Front oil-gas suspension assembly and vehicle

Abstract

The present invention relates to the field of vehicle technology, and in particular to a front oil-gas suspension assembly and a vehicle. The front oil-gas suspension assembly includes an oil-gas spring and a lower swing arm. The oil-gas spring is arranged on the outside of the vehicle frame. The two ends of the oil-gas spring are respectively hinged to the vehicle frame and the axle. At least two oil-gas springs are symmetrically arranged relative to the vehicle frame, and the top of the oil-gas spring is inclined toward the inside of the vehicle frame. The lower swing arm is respectively hinged to the vehicle frame and the oil-gas spring, and the line connecting the three hinge points of the lower swing arm forms a right triangle. The top of the oil-gas spring is inclined toward the inside of the vehicle frame, and the line connecting the centers of the three hinge parts of the lower swing arm forms a right triangle. After the force on each hinge point is decomposed along the transverse arm, the front suspension is only subjected to the force in the up-down direction. Therefore, the lower swing arm structure can make the hinge point at the axle end swing up and down around the two hinge points of the frame without causing deviation in the front-back direction. Therefore, the oil-gas spring mainly bears the vertical force, which can effectively prevent the piston rod of the oil-gas spring from breaking.

Description

Technical Field

[0001] The present invention relates to the technical field of vehicles, and in particular to a front oil-gas suspension assembly and a vehicle. Background Art

[0002] The suspension is a connecting device between the frame and axle of a vehicle such as a car. The suspension is used to transmit the force and torque acting between the axle and the frame, and to cushion the impact force transmitted to the frame by uneven road surfaces and reduce the vibration caused thereby to ensure that the car can run smoothly.

[0003] Currently, a commonly used suspension is the hydro-pneumatic suspension. With its variable stiffness and small longitudinal dimensions, it's often used in vehicles operating in harsh environments like mining sites and deserts. It reduces vehicle vibration, increases component life, and improves the driver experience. The hydro-pneumatic suspension consists of a hydro-pneumatic spring, longitudinal thrust rods, and transverse thrust rods positioned between the vehicle frame and axle. The hydro-pneumatic springs are hinged to the frame and axle at both ends, providing damping force and mitigating vehicle vibrations. The longitudinal thrust rods and transverse thrust rods are arranged longitudinally and transversely along the frame, connecting the frame and axle, respectively, and transmitting longitudinal and transverse forces between the two.

[0004] However, when the vehicle bounces, the gas spring is subjected to greater force, bearing both axial force and lateral force, which can easily cause the gas spring piston rod to break, reducing the safety and reliability of the gas suspension.

[0005] Therefore, a front oil-gas suspension assembly is urgently needed to solve the above technical problems. Summary of the Invention

[0006] The purpose of the present invention is to provide a front oil-gas suspension assembly that can prevent the oil-gas spring piston rod from breaking.

[0007] To achieve this object, the present invention adopts the following technical solutions:

[0008] A front oil-gas suspension assembly is provided, which is used to connect a vehicle frame and an axle located below the vehicle frame, comprising:

[0009] a gas spring disposed on the outside of the vehicle frame, with both ends of the gas spring being hinged to the vehicle frame and the axle respectively, at least two gas springs being symmetrically disposed relative to the vehicle frame, and with the top ends of the gas springs tilted toward the inside of the vehicle frame;

[0010] The lower swing arm is hinged to the vehicle frame and the oil-gas spring respectively, and the connecting line of the two hinge points of the lower swing arm and the vehicle frame and the connecting line of the lower swing arm and one hinge point of the oil-gas spring forms a right triangle.

[0011] As an optimal technical solution for the above-mentioned front oil-gas suspension assembly, the oil-gas spring includes a cylinder and a piston rod, one end of the piston rod extends into the lower end of the cylinder and can move inside the cylinder, the upper end of the cylinder is rotatably connected to the frame, and the other end of the piston rod is interference fit connected to the axle.

[0012] As an optimal technical solution for the above-mentioned front oil-gas suspension assembly, the cylinder is connected to the frame through a joint bearing, the other end of the piston rod is a conical structure, a conical hole is provided on the axle, the other end of the piston rod passes through the conical hole, and a limiting portion is fixedly provided on the part of the other end of the piston rod passing through the conical hole, the limiting portion abuts against the axle, and the other end of the piston rod is also hinged to the lower control arm.

[0013] As a preferred technical solution of the above-mentioned front oil-gas suspension assembly, the central axis of the oil-gas spring is arranged parallel to a plane perpendicular to the forward direction of the frame.

[0014] As a preferred technical solution of the above-mentioned front oil-gas suspension assembly, the frame includes two longitudinal beams arranged in a centrally symmetrical manner, and the distance from the connection between the lower control arm and the frame to the central axis between the two longitudinal beams is less than a preset distance.

[0015] As a preferred technical solution of the above-mentioned front oil-gas suspension assembly, the line segment connecting the two hinge points connecting the axle and the frame is parallel to the central axis between the two longitudinal beams, and the line segment and the central axis are at the same height from the same horizontal plane.

[0016] As an optimal technical solution for the above-mentioned front oil-gas suspension assembly, the lower control arm includes a transverse arm, an oblique arm and an oblique rib, the first end of the oblique arm is connected to the first end of the transverse arm, and a first hinge hole is provided at the connection between the oblique arm and the transverse arm, the second end of the oblique arm is provided with a second hinge hole, and the second end of the transverse arm is provided with a third hinge hole, the oblique rib is respectively connected to the oblique arm and the transverse arm, the transverse arm, the oblique arm and the oblique rib form an A-type structure, and the line connecting the center point of the first hinge hole, the center point of the second hinge hole and the center point of the third hinge hole forms a right triangle.

[0017] As a preferred technical solution of the above-mentioned front oil-gas suspension assembly, the line connecting the center points of the first hinge hole, the second hinge hole and the third hinge hole forms an isosceles right triangle.

[0018] A second object of the present invention is to provide a vehicle that can protect the oil and gas springs and improve the stability and safety of the vehicle.

[0019] A vehicle is provided, comprising the front oil-gas suspension assembly described above.

[0020] Beneficial effects of the present invention:

[0021] In the front hydro-pneumatic suspension provided by the present invention, the hydro-pneumatic spring primarily bears vertical forces. Because the hydro-pneumatic spring is simple to load, it primarily serves as a shock absorber and steering kingpin. Lateral and longitudinal forces are primarily borne by the lower control arm located below the hydro-pneumatic spring. The lines connecting the two hinge points of the lower control arm with the vehicle frame and one hinge point of the lower control arm with the hydro-pneumatic spring form a right triangle. Because triangles offer optimal stability, the triangle formed by the lines connecting the centers of the three hinged portions of the lower control arm improves the strength and rigidity of the lower control arm, reducing its manufacturing cost. Furthermore, because the triangle is a right triangle, the forces acting at each hinge point are decomposed along the transverse arm, eliminating the fore-aft forces acting on the front suspension and only the up-and-down forces. Therefore, the lower control arm structure allows the hinge point at the axle end to swing up and down around the two hinge points on the frame without causing fore-and-aft deviation. Therefore, the hydro-pneumatic spring primarily bears vertical forces, effectively preventing breakage of the hydro-pneumatic spring's piston rod and improving the safety and reliability of the hydro-pneumatic suspension. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 is a front view of a portion of the structure of a vehicle provided by an embodiment of the present invention;

[0023] Figure 2 is a side view of a portion of the structure of a vehicle provided by an embodiment of the present invention;

[0024] Figure 3 is an axonometric view of a portion of the structure of a vehicle provided by an embodiment of the present invention;

[0025] Figure 4 1 is a schematic structural diagram of a front oil-gas suspension assembly provided by an embodiment of the present invention;

[0026] Figure 5 This is a schematic structural diagram of a lower swing arm provided by an embodiment of the present invention from one perspective;

[0027] Figure 6 It is a structural schematic diagram of the lower swing arm provided by an embodiment of the present invention from another perspective.

[0028] Figure 7 is an exploded schematic diagram of a lower swing arm provided by an embodiment of the present invention;

[0029] In the picture:

[0030] 1. Oil and gas spring; 11. Cylinder; 12. Piston rod;

[0031] 2. Lower arm; 21. Cross arm; 22. Oblique arm; 23. Oblique rib; 24. First hinge hole; 25. Second hinge hole; 26. Third hinge hole; 27. Spherical bearing; 28. Flange; 29. ​​Bolt; 210. Circlip;

[0032] 100, frame; 101, longitudinal beam; 102, protection beam;

[0033] 200. Axle. DETAILED DESCRIPTION

[0034] The present invention will be further described in detail below with reference to the accompanying drawings and examples. It will be understood that the specific embodiments described herein are intended only to illustrate the present invention and are not intended to limit the present invention. It should also be noted that, for ease of description, the accompanying drawings only illustrate portions relevant to the present invention, not all structures.

[0035] In the description of the present invention, unless otherwise expressly specified or limited, the terms "connected," "connected," and "fixed" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integration; mechanical connections or electrical connections; right-angle connections or indirect connections through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention in specific circumstances.

[0036] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0037] In the description of this embodiment, the terms "upper," "lower," "right," and other orientations or positional relationships are based on the orientations or positional relationships shown in the accompanying drawings and are intended solely for ease of description and simplified operation. They do not indicate or imply that the devices or components referred to must have, be constructed, or operate in a specific orientation. Therefore, they should not be construed as limitations on the present invention. Furthermore, the terms "first" and "second" are used solely for descriptive purposes and have no special meanings.

[0038] Aiming at the problem that the piston rod of the oil-gas spring in the prior art is easy to break, the present invention provides a vehicle, such as Figure 1 、 Figure 2 and Figure 3 As shown, the vehicle includes a steering structure, a frame 100, an axle 200, and a front hydro-pneumatic suspension assembly. The front hydro-pneumatic suspension assembly connects the frame 100 to the axle 200 located below the frame 100. The frame 100 includes a protective beam 102 and two longitudinal beams 101 symmetrically arranged about the widthwise central axis of the protective beam 102. The protective beam 102 is connected to the longitudinal beams 101 at both ends, i.e., the protective beam 102 is located between the two longitudinal beams 101. The axle 200 is a disconnectable front axle and is also provided with a connecting seat for the steering structure to rotate and connect.

[0039] Optionally, in an embodiment of the present invention, the steering structure includes a steering tie rod arm, a steering tie rod, and a steering cylinder. The vehicle frame 100 includes a protective beam 102, the steering tie rod arm is disposed on one side of the protective beam 102, and a connecting seat is disposed on the axle 200. The ends of the steering cylinder are respectively hingedly connected to the connecting seat and the protective beam 102, and the ends of the steering tie rod are respectively hingedly connected to the connecting seat and the steering tie rod arm. The steering structure can steer the axle 200 as needed by placing the steering cylinder behind the axle 200, thereby ensuring that the vehicle's forward direction can be selected as needed.

[0040] like Figure 4-7 As shown, the front oil-gas suspension assembly includes an oil-gas spring 1 and a lower control arm 2. The oil-gas spring 1 is arranged on the outside of the frame 100. The two ends of the oil-gas spring 1 are respectively hinged to the frame 100 and the axle 200. The oil-gas spring 1 is symmetrically arranged relative to the frame 100, and the top of the oil-gas spring 1 is inclined toward the inside of the frame 100; the lower control arm 2 is respectively hinged to the frame 100 and the oil-gas spring 1, and the line connecting the two hinge points of the lower control arm 2 and the frame 100 and one hinge point of the lower control arm 2 and the oil-gas spring 1 forms a right triangle.

[0041] The top of the gas spring 1 is tilted inwardly toward the vehicle frame 100, so it primarily bears vertical forces. Because the force response of the gas spring 1 is simple, it primarily serves as a shock absorber and kingpin. Lateral and longitudinal forces are primarily borne by the lower arm 2 located below the gas spring 1.

[0042] The top of the gas spring 1 tilts inward toward the vehicle frame 100, and the line connecting the three hinge points of the lower control arm 2 forms a right triangle. Lateral and longitudinal forces are primarily borne by the left and right lower control arms 2. Because the triangle is a right triangle, the forces acting at each hinge point are decomposed along the transverse arms. The front suspension is not subject to fore-aft forces, but only to up-and-down forces. Therefore, the lower control arm structure allows the hinge point at the axle end to swing up and down around the two hinge points of the vehicle frame 100 without fore-and-aft deviation, allowing the gas spring 1 to primarily bear vertical forces. Due to its simple force distribution, the gas spring 1 primarily serves as a shock absorber and steering kingpin. This effectively prevents breakage of the gas spring 1's piston rod, improving the safety and reliability of the gas suspension.

[0043] The bottom end of the oil-gas spring 1 passes through the axle 200 and is hinged to the lower control arm 2. Since the frame 100 includes two symmetrically arranged longitudinal beams 101, and an oil-gas spring 1 is provided on the outer side of the longitudinal beams 101, the number of oil-gas springs 1 is also two, and the number of lower control arms 2 is also two. The oil-gas springs 1 and the lower control arms 2 are symmetrically arranged relative to the symmetry axis of the two longitudinal beams 101.

[0044] Optionally, in an embodiment of the present invention, continue to refer to Figure 1 and Figure 2 The gas spring 1 includes a cylinder 11 and a piston rod 12. One end of the piston rod 12 extends into the lower end of the cylinder 11 and can move inside the cylinder 11. The upper end of the cylinder 11 is rotatably connected to the vehicle frame 100, so that the gas spring 1 can rotate freely and is easy to assemble; the other end of the piston rod 12 is interference fit connected to the axle 200, which can eliminate the assembly gap between the gas spring 1 and the axle 200 and prevent the piston rod 12 of the gas spring 1 from positional deviation and affecting the overall steering accuracy of the vehicle. Specifically, in an embodiment of the present invention, the cylinder 11 is connected to the vehicle frame 100 via a spherical bearing 27. The other end of the piston rod 12 is a tapered structure. The axle 200 is provided with a tapered hole. The tapered structure extends into the tapered hole, and the other end of the piston rod 12 extends out of the tapered hole. The other end of the piston rod 12 is fixedly provided with a limit portion, which abuts the axle 200. The other end of the piston rod 12 is also hinged (i.e., pivotally connected) to the lower arm 2. It should be noted that the portion of the piston rod 12 hinged to the lower arm 2 is located below the limit portion. After extending out of the axle 200, this portion is hinged to the lower arm 2. Optionally, in this embodiment, the limit portion can be a positioning flange, which is provided above the lower arm 2. The positioning flange abuts the axle 200, stabilizes the connection between the piston rod 12 and the axle 200, and prevents the piston rod 12 from detaching from the axle 200. The first end of the piston rod 12 extends out of the limiting portion and is hinged to the lower swing arm 2 , so that the other end of the piston rod 12 is connected to the axle 200 and the lower swing arm 2 in sequence.

[0045] To ensure that the axle 200 only experiences lateral displacement during vertical adjustment, in this embodiment of the present invention, the central axis of the gas spring 1 is arranged parallel to a plane perpendicular to the forward direction of the vehicle frame 100. Preferably, the line segment connecting the two hinge points where the gas spring 1 connects to the axle 200 and the frame 100, respectively, is parallel to the central axis between the two longitudinal beams 101, and the line segment and the central axis are at the same height from the same horizontal plane. This further reduces displacement of the axle 200 in directions other than lateral during vertical adjustment.

[0046] To ensure stable vehicle operation, the frame 100 includes two longitudinal beams 101 arranged symmetrically about the center of the vehicle. The distance between the connection between the lower control arm 2 and the frame 100 and the central axis between the two longitudinal beams 101 is less than a predetermined distance. This predetermined distance is not specifically defined in the embodiments of the present invention and is determined based on the vehicle type and the width of the frame 100. This arrangement allows the hinged connection between the lower control arm 2 and the frame 100 to be located closer to the center of the frame 100, making the lower control arm 2 longer and reducing the offset during vertical adjustment of the axle 200.

[0047] In an embodiment of the present invention, the structure of the lower swing arm 2 includes a transverse arm 21, an oblique arm 22 and an oblique rib 23. The first end of the oblique arm 22 is connected to the first end of the transverse arm 21, and a first hinge hole 24 is provided at the connection between the oblique arm 22 and the transverse arm 21. The second end of the oblique arm 22 is provided with a second hinge hole 25, and the second end of the transverse arm 21 is provided with a third hinge hole 26. The oblique rib 23 is respectively connected to the oblique arm 22 and the transverse arm 21. The transverse arm 21, the oblique arm 22 and the oblique rib 23 form an A-type structure, and the line connecting the center point of the first hinge hole 24, the center point of the second hinge hole 25 and the center point of the third hinge hole 26 forms a right triangle.

[0048] Since the line connecting the center point of the first hinge hole 24, the center point of the second hinge hole 25 and the center point of the third hinge hole 26 forms a right triangle, and since the triangle has the best stability, the triangle formed by the three hinge points of the lower control arm 2 can improve the strength and rigidity of the lower control arm 2 and reduce the manufacturing cost of the lower control arm 2. In addition, since the triangle is a right triangle, after the force on each hinge point is decomposed along the cross arm 21, the front suspension will not be subjected to the force in the front and rear directions, but only to the force in the up and down directions. Therefore, the structure of the lower control arm 2 can make the hinge point at the end of the axle 200 swing up and down around the two hinge points of the frame 100 without causing any offset in the front and rear directions.

[0049] Preferably, in an embodiment of the present invention, the lines connecting the center points of the first hinge hole 24, the second hinge hole 25, and the third hinge hole 26 form an isosceles right triangle. The lateral force and the decomposed longitudinal force acting on the lower swing arm 2 are transmitted to the oblique arm 22, resulting in the direction of the resultant force along the length of the oblique arm 22 substantially aligning with that of the oblique arm 22. No additional torque other than that along the length of the oblique arm 22 is generated between the first hinge hole 24 and the third hinge hole 26. This structure reduces the strength requirements for the lower swing arm 2, thereby reducing manufacturing costs.

[0050] Optionally, in an embodiment of the present invention, the central axes of the first hinge hole 24, the second hinge hole 25, and the third hinge hole 26 are not coplanar. In this case, the central axes of the first hinge hole 24, the second hinge hole 25, and the third hinge hole 26 are arranged at an angle. This arrangement can reduce the force acting on the first hinge hole 24 and effectively connect the lower arm 2 structure to the vehicle frame 100. The first hinge hole 24, the second hinge hole 25, and the third hinge hole 26 are arranged according to the shape and position of the vehicle frame 100.

[0051] Preferably, in order to allow the lower arm 2 to deform to a certain extent without failure after the vehicle frame 100 is subjected to vibration, in this embodiment, joint bearings 27 are provided in the first hinge hole 24, the second hinge hole 25, and the third hinge hole 26. The lower arm 2 can rotate to a certain extent according to the actual force applied to it, thereby offsetting the torque generated by the force.

[0052] A limit flange 28 is provided at one end of the first hinge hole 24, which abuts against the spherical plain bearing 27. The piston rod 12 of the gas spring 1 is mounted at the first hinge hole 24, with its axis pointing vertically downward. The spherical plain bearing 27 is compressed and installed by the limit flange 28, eliminating any installation clearance for the spherical plain bearing 27. Optionally, in this embodiment of the present invention, the limit flange 28 is fixed to the cross arm 21 via bolts 29. Bolts 29 are provided circumferentially around the first hinge hole 24 to secure the limit flange 28 to the cross arm 21.

[0053] Optionally, a retaining spring 210 is provided at both ends of the second hinge hole 25 and the third hinge hole 26 respectively. The retaining spring 210 can fix the joint bearing 27 provided in the first hinge hole 24 and the second hinge hole 25 to prevent the joint bearing 27 from falling off.

[0054] It should be noted that the second hinge hole 25 and the third hinge hole 26 are connected to the vehicle frame 100 through a pin and a spacer, and both ends of the second hinge hole 25 and the third hinge hole 26 are provided with a spacer.

[0055] The piston rod 12 of the gas spring 1 is mounted at the first hinge hole 24, with the axis pointing vertically downward. The spherical bearing 27 is compressed and installed via a limiting flange 28 to eliminate installation clearance. The second and third hinge holes 25, 26 are mounted on the support of the frame 100. The axis of the second hinge hole 25 is parallel to the center plane of the vehicle, while the axis of the third hinge hole 26 forms a certain angle (non-parallel) with the axis of the second hinge hole 25, so that the retaining spring 210 of the spherical bearing 27 at the second and third hinge holes 25, 26 is subjected to less force. The second and third hinge holes 25, 26 are mounted on the frame 100 via pins and spacers to provide axial positioning for the second and third hinge holes 25, 26.

[0056] Furthermore, the above are only preferred embodiments of the present invention and the technical principles employed. Those skilled in the art will appreciate that the present invention is not limited to the specific embodiments described herein, and that various obvious changes, readjustments, and substitutions are possible for those skilled in the art without departing from the scope of the present invention. Therefore, although the present invention has been described in detail through the above embodiments, the present invention is not limited to the above embodiments and may include many other equivalent embodiments without departing from the scope of the present invention. The scope of the present invention is determined by the scope of the appended claims.

Claims

1. A front oil-gas suspension assembly for connecting a vehicle frame (100) and an axle (200) located below the vehicle frame (100), characterized in that: include: An oil-gas spring (1) is arranged on the outside of the vehicle frame (100), with both ends of the oil-gas spring (1) being hinged to the vehicle frame (100) and the axle (200) respectively, at least two of the oil-gas springs (1) being symmetrically arranged relative to the vehicle frame (100), and the top ends of the oil-gas springs (1) being inclined toward the inside of the vehicle frame (100); A lower swing arm (2) is hinged to the vehicle frame (100) and the oil-gas spring (1), respectively, and a line connecting two hinge points of the lower swing arm (2) and the vehicle frame (100) and one hinge point of the lower swing arm (2) and the oil-gas spring (1) forms a right triangle; The lower swing arm (2) comprises a transverse arm (21), an oblique arm (22) and an oblique rib (23); a first end of the oblique arm (22) is connected to a first end of the transverse arm (21); a first hinge hole (24) is provided at the connection between the oblique arm (22) and the transverse arm (21); a second hinge hole (25) is provided at the second end of the oblique arm (22); a third hinge hole (26) is provided at the second end of the transverse arm (21); the oblique rib (23) is connected to the oblique arm (22) and the transverse arm (21) respectively; the transverse arm (21), the oblique arm (22) and the oblique rib (23) form an A-type structure; and a line connecting the center point of the first hinge hole (24), the center point of the second hinge hole (25) and the center point of the third hinge hole (26) forms a right triangle; The connecting line of the center point of the first hinge hole (24), the center point of the second hinge hole (25) and the center point of the third hinge hole (26) forms an isosceles right triangle; The oil-gas spring (1) comprises a cylinder (11) and a piston rod (12), one end of the piston rod (12) extends into the lower end of the cylinder (11) and is movable in the cylinder (11), the upper end of the cylinder (11) is rotatably connected to the vehicle frame (100), and the other end of the piston rod (12) is connected to the vehicle axle (200) by interference fit; The cylinder (11) is connected to the vehicle frame (100) via a joint bearing (27); the other end of the piston rod (12) is a conical structure; a conical hole is provided on the vehicle axle (200); the other end of the piston rod (12) passes through the conical hole; a limiting portion is fixedly provided on the portion of the other end of the piston rod (12) passing through the conical hole; the limiting portion abuts against the vehicle axle (200); and the other end of the piston rod (12) is also hinged to the lower swing arm (2).

2. The front oil-gas suspension assembly according to claim 1, characterized in that: The central axis of the oil-gas spring (1) is arranged parallel to a plane perpendicular to the forward direction of the vehicle frame (100).

3. The front oil-gas suspension assembly according to claim 1, characterized in that: The vehicle frame (100) comprises two longitudinal beams (101) arranged in a centrally symmetrical manner, and the distance between the connection point between the lower swing arm (2) and the vehicle frame (100) and the central axis between the two longitudinal beams (101) is less than a preset distance.

4. The front oil-gas suspension assembly according to claim 3, characterized in that: A line segment connecting the two hinge points connecting the axle (200) and the frame (100) is parallel to the central axis between the two longitudinal beams (101), and the line segment and the central axis are at the same height from the same horizontal plane.

5. A vehicle, characterized in that: The invention comprises a vehicle frame (100), a vehicle axle (200) and a front oil-gas suspension assembly as claimed in any one of claims 1 to 4.

6. The vehicle according to claim 5, characterized in that The vehicle also includes a steering structure, which includes a steering tie rod arm, a steering tie rod and a steering oil cylinder. The vehicle frame (100) includes a protection beam (102). The steering tie rod arm is arranged on one side of the protection beam (102). A connecting seat is provided on the vehicle axle (200). The two ends of the steering oil cylinder are respectively hingedly connected to the connecting seat and the protection beam (102). The two ends of the steering tie rod are respectively hingedly connected to the connecting seat and the steering tie rod arm.

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