CN113895198A - Gas spring interconnected suspension system and vehicle with same - Google Patents
Gas spring interconnected suspension system and vehicle with same Download PDFInfo
- Publication number
- CN113895198A CN113895198A CN202111180416.2A CN202111180416A CN113895198A CN 113895198 A CN113895198 A CN 113895198A CN 202111180416 A CN202111180416 A CN 202111180416A CN 113895198 A CN113895198 A CN 113895198A
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- suspension system
- oil cylinder
- interconnected suspension
- cylinder
- side oil
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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
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G21/00—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces
- B60G21/02—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected
- B60G21/06—Interconnection systems for two or more resiliently-suspended wheels, e.g. for stabilising a vehicle body with respect to acceleration, deceleration or centrifugal forces permanently interconnected fluid
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2202/00—Indexing codes relating to the type of spring, damper or actuator
- B60G2202/10—Type of spring
- B60G2202/15—Fluid spring
- B60G2202/154—Fluid spring with an accumulator
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- B—PERFORMING OPERATIONS; TRANSPORTING
- B60—VEHICLES IN GENERAL
- B60G—VEHICLE SUSPENSION ARRANGEMENTS
- B60G2204/00—Indexing codes related to suspensions per se or to auxiliary parts
- B60G2204/62—Adjustable continuously, e.g. during driving
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- Vehicle Body Suspensions (AREA)
Abstract
The invention provides a gas-spring interconnected suspension system and a vehicle with the same, wherein the gas-spring interconnected suspension system comprises: an interconnected suspension system, the interconnected suspension system comprising: a first accumulator and a second accumulator; the hydro-cylinder, the hydro-cylinder includes: the front left side oil cylinder, the front right side oil cylinder, the rear left side oil cylinder and the rear right side oil cylinder are all provided with an upper cavity and a lower cavity which are separated by a piston; the first oil way is communicated with the upper cavity of the front left oil cylinder, the lower cavity of the front right oil cylinder, the upper cavity of the rear left oil cylinder, the lower cavity of the rear right oil cylinder and the first energy accumulator; and the second oil way is communicated with the lower cavity of the front left-side oil cylinder, the upper cavity of the front right-side oil cylinder, the lower cavity of the rear left-side oil cylinder, the upper cavity of the rear right-side oil cylinder and the second energy accumulator. The technical scheme of the embodiment of the invention can control the stability and the smoothness of the gas-spring interconnected suspension system, improve the tire grip, improve the vehicle trafficability and improve the average cross-country vehicle speed.
Description
Technical Field
The invention relates to the field of vehicles, in particular to an oil-gas spring interconnected suspension system and a vehicle with the same.
Background
Traditional two xarm coil spring suspension systems, in order to satisfy the vehicle ride comfort, coil spring rigidity design ratio is lower, and is the constant stiffness spring mostly, consequently must install the stabilizer bar additional to increase the roll rigidity, reduce the roll angle when the vehicle turns. Similarly, the roll stiffness generated by the hydro-pneumatic spring is very low when the suspension system is at a design position due to the nonlinear characteristic of the hydro-pneumatic spring, and particularly for a vehicle with a high center of gravity, the roll stiffness needs to be increased, so that the roll stiffness of the suspension can meet the requirement by adding a stabilizer bar mechanism. However, due to the limitation of space and structural strength, the stabilizer bar has a limited roll stiffness that can be increased, and cannot meet the roll stiffness requirement of the vehicle.
Disclosure of Invention
In view of the above, the invention provides a gas-spring interconnected suspension system and a vehicle with the same.
In order to solve the technical problems, the invention adopts the following technical scheme:
according to an embodiment of the first aspect of the present invention, a gas-spring interconnected suspension system includes: an interconnected suspension system, said interconnected suspension system comprising:
a first accumulator and a second accumulator;
a cylinder, the cylinder comprising: the front left side oil cylinder, the front right side oil cylinder, the rear left side oil cylinder and the rear right side oil cylinder are all provided with an upper cavity and a lower cavity which are separated by a piston;
the first oil way is communicated with the upper cavity of the front left side oil cylinder, the lower cavity of the front right side oil cylinder, the upper cavity of the rear left side oil cylinder, the lower cavity of the rear right side oil cylinder and the first energy accumulator; and
and the second oil path is communicated with the lower cavity of the front left side oil cylinder, the upper cavity of the front right side oil cylinder, the lower cavity of the rear left side oil cylinder, the upper cavity of the rear right side oil cylinder and the second energy accumulator.
In some embodiments, the gas-spring interconnected suspension system comprises: and the oil-gas spring system comprises a third oil way, and an oil-gas spring, an electromagnetic valve, a third energy accumulator and an electromagnetic valve which are respectively communicated with the third oil way.
In some embodiments, the stiffness of the gas spring in the gas spring system is positively correlated to the loading mass.
In some embodiments, the gas-spring interconnected suspension system comprises: and the interconnected suspension system and/or the oil-gas spring system are connected with the swing arm.
In some embodiments, the swing arm comprises: an upper swing arm and a lower swing arm which are arranged at intervals.
In some embodiments, the material of the swing arm comprises a titanium alloy material.
In some embodiments, the gas-spring interconnected suspension system comprises: and the control valve is respectively communicated with the first oil way and the second oil way and is used for respectively controlling the flow direction of fluid in the first oil way or the second oil way.
A vehicle according to an embodiment of the second aspect of the invention includes: a frame; a wheel; and the gas-spring interconnected suspension system of the embodiment of the first aspect, wherein the gas-spring interconnected suspension system is connected with the frame and the wheel.
In some embodiments, the pressure difference in the first oil passage and the second oil passage is different when the vehicle is in an inclined state.
In some embodiments, the roll stiffness of the rams in the gas spring interconnected suspension system is positively correlated to the roll angle of the vehicle.
The technical scheme of the invention has the following beneficial effects:
in the oil-gas spring interconnected suspension system of the embodiment of the invention, in the working condition of tilting motion, the interconnected suspension system is communicated with the upper cavity of the front left oil cylinder, the lower cavity of the front right oil cylinder, the upper cavity of the rear left oil cylinder, the lower cavity of the rear right oil cylinder and the first energy accumulator through a first oil path; and the second oil path is communicated with the lower cavity of the front left side oil cylinder, the upper cavity of the front right side oil cylinder, the lower cavity of the rear left side oil cylinder, the upper cavity of the rear right side oil cylinder and the second energy accumulator, so that the inclination rigidity is adjusted, and the requirement for meeting the roll rigidity is effectively met. Therefore, the technical scheme of the embodiment of the invention can control the stability and the smoothness of the gas-spring interconnected suspension system, improve the tire grip, improve the vehicle trafficability and improve the average cross-country vehicle speed.
Drawings
FIG. 1 is a schematic diagram of an interconnected suspension system according to one embodiment of the present invention in a leaning condition;
FIG. 2 is a schematic diagram of an interconnected suspension system according to an embodiment of the present invention in a pitch condition;
FIG. 3 is a schematic diagram of an interconnected suspension system according to an embodiment of the present invention in a vertical position;
FIG. 4 is a schematic structural diagram of an interconnected suspension system in a torsional mode according to an embodiment of the present invention;
FIG. 5 is a schematic view of a portion of a hydro-pneumatic interconnected suspension system in accordance with an embodiment of the present invention in connection with a vehicle frame and a wheel;
FIG. 6 is a schematic structural diagram of an interconnected suspension system in accordance with an embodiment of the present invention;
FIG. 7 is a schematic diagram of a gas spring system according to an embodiment of the present invention;
FIG. 8 is a graph of stiffness of a gas spring in a gas spring system versus load mass in accordance with an embodiment of the present invention;
FIG. 9 is a graph of oil versus tilt angle for an interconnected suspension system in accordance with an embodiment of the present invention.
Reference numerals
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the drawings of the embodiments of the present invention. It is to be understood that the embodiments described are only a few embodiments of the present invention, and not all embodiments. All other embodiments, which can be derived by a person skilled in the art from the described embodiments of the invention, are within the scope of the invention.
First, a gas-spring interconnected suspension system according to an embodiment of the present invention will be described in detail with reference to the accompanying drawings.
Specifically, the gas spring interconnected suspension system includes: an interconnected suspension system, said interconnected suspension system comprising: first accumulator 21, second accumulator 22, cylinder 10, first oil passage 32, and second oil passage 31, wherein cylinder 10 includes: the hydraulic cylinder assembly comprises a front left side oil cylinder 11, a front right side oil cylinder 12, a rear left side oil cylinder 13 and a rear right side oil cylinder 14, wherein the front left side oil cylinder 11, the front right side oil cylinder 12, the rear left side oil cylinder 13 and the rear right side oil cylinder 14 are respectively provided with an upper cavity and a lower cavity which are separated by a piston 15; the first oil passage 32 communicates the upper chamber 111 of the front left cylinder, the lower chamber 122 of the front right cylinder, the upper chamber 131 of the rear left cylinder, the lower chamber 142 of the rear right cylinder, and the first accumulator 21; the second oil path 31 communicates the lower chamber 112 of the front left cylinder, the upper chamber 121 of the front right cylinder, the lower chamber 132 of the rear left cylinder, the upper chamber 141 of the rear right cylinder, and the second accumulator 22.
As shown in fig. 1, in the roll motion condition, the cylinder pistons 15 on the left and right sides of the interconnected suspension system move, resulting in different oil pressures in the second oil passage 31 and the first oil passage 32, and the pressure difference between the two oil passages acts on the pistons 15 to prevent the vehicle body from rolling. The straight arrows in fig. 1 and 2 are directed to the flow direction of fluid such as hydraulic oil in the respective oil passages, wherein the implementing arrows correspond to the flow direction of fluid in the first oil passage 32, and the broken arrows correspond to the flow direction of fluid in the second oil passage 31. The hollow arrows point in the direction of movement of the piston 15 rod in the respective cylinder.
Therefore, in the working condition of the tilting movement, the interconnected suspension system communicates the upper cavity of the front left cylinder 11, the lower cavity of the front right cylinder 12, the upper cavity of the rear left cylinder 13, the lower cavity of the rear right cylinder 14 and the first accumulator 21 through the first oil path 32; and the second oil path 31 is communicated with the lower cavity of the front left side oil cylinder 11, the upper cavity of the front right side oil cylinder 12, the lower cavity of the rear left side oil cylinder 13, the upper cavity of the rear right side oil cylinder 14 and the second energy accumulator 22, so that the inclination rigidity is adjusted, and the requirement for meeting the roll rigidity is effectively met. Therefore, the technical scheme of the embodiment of the invention can control the stability and the smoothness of the gas-spring interconnected suspension system, improve the tire grip, improve the vehicle trafficability and improve the average cross-country vehicle speed.
Furthermore, as shown in fig. 2, in the pitching operation, when the front and rear cylinder pistons 15 of the interconnected suspension system move, the oil pressure in the oil path does not change, so that no additional anti-pitching moment is generated.
As shown in fig. 3, in the vertical movement condition, only a small amount of hydraulic oil flows into and out of the accumulator 20 (referred to as the first accumulator 21 and the second accumulator 22) due to the rod of the piston 15, and the flow rate is small, so that the vertical rigidity is not affected.
As shown in fig. 4, in the torsional motion condition, the oil pressure in the interconnected suspension system is not changed, so that no additional torque is generated, the vehicle passing ability is increased, the torsional moment applied to the vehicle body and the vehicle frame 400 is reduced, and the service life of the vehicle is prolonged.
In some embodiments, the gas-spring interconnected suspension system comprises: the oil-gas spring system 200, the oil-gas spring system 200 includes a third oil path, and an oil-gas spring, a solenoid valve 210, a third accumulator 250 and a solenoid valve 210 respectively communicated with the third oil path.
Further, the gas spring system 200 further includes a display screen, a controller, and a power unit 220. The power unit 220 drives a fluid such as hydraulic oil to flow through the third oil passage, and adjusts the pressure of the oil-gas spring.
In some embodiments, the stiffness of the gas spring in the gas spring system 200 is positively correlated to the loading mass.
The gas spring 240 is a variable rate spring. As shown in fig. 8, the abscissa represents the loaded mass, and the ordinate represents the spring rate (also referred to as stiffness). The spring rate may be increased with the loaded mass of the vehicle, allowing the vehicle to have optimal ride comfort at any loaded mass.
In some embodiments, as shown in fig. 5, the gas spring interconnected suspension system comprises: a swing arm to which the interconnected suspension system and/or the gas spring system 200 is connected.
The swing arm has support and guide effect, can further guarantee driving stability.
In some embodiments, the swing arm comprises: an upper swing arm 310 and a lower swing arm 320 are arranged at intervals.
As shown in FIG. 5, the two swing arms make the hydro-pneumatic spring interconnected suspension system of the invention be a double-cross arm type, which is beneficial to further improving the stability and the smoothness of driving.
In some embodiments, the material of the swing arm comprises a titanium alloy material.
The use of the light titanium alloy material is beneficial to reducing the dead weight of the vehicle and reducing the energy consumption.
In some embodiments, the gas-spring interconnected suspension system comprises: and control valves respectively communicating with the first oil passage 32 and the second oil passage 31, and respectively controlling a flow direction of fluid in the first oil passage 32 or the second oil passage 31.
As shown in fig. 1 to 4, the control valve can realize that the fluid in the same oil path has different flow directions, thereby enriching the control scheme for adjusting the rigidity.
In a specific example, the double-wishbone type oil-gas spring interconnected suspension system is composed of an oil-gas spring system 200, an interconnected suspension system, an upper swing arm 320, a lower swing arm 320, an upper buffer block and a lower buffer block. As shown in fig. 7, the hydro-pneumatic spring system is composed of a display screen, a controller, an adjustable damping valve 260, an electromagnetic valve 210, a pipeline 230, a third accumulator 250, a power unit 220, a pipeline and other components. The gas spring 240 is a variable rate spring, as shown in the following figures: the spring stiffness can be increased along with the loading mass of the vehicle, so that the vehicle has optimal smoothness under any loading mass, but the controllability of the suspension is not ideal, and the roll stiffness generated by the gas spring is small because the spring stiffness is small when the vehicle is unloaded, so that the roll of the vehicle is large. As shown in fig. 6, the interconnected suspension system is composed of an actuator, an accumulator, a damping valve 50, an oil filling valve 40, a hydraulic pipeline 30, a clamp and the like, and usually adopts a left-right interconnection and front-rear communication mode. The body of the upper and lower swing arms 320 assembly can be made of lightweight titanium alloy material, and the swing arms are connected with the frame 400 and the steering knuckle through ball hinges. The upper and lower buffer block assemblies can be screwed on the buffer block bracket to play a role in limiting the stroke of the suspension. According to the technical scheme, the oil-gas spring and the interconnected suspension are organically fused, the oil-gas spring system 200 and the interconnected suspension system are adopted in the system, advantages and disadvantages are complementary, and the suspension system is more superior than a traditional suspension system. Moreover, the technical scheme of this example can effectual improvement suspension system's operating stability and ride comfort, improves tire grip, improves the vehicle trafficability characteristic, improves average cross-country vehicle speed. Meanwhile, the torque borne by the frame 400 can be reduced, the service life of the frame 400 can be prolonged, and the abrasion of tires can be reduced.
An embodiment of the present invention further provides a vehicle, including the vehicle, including: a frame 400; a wheel 500; and the gas-spring interconnected suspension system of any one of the above embodiments, which connects the frame 400 and the wheel 500.
Since the gas-spring interconnected suspension system according to the above embodiment of the present invention has the above technical effects, the vehicle according to the embodiment of the present invention also has corresponding technical effects, that is, in a tilting motion condition, the interconnected suspension system communicates the upper chamber of the front left cylinder 11, the lower chamber of the front right cylinder 12, the upper chamber of the rear left cylinder 13, the lower chamber of the rear right cylinder 14, and the first accumulator 21 through the first oil path 32; and the second oil path 31 is communicated with the lower cavity of the front left side oil cylinder 11, the upper cavity of the front right side oil cylinder 12, the lower cavity of the rear left side oil cylinder 13, the upper cavity of the rear right side oil cylinder 14 and the second energy accumulator 22, so that the inclination rigidity is adjusted, and the requirement for meeting the roll rigidity is effectively met. Therefore, the technical scheme of the embodiment of the invention can control the stability and the smoothness of the gas-spring interconnected suspension system, improve the tire grip, improve the vehicle trafficability and improve the average cross-country vehicle speed.
In some embodiments, the pressure difference in the first oil passage 32 and the second oil passage 31 is different when the vehicle is in an inclined state.
As shown in fig. 1, the cylinder pistons 15 on the left and right sides of the hydraulically interconnected suspension move, resulting in a difference in oil pressure between the second oil passage 31 and the first oil passage 32, and a pressure difference between the two oil passages acts on the pistons 15 to prevent the vehicle body from rolling.
In some embodiments, the roll stiffness of the rams in the gas spring interconnected suspension system is positively correlated to the roll angle of the vehicle.
As shown in fig. 9, the abscissa represents the tilt angle, and the ordinate represents the tilt moment. The roll stiffness provided by the oil cylinders of the interconnected suspension system is nonlinear roll stiffness, the roll stiffness characteristic can be smaller when the roll angle is small, the smoothness can be improved, the average cross-country vehicle speed can be increased, and when the roll angle of the side body is increased, the roll stiffness is rapidly increased and the roll angle is reduced.
Other structures and operations of the suspension and the vehicle according to the embodiment of the present invention will be understood and readily implemented by those skilled in the art, and thus will not be described in detail.
Unless defined otherwise, technical or scientific terms used herein shall have the ordinary meaning as understood by one of ordinary skill in the art to which this invention belongs. The use of "first," "second," and similar terms in the present application do not denote any order, quantity, or importance, but rather the terms are used to distinguish one element from another. The terms "connected" or "coupled" and the like are not restricted to physical or mechanical connections, but may include electrical connections, whether direct or indirect. "upper", "lower", "left", "right", and the like are used merely to indicate relative positional relationships, and when the absolute position of the object being described is changed, the relative positional relationships are changed accordingly.
While the foregoing is directed to the preferred embodiment of the present invention, it will be understood by those skilled in the art that various changes and modifications may be made without departing from the spirit and scope of the invention as defined in the appended claims.
Claims (10)
1. A gas-spring interconnected suspension system, comprising: an interconnected suspension system, said interconnected suspension system comprising:
a first accumulator and a second accumulator;
a cylinder, the cylinder comprising: the front left side oil cylinder, the front right side oil cylinder, the rear left side oil cylinder and the rear right side oil cylinder are all provided with an upper cavity and a lower cavity which are separated by a piston;
the first oil way is communicated with the upper cavity of the front left side oil cylinder, the lower cavity of the front right side oil cylinder, the upper cavity of the rear left side oil cylinder, the lower cavity of the rear right side oil cylinder and the first energy accumulator; and
and the second oil path is communicated with the lower cavity of the front left side oil cylinder, the upper cavity of the front right side oil cylinder, the lower cavity of the rear left side oil cylinder, the upper cavity of the rear right side oil cylinder and the second energy accumulator.
2. The gas-spring interconnected suspension system of claim 1, comprising: and the oil-gas spring system comprises a third oil way, and an oil-gas spring, an electromagnetic valve, a third energy accumulator and an electromagnetic valve which are respectively communicated with the third oil way.
3. The gas-spring interconnected suspension system of claim 2, wherein the stiffness of the gas spring in the gas-spring system is positively correlated to the load mass.
4. The gas-spring interconnected suspension system of claim 2, comprising: and the interconnected suspension system and/or the oil-gas spring system are connected with the swing arm.
5. The gas spring interconnected suspension system of claim 4, wherein said swing arm comprises: an upper swing arm and a lower swing arm which are arranged at intervals.
6. The air-spring interconnected suspension system of claim 4 or 5, wherein the material of the swing arm comprises a titanium alloy material.
7. The gas-spring interconnected suspension system of claim 1, comprising: and the control valve is respectively communicated with the first oil way and the second oil way and is used for respectively controlling the flow direction of fluid in the first oil way or the second oil way.
8. A vehicle, characterized in that the vehicle comprises:
a frame;
a wheel; and
the hydro-pneumatic interconnected suspension system of any one of claims 1 to 7, connecting said frame and said wheel.
9. The vehicle according to claim 8, characterized in that the pressure difference in the first oil passage and the second oil passage is different when the vehicle is in an inclined state.
10. The vehicle of claim 8, wherein the roll stiffness of the rams in the hydro-pneumatic interconnected suspension system is positively correlated to the roll angle of the vehicle.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111180416.2A CN113895198A (en) | 2021-10-11 | 2021-10-11 | Gas spring interconnected suspension system and vehicle with same |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202111180416.2A CN113895198A (en) | 2021-10-11 | 2021-10-11 | Gas spring interconnected suspension system and vehicle with same |
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| CN113895198A true CN113895198A (en) | 2022-01-07 |
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| Application Number | Title | Priority Date | Filing Date |
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| CN202111180416.2A Pending CN113895198A (en) | 2021-10-11 | 2021-10-11 | Gas spring interconnected suspension system and vehicle with same |
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Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040245732A1 (en) * | 2001-09-28 | 2004-12-09 | Marcus Kotulla | Vehicle suspension system |
| CN108749506A (en) * | 2018-07-04 | 2018-11-06 | 湖南工学院 | A kind of interconnection type variable volume air suspension and its control method |
| CN109501544A (en) * | 2018-10-31 | 2019-03-22 | 江苏大学 | A kind of air suspension and the vehicle for installing the suspension |
| CN109501545A (en) * | 2018-10-31 | 2019-03-22 | 江苏大学 | A kind of air suspension and the vehicle and method for installing the suspension |
| CN110065355A (en) * | 2019-04-19 | 2019-07-30 | 北京航天发射技术研究所 | The hydro-pneumatic suspension system and its optimum design method of multi-axle heavy type vehicle |
| CN111391602A (en) * | 2020-04-26 | 2020-07-10 | 常州万安汽车部件科技有限公司 | Passenger car suspension system |
| CN112572087A (en) * | 2020-12-30 | 2021-03-30 | 常州万安汽车部件科技有限公司 | Electromagnetic balance type vehicle hydraulic suspension system and control method thereof |
| CN214057159U (en) * | 2020-12-30 | 2021-08-27 | 常州万安汽车部件科技有限公司 | Electromagnetic balance type vehicle hydraulic suspension system |
-
2021
- 2021-10-11 CN CN202111180416.2A patent/CN113895198A/en active Pending
Patent Citations (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20040245732A1 (en) * | 2001-09-28 | 2004-12-09 | Marcus Kotulla | Vehicle suspension system |
| CN108749506A (en) * | 2018-07-04 | 2018-11-06 | 湖南工学院 | A kind of interconnection type variable volume air suspension and its control method |
| CN109501544A (en) * | 2018-10-31 | 2019-03-22 | 江苏大学 | A kind of air suspension and the vehicle for installing the suspension |
| CN109501545A (en) * | 2018-10-31 | 2019-03-22 | 江苏大学 | A kind of air suspension and the vehicle and method for installing the suspension |
| CN110065355A (en) * | 2019-04-19 | 2019-07-30 | 北京航天发射技术研究所 | The hydro-pneumatic suspension system and its optimum design method of multi-axle heavy type vehicle |
| CN111391602A (en) * | 2020-04-26 | 2020-07-10 | 常州万安汽车部件科技有限公司 | Passenger car suspension system |
| CN112572087A (en) * | 2020-12-30 | 2021-03-30 | 常州万安汽车部件科技有限公司 | Electromagnetic balance type vehicle hydraulic suspension system and control method thereof |
| CN214057159U (en) * | 2020-12-30 | 2021-08-27 | 常州万安汽车部件科技有限公司 | Electromagnetic balance type vehicle hydraulic suspension system |
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