b of the first liquid flow pipeline is as follows:
further, the method for calculating the inertial force b of the second liquid flow pipeline is as follows:
Furthermore, the fluid is water, nontoxic and harmless low-viscosity oil or magnetorheological fluid, the double-rod hydraulic cylinder formed by the hydraulic cylinder barrel (11) and the piston rod (12) is made of steel materials, the short straight pipe (6) and the spiral pipe (8) are made of rubber materials, and the high-speed switching valve (9) adopts a high-precision valve system structure.
Compared with the prior art, the invention has the beneficial effects that:
1. The invention provides a single-cylinder novel fluid inertial-volume suspension device scheme, and particularly provides a valve-control constant-damping adjustable fluid inertial-volume suspension device. Compared with the traditional fluid inertial container, the invention adopts a single-cylinder fluid inertial container structure, is provided with a spiral pipe liquid flow pipeline and a short straight pipe liquid flow pipeline, and can switch the working liquid flow pipeline through a high-speed switch valve, thereby realizing the adjustment of the inertial coefficient of the fluid inertial container.
2. The valve-controlled constant-damping adjustable fluid inertial volume suspension device has a structure that various damping and inertial volume effects are integrated, is used for adjusting the inertial volume and damping characteristics of suspension, can greatly improve the comprehensive performance of suspension, has sufficient load bearing capacity, has high inertial mass coefficient and strong impact resistance, is suitable for severe working conditions of the off-road vehicle suspension device, and has higher application value.
3. The scheme of the invention is simple and easy to understand, and the principle is reliable and easy to implement.
4. The short straight pipes can provide smaller inertia force, and compared with the spiral pipe, the damping force generated by the short straight pipes is smaller, and when the flow passage of oil is switched between the short straight pipes through the spiral pipe, the damping force can generate severe fluctuation. According to the invention, the orifice device is added in the short straight pipe, and the size of the orifice is regulated to ensure that the damping force is kept approximately constant when the oil is switched between the spiral pipe and the short straight pipe, so that the fluctuation of the damping force is reduced, and the vibration reduction efficiency of suspension is greatly improved.
5. The invention realizes constant damping force in the switching process by setting the size of the damping hole, and has simple structure, good manufacturability and low cost.
Drawings
FIG. 1 is a schematic diagram of a valve-controlled constant damping adjustable fluid inertial suspension apparatus according to the present invention.
FIG. 2 is an equivalent schematic diagram of a valve-controlled constant-damping adjustable fluid inertial suspension device spiral pipe structure according to the present invention.
FIG. 3 is an equivalent schematic diagram of a valve-controlled constant-damping adjustable fluid inertial suspension device short straight pipe pipeline structure.
FIG. 4 is a schematic illustration of an embodiment of a valve controlled constant damping adjustable fluid inertial suspension apparatus according to the present invention.
FIG. 5 is an equivalent schematic diagram of an embodiment of a valve-controlled constant damping adjustable fluid inertial suspension device according to the present invention.
In the figure, 1a first end point, 2a left cavity, 3a right cavity, 4 a second end point, 5a first oil port, 6a short straight pipe, and 7, a damping hole, 8, a spiral pipe, 9, a high-speed switch valve, 10, a second oil port, 11, a hydraulic cylinder barrel and 12, a piston rod.
Detailed Description
In order that the invention may be readily understood, a more complete description of the invention will be rendered by reference to the appended drawings. This invention may be embodied in many different forms and the specific embodiments described herein are merely illustrative of the invention and are not intended to be limiting. Rather, the purpose of the present disclosure is to provide a better understanding of the present disclosure, taken in conjunction with the accompanying drawings and examples.
As shown in figure 1, the valve-controlled constant-damping adjustable fluid inertial suspension device comprises a first end point 1, a second end point 4, a left oil cavity 2, a right oil cavity 3, a first oil port 5, a second oil port 10, a short straight pipe 6, a damping hole 7, a spiral pipe 8, a high-speed switch valve 9, a hydraulic cylinder 11 and a piston rod 12. The valve-controlled constant-damping adjustable fluid inertial suspension device comprises a double-rod hydraulic cylinder, wherein the double-rod hydraulic cylinder consists of a hydraulic cylinder 11 and a piston rod 12, and outputs force outwards. The left side of the cylinder 11 is provided with an end point 1, the right side of the piston rod 12 is provided with an end point 4, and the end point 1 and the end point 4 are two interfaces of inertial force. The valve-controlled constant-damping adjustable fluid inertial suspension device can generate inertial force and damping force in the working process, comprises two liquid flow pipeline combinations, and realizes the switching of working pipelines of the fluid inertial suspension device by controlling the high-speed switch valve 9 by using a switch control method. The oil cavities 2 and 3, the oil ports 5 and 10 and the spiral pipe 8 form a first liquid flow pipeline, and the oil cavities 2 and 3, the oil ports 5 and 10, the short straight pipe 6 and the damping hole 7 form a second liquid flow pipeline. The high-speed switch valve 9 can control the on-off of the spiral pipe 8 and the short straight pipe 6, so that the two liquid flow pipeline working modes are switched. When fluid flows through the two fluid lines at high velocity, inertial and damping forces are created. When the endpoints 1 and 4 move relatively, the oil liquid is forced to reciprocate between the liquid flow pipelines at high speed, so that the encapsulation of inertial force is realized. The on-off of the spiral pipe 8 and the short straight pipe 6 is controlled through the high-speed switch valve 9, and the working modes of the two liquid flow pipelines are switched, so that the adjustment of the fluid inertial volume suspension inertial mass coefficient is realized. The oil chambers 2,3, the oil ports 5, 10 and the spiral pipe 8 form a first liquid flow pipeline. When fluid flows through the first fluid flow pipeline, a larger parasitic damping force is generated while an inertia force is provided, and the mechanical property of the parasitic damping force is equivalent to that of a linear inertia container and a nonlinear damper which are connected in parallel is shown in figure 2. By optimizing the structural parameters of the spiral tube 8, an optimal combination of inertial and damping coefficients can be obtained, depending on the dynamics requirements of the suspension. The oil cavities 2,3, the oil ports 5, 10, the short straight pipe 6 and the damping hole 7 form a second liquid flow pipeline. When fluid flows through the second liquid flow pipeline, the mechanical property of the fluid is equivalent to the parallel connection of a linear inertial container and a nonlinear damper, and the nonlinear damper with small orifice throttling is overlapped, as shown in fig. 3, and the combination of a small inertial coefficient and a large damping coefficient can be realized through the additional orifice throttling effect. The fluid can be water, nontoxic and harmless low-viscosity oil liquid or magnetorheological fluid, etc. The high-speed switch valve 9 adopts a high-precision valve system structure. The device has enough load bearing capacity, large inertial coefficient and strong impact resistance, and is suitable for the severe working condition of the off-road vehicle suspension device.
The working principle of the valve-controlled constant-damping adjustable fluid inertial-volume suspension device, the mechanical property calculation method and the valve-controlled constant-damping adjustable fluid inertial-volume suspension device embodiment scheme are further provided below, the scheme is simple and easy to understand, and the principle is reliable and easy to implement.
The piston is subjected to stress analysis by considering the damping force F c and the inertia force F b of the oil flowing through two liquid flow pipelines without considering the influence of potential energy, heat energy dissipation and temperature change on the oil flow, so that an equivalent schematic diagram of the two liquid flow pipeline structures can be obtained, as shown in fig. 2 and 3.
The stress F at the two ends of the fluid inertial container is as follows:
F=Fc+Fb (1)
Inertial force F b is
Wherein: for the relative acceleration of the two end points, the magnitudes of the damping force F c and the inertial force F b were quantitatively analyzed, and a detailed comparative analysis was performed on the two fluid flow lines flowing through the spiral pipe 8 and the short straight pipe 6+ damping hole 7, as shown in the following table, in which: For relative speed sign is a sign function, other structural dimensions are defined in the following table.
As shown in the table above, when fluid flows through the coil 8, a large parasitic damping force is generated while providing inertial force, the mechanical properties of which are equivalent to a parallel connection of a linear inertial container and a nonlinear damper. When fluid flows through the combined pipeline of the short straight pipe 6 and the damping hole 7, the combined pipeline is equivalent to the parallel connection of a linear inertial container and a nonlinear damper, and the nonlinear damper with small hole throttling is overlapped. The damping hole has the function of ensuring that the damping force is approximately constant during the switching process.
It can be found from the calculation formulas in the table that in the spiral tube liquid flow loop, the dynamic viscosity μ of the fluid and the bending radius R of the spiral tube affect only the magnitude of the damping force, irrespective of the magnitude of the inertial force, so that the magnitude of the inertial force and the damping force flowing through the spiral tube 8 can be decoupled by adjusting the dynamic viscosity μ of the fluid and the bending radius R of the spiral tube. Similarly, the inertial force and the damping force flowing through the combination of the short straight pipe 6 and the damping hole 7 can be decoupled by adjusting the dynamic viscosity mu of the fluid and the radius r k of the damping hole 7. Therefore, the required inertial coefficient can be obtained by optimizing rho, R c,rch,rr,lch of the first liquid flow pipeline and rho, R c,rh,rr and l of the second liquid flow pipeline, the aim of adjusting the inertial force of the two liquid flow pipelines is fulfilled by optimizing R ch,lch and R h and l respectively because rho and R c,rr are related simultaneously, the optimal damping force can be realized by adjusting R or R k on the basis of determining the inertial coefficient, the optimized inertial coefficient cannot be influenced, and the method can simultaneously obtain the optimal inertial coefficient and the optimal damping coefficient by adjusting the structural size of the fluid inertial container.
An embodiment of a valve-controlled constant-damping adjustable fluid inertial-volume suspension device is shown in fig. 4, and an equivalent schematic diagram of an embodiment of the valve-controlled constant-damping adjustable fluid inertial-volume suspension device is shown in fig. 5. The upper cross arm and the lower cross arm adopt a double-fork arm structure, the upper cross arm, the lower cross arm and a main pin form a steering knuckle, a single-cylinder fluid inertial container is arranged on the inner side of a wheel, the upper end point of the single-cylinder fluid inertial container is connected with a vehicle body through an upper hinge, the lower end point of the single-cylinder fluid inertial container is connected with the lower cross arm through a lower hinge, and the cylinder barrel can change along with the suspension compression or recovery stroke, so that the single-cylinder fluid inertial container is connected with a spiral pipe and a short straight pipe through a rubber hose to serve as a channel for fluid to flow back and forth between the two hydraulic cylinders, and the on-off of the spiral pipe and the short straight pipe is controlled through a high-speed switch valve by using a switch control method, so that the inertial coefficient of the inertial container is adjusted. The suspension model is equivalent to a structure with three elements of adjustable inertial volume, a spring and damping connected in parallel, wherein the adjustable inertial volume is provided by flowing through different pipelines, the spring adopts a spiral spring, the damping is viscous damping generated by flowing through the pipelines, and the damping of each pipeline is constant.
Specifically, when the vehicle encounters jolt in the running process, the single-acting hydraulic cylinder is in a compressed or stretched state, the wheels move upwards or downwards relative to the vehicle body, so that excessive dynamic load is not generated on the wheels, the longitudinal displacement of the vehicle body is small, the inertia force generated by the fluid inertial container is small, namely the inertial coefficient of the fluid inertial container is small, the wheels can move relatively fast relative to the fluid inertial container, the kinetic energy generated by the movement of the wheels is absorbed through the flow of the fluid in the inertial container, and therefore the displacement of the vehicle body in the longitudinal direction is reduced, and the vibration reduction effect is exerted. According to the method for calculating the inertial coefficient, in order to achieve the purpose of reducing the inertial coefficient, the high-speed switching valve is required to be communicated with a short straight pipe and damping hole combined pipeline, so that the inertial coefficient of the inertial container is reduced, and the damping coefficient is increased.
When the vehicle runs from a bumpy road surface to a flat road surface, the vehicle suspension can return to a normal state, and the inertial container has larger inertial force, namely larger inertial coefficient, so as to achieve the purposes of reducing or avoiding the impact generated by the wheel pressing back to the ground and keeping the vehicle body stable. In order to achieve the purpose of increasing the inertial coefficient, the high-speed switching valve needs to be communicated with a spiral pipe pipeline, so that the inertial coefficient of the inertial container is increased, and a proper damping coefficient is obtained. The damping performance of the valve-controlled adjustable fluid inertia suspension device is optimal under different working conditions through the on-off control of the liquid flow pipeline.
The above embodiments are merely for illustrating the design concept and features of the present invention, and are intended to enable those skilled in the art to understand the content of the present invention and implement the same, the scope of the present invention is not limited to the above embodiments. Therefore, all equivalent changes or modifications according to the principles and design ideas of the present invention are within the scope of the present invention.
Claims (6)
1. The valve-controlled constant-damping adjustable fluid inertial suspension device is based on a double-rod hydraulic cylinder, the double-rod hydraulic cylinder comprises a hydraulic cylinder barrel (11) and a piston rod (12) which output force outwards, and the left end point of the hydraulic cylinder barrel (11) and the right end point of the piston rod (12) are two interfaces of inertial force, and the valve-controlled constant-damping adjustable fluid inertial suspension device is characterized in that switching of two liquid flow pipelines is realized through a high-speed switching valve (9), the expected inertial force and damping force are generated when fluid flows through any liquid flow pipeline at a high speed through structural parameter design, the adjustment of the inertial force and the damping force are mutually independent, the damping force is constant, wherein a first liquid flow pipeline is formed by connecting a linear inertial container with a nonlinear damper in parallel, and a second liquid flow pipeline is formed by connecting a linear inertial container with the nonlinear damper in parallel and superposing a nonlinear damper with a small hole for throttling;
The hydraulic cylinder is provided with a spiral pipe (8), fluid flows from one side of the hydraulic cylinder (11) to the other side through the spiral pipe (8) to form a first liquid flow pipeline, a short straight pipe (6) with a damping hole (7) is arranged, and the fluid flows from one side of the hydraulic cylinder (11) to the other side through the short straight pipe (6) with the damping hole (7) to form a second liquid flow pipeline;
The damping force of the first liquid flow pipeline is changed by changing the bending radius of the spiral pipe, the damping force of the second liquid flow pipeline is changed by changing the radius of the damping hole, the inertial force of the first liquid flow pipeline is changed by changing the length of the spiral pipe pipeline or the inner diameter of the spiral pipe or both the length of the spiral pipe pipeline and the inner diameter of the spiral pipe, and the inertial force of the second liquid flow pipeline is changed by changing the inner diameter of the short straight pipe pipeline or both the inner diameter of the short straight pipe pipeline and the length of the short straight pipe.
2. The valve controlled constant damping adjustable fluid inertial suspension device of claim 1, wherein the damping force F c of the first fluid flow line is calculated by:
Wherein,
Z 1 is the displacement of one end point, z 2 is the displacement of the other end point,Relative speed for two endpoints;
sign is a sign function;
ρ is the density of the oil liquid,
L ch is the length of the spiral pipe line,N is the number of turns of the spiral tube, h is the helical pipe pitch;
R c is the inner diameter of the oil cylinder, R r is the radius of the piston rod, R is the bending radius of the spiral tube, and R ch is the inner diameter of the spiral tube.
3. The valve controlled constant damping adjustable fluid inertial suspension device of claim 2, wherein the damping force F c of the second fluid flow line is calculated by:
Wherein,
R c is the inner diameter of the oil cylinder, r r is the radius of the piston rod, C d is the flow coefficient, and r k is the radius of the damping hole;
Mu is dynamic viscosity of fluid, l is length of short straight pipe, and r h is inner diameter of short straight pipe.
4. A valve controlled constant damping adjustable fluid inertial suspension according to claim 3, characterized in that the inertial force b of the first flow line is calculated as follows:
5. The valve controlled constant damping adjustable fluid inertial suspension device of claim 4, wherein the inertial force b of the second flow conduit is calculated by:
6. The valve-controlled constant-damping adjustable fluid inertial-volume suspension device according to any one of claims 1-5, wherein the fluid is water, nontoxic harmless low-viscosity oil or magnetorheological fluid, and the high-speed switching valve (9) adopts a high-precision valve system structure.
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Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103538434A (en) * | 2013-09-24 | 2014-01-29 | 江苏大学 | Vehicle suspension structure with inerter-spring-damper |
| CN105276060A (en) * | 2015-11-10 | 2016-01-27 | 江苏大学 | Double-pipeline liquid inertia container with variable inerter coefficient |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP4464798B2 (en) * | 2004-11-24 | 2010-05-19 | トヨタ自動車株式会社 | Vehicle suspension system |
| CN100368701C (en) * | 2006-07-19 | 2008-02-13 | 中南大学 | Magneto-rheological fluid adjustable damper |
| CN203730646U (en) * | 2013-09-18 | 2014-07-23 | 中国北方车辆研究所 | Inertia mass energy accumulation type vibration damping device with parallel dampers |
| KR102548819B1 (en) * | 2016-09-02 | 2023-06-28 | 에이치엘만도 주식회사 | Regenerative suspension for vehicle |
| CN111086363A (en) * | 2020-01-20 | 2020-05-01 | 中国北方车辆研究所 | Two-stage serial-type suspension structure with double inertial containers |
| CN114211925B (en) * | 2021-12-30 | 2023-08-15 | 尨腾汽车科技(南京)有限公司 | Self-powered active suspension single-head oil cylinder equal-damping equal-inertial-volume oil circuit and working method thereof |
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Patent Citations (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN103538434A (en) * | 2013-09-24 | 2014-01-29 | 江苏大学 | Vehicle suspension structure with inerter-spring-damper |
| CN105276060A (en) * | 2015-11-10 | 2016-01-27 | 江苏大学 | Double-pipeline liquid inertia container with variable inerter coefficient |
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