CN116324210A

CN116324210A - Shock absorber

Info

Publication number: CN116324210A
Application number: CN202080105352.7A
Authority: CN
Inventors: 郭灵智; 赵俊锋; 张德超; 杨国华
Original assignee: Zhejiang Geely Holding Group Co Ltd; Zhejiang Geely Automobile Research Institute Co Ltd
Current assignee: Zhejiang Geely Holding Group Co Ltd; Zhejiang Geely Automobile Research Institute Co Ltd
Priority date: 2020-12-22
Filing date: 2020-12-22
Publication date: 2023-06-23
Also published as: WO2022133748A1

Abstract

A shock absorber, the shock absorber comprising: the cylinder barrel (10) is internally provided with a cavity; the piston rod is inserted into the cavity and comprises a rod body (21) and a piston ring (22), the piston ring (22) is arranged outside the rod body (21), the piston ring (22) abuts against the inner wall of the cylinder barrel (10), and the piston ring (22) divides the cavity into a first cavity (101) and a second cavity (102); and the two damping components are respectively arranged in the first chamber (101) and the second chamber (102), and are used for adjusting the flow rate of liquid in the chambers.

Description

Shock absorber

Technical Field

The invention relates to the field of vehicle structures, in particular to a shock absorber.

Background

In order to improve the running smoothness of the automobile, the shock absorber is arranged in parallel with the elastic element in the suspension, and most of the shock absorber adopted in the automobile suspension system is a hydraulic shock absorber for damping the shock, the cylinder type shock absorber is widely adopted in the automobile suspension system, and the shock absorbing effect is achieved in the compression and extension strokes of the suspension system.

The vehicle body is typically provided with shock absorbing springs and shock absorbers. The shock absorber is mainly used for inhibiting vibration and impact from a road surface when the shock absorbing spring rebounds after absorbing the shock. While the shock absorbing spring can filter the vibration of the road surface when passing over the uneven road surface, the shock absorbing spring itself can reciprocate, and the shock absorber is used for restraining the spring from jumping. The shock absorber is too soft, the automobile body will jump from top to bottom, and too hard of shock absorber will bring too big resistance, prevents the normal work of shock absorbing spring. The shock absorber is mainly used for protecting a host machine, an auxiliary machine, various power machines and instruments from vibration, and plays roles of reducing vibration and noise and preventing impact. The existing shock absorber has the problems of low horsepower, high noise, complex structure, poor shock absorption effect, complex installation and disassembly, short service life and the like due to the existence of self-vibration images, medium-frequency vibration transmission.

Therefore, the design of the shock absorber takes into account the adjustability of the damping. Realize the damping adjustment of the shock absorber, have very great control application value to the shock isolation system. In general, damping of a shock absorber is variable by using a special viscous liquid such as a magnetorheological fluid or an electrorheological fluid, and changing the viscous resistance by changing the viscosity.

The conventional common cylinder type shock absorber structure has the defects of smaller damping force adjusting range and limited adjusting capability. The magnetorheological damper responds to road conditions and driving environments in real time based on input information from monitoring vehicle bodies and wheel motion sensors by utilizing electromagnetic response, but the magnetorheological damper has the following defects when in use: when the electromagnetic coil is used, when the current amount in the electromagnetic coil is smaller, and a larger magnetic field cannot be generated to influence magnetorheological fluid, the damping effect of the damper is reduced, and under the condition of larger vibration, the electromagnetic coil cannot be damped through the damper, so that the vehicle jolts more, and the riding experience is influenced; in addition, when the shock absorber is used, dust can be stained on the outer side of the limiting pipe, so that a clamping phenomenon occurs in the shock absorbing process, and the shock absorber cannot be damped; when the shock absorber is placed, the shock absorber can be directly contacted with the ground, the shock absorber can be damaged, and the normal use of the shock absorber is affected; when the shock absorber works, the shock absorber can do reciprocating piston movement, larger heat can be generated, and the service life of the shock absorber is influenced; in addition, the outer surface of the working cylinder is not provided with a protective coating, so that the ageing resistance and the wear resistance of the working cylinder are relatively poor, and the service life of the working cylinder is shortened.

Therefore, it is necessary to provide a solution to the problems of small damping adjustable range and poor adjustability of the existing shock absorber, so as to improve the shock absorption performance of the shock absorber and the comfort of the vehicle running.

Disclosure of Invention

In order to solve the problems of small damping adjustable range and poor adjustability of the existing shock absorber, thereby improving the shock absorption performance of the shock absorber and the travelling comfort of a vehicle, the invention provides the shock absorber, and the shock absorber is realized by the following technical scheme.

The invention provides a shock absorber, comprising:

the cylinder barrel is internally provided with a cavity;

the piston rod is inserted into the cavity and comprises a rod body and a piston ring, the piston ring is arranged outside the rod body and abuts against the inner wall of the cylinder barrel, and the piston ring divides the cavity into a first cavity and a second cavity;

the two damping components are respectively arranged in the first cavity and the second cavity, and the damping components are used for adjusting the liquid flow rate in the cavities.

The invention provides a further improvement of the shock absorber, which is characterized in that the damping assembly comprises a hydraulic valve and a limiting table;

the limiting table is arranged outside the rod body, and a gap is arranged between the limiting table and the inner wall;

the hydraulic valve is arranged outside the rod body, the hydraulic valve is arranged on one side, far away from the piston ring, of the limiting table, and the side, far away from the piston ring, of the hydraulic valve is communicated with the side, far away from the rod body, of the hydraulic valve.

The invention provides a further improvement of a shock absorber, which is characterized in that a throttle hole and a diversion trench are arranged on the hydraulic valve, the throttle hole penetrates through the hydraulic valve along the axial direction of a rod body, the diversion trench is arranged on the side surface of the hydraulic valve, which is close to a piston ring, a first end of the diversion trench is communicated with the throttle hole, and a second end of the diversion trench penetrates through the edge of the hydraulic valve.

The invention provides a further improvement of the shock absorber, wherein the hydraulic valve and the limiting table are both disc-shaped.

The shock absorber provided by the invention is further improved in that a preset distance is arranged between the limiting table and the piston ring.

The shock absorber provided by the invention is further improved in that a sealing ring is arranged between the hydraulic valve and the inner wall, and the sealing ring is positioned on one side of the hydraulic valve away from the piston ring.

The invention provides a further improvement of a shock absorber, which is characterized in that the damping assembly further comprises a spring, the spring is sleeved outside the rod body, the spring is positioned on one side of the hydraulic valve, which is far away from the piston ring, and one end of the spring, which is far away from the piston ring, is abutted against the cylinder barrel.

The invention provides a further improvement of a shock absorber, which is characterized in that a cylinder barrel is provided with a first sealing cover, a second sealing cover and a cylinder body, the first sealing cover is arranged at a first end of the cylinder body, the second sealing cover is arranged at a second end of the cylinder body, and springs of two damping assemblies respectively abut against the first sealing cover and the second sealing cover.

The invention provides a further improvement of a shock absorber, which is characterized in that the cylinder body comprises an inner cylinder and an outer cylinder, the outer cylinder is sleeved outside the inner cylinder, the first sealing cover is respectively connected with the first end of the inner cylinder and the first end of the outer cylinder, and the second sealing cover is respectively connected with the second end of the inner cylinder and the second end of the outer cylinder.

The invention provides a further improvement of a shock absorber, which is characterized in that the inner cylinder comprises a main body section, a first bending section, a second bending section, a first extension section and a second extension section;

the first end of the main body section is connected with the first end of the first bending section, the first bending section bends towards the rod body and forms a second end of the first bending section, and the second end of the first bending section is connected with the first extending section;

the second end of the main body section is connected with the first end of the second bending section, the second bending section bends towards the rod body and forms a second end of the second bending section, and the second end of the second bending section is connected with the second extending section;

the two springs are respectively arranged between the first extension section and the rod body and between the second extension section and the rod body.

The damper provided by the invention can realize adjustable damping by adjusting the liquid flow rate in the cavity through the damping component. When the flow velocity of the oil in the cavity is high, the damping of the shock absorber is low; when the oil flow rate in the cavity is small, the damping of the shock absorber is large. The damper provided by the invention can realize large-scale adjustment of damping force and has good damping effect; the structure is relatively simple, and the cost is low; the strength and fatigue reliability are high, and the damage is not easy. The adjustable damping device has the advantages that the adjustable damping device can play a damping and damping role in compression and extension strokes of a suspension system, has a large adjustable range, improves the driving comfort of a vehicle, and has high reliability.

Drawings

In order to more clearly illustrate the embodiments of the invention or the technical solutions in the prior art, the drawings that are required in the embodiments or the description of the prior art will be briefly described, it being obvious that the drawings in the following description are only some embodiments of the invention, and that other drawings may be obtained according to these drawings without inventive effort for a person skilled in the art.

Fig. 1 is a schematic structural diagram of a shock absorber according to an embodiment of the present invention.

Fig. 2 is a schematic structural diagram of a hydraulic valve in a shock absorber according to an embodiment of the present invention.

Fig. 3 is a schematic cross-sectional view in the direction A-A of fig. 2.

FIG. 4 is a schematic diagram of the direction of oil flow in a first process according to an embodiment of the invention.

FIG. 5 is a schematic diagram of a damping characteristic curve in a first process according to an embodiment of the present invention.

FIG. 6 is a schematic diagram of the direction of oil flow in a second process according to an embodiment of the invention.

FIG. 7 is a schematic diagram of a damping characteristic curve in a second process according to an embodiment of the present invention.

FIG. 8 is a schematic diagram of a damping characteristic curve in a third process according to an embodiment of the present invention.

Detailed Description

The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It will be apparent that the described embodiments are only some, but not all, embodiments of the invention. All other embodiments, which can be made by those skilled in the art based on the embodiments of the invention without making any inventive effort, are intended to be within the scope of the invention.

In order to solve the problems of small damping adjustable range and poor adjustability of the existing shock absorber, thereby improving the shock absorption performance of the shock absorber and the travelling comfort of a vehicle, an embodiment of the present invention provides a shock absorber, and in combination with the shock absorber shown in fig. 1 to 8, the shock absorber in this embodiment includes:

the cylinder barrel 10 is internally provided with a cavity;

the piston rod is inserted into the cavity and comprises a rod body 21 and a piston ring 22, the piston ring 22 is arranged outside the rod body 21, the piston ring 22 abuts against the inner wall of the cylinder 10, and the piston ring 22 divides the cavity into a first cavity 101 and a second cavity 102;

the two damping components are respectively arranged in the first chamber 101 and the second chamber 102, and are used for adjusting the flow rate of liquid in the chambers.

In the embodiment, the damping component is used for adjusting the flow rate of liquid in the cavity, so that the damping is adjustable. When the flow velocity of the oil in the cavity is high, the damping of the shock absorber is low; when the oil flow rate in the cavity is small, the damping of the shock absorber is large. The piston rod in this embodiment is fixedly connected to the outside of the rod body 21, and the edge of the piston ring 22 abuts against the inner wall of the cylinder tube 10.

Further, the damping assembly includes a hydraulic valve 31 and a stop block 32; the limiting table 32 is arranged outside the rod body 21, and a gap is arranged between the limiting table 32 and the inner wall; the hydraulic valve 31 is sleeved outside the rod body 21, and the hydraulic valve 31 is positioned on one side of the limiting table 32, which is far away from the piston ring 22, and the side of the hydraulic valve 31, which is far away from the piston ring 22, and the side, which is close to the piston ring 22, are communicated with the side, which is far away from the rod body 21.

Further, the hydraulic valve 31 is provided with an orifice 312 and a flow guiding groove 311, the orifice 312 penetrates the hydraulic valve 31 along the axial direction of the rod body 21, the flow guiding groove 311 is arranged on the side surface of the hydraulic valve 31, which is close to the piston ring 22, a first end of the flow guiding groove 311 is communicated with the orifice 312, and a second end of the flow guiding groove 311 penetrates the edge of the hydraulic valve 31.

In this embodiment, the diversion trench 311 is disposed on the side surface of the hydraulic valve 31 near the piston ring 22, the first end of the diversion trench 311 is communicated with the orifice 312, and the second end of the diversion trench 311 penetrates through the edge of the hydraulic valve 31; thus, it can be said that the flow guide groove 311 is provided with a first opening on the side surface of the hydraulic valve 31 close to the piston ring 22, the first opening being in communication with the orifice 312; the diversion trench 311 is provided with a second opening at the side surface of the hydraulic valve 31 far away from the rod body 21; thus, the oil can flow from the side of the hydraulic valve 31 away from the piston ring 22 to the side of the hydraulic valve 31 close to the piston ring 22 through the orifice 312, and the oil can also be guided by the guide groove 311, and flows from the first opening to the second opening of the guide groove 311; the flow direction of the oil is not limited thereto.

Further, both the limiting table 32 and the hydraulic valve 31 are disk-shaped. In this embodiment, the limiting table 32 and the hydraulic valve 31 are both disc-shaped, and when the limiting table 32 abuts against the hydraulic valve 31, the limiting table 32 can cover the surface of the hydraulic valve 31, so that oil cannot flow out from the first opening, but only can flow out from the second opening of the diversion trench 311 through the orifice 312 and pass through the diversion trench 311. The oil on both sides of the stopper 32 can flow only through the gap between the stopper 32 and the inner wall of the cylinder 10.

Further, a predetermined distance is provided between the stop 32 and the piston ring 22. The oil can flow between the limiting table 32 and the piston ring 22, or can flow out from between the limiting table 32 and the piston ring 22.

In this embodiment, the range of values for the extension stroke and the compression stroke of the shock absorber may be 100 to 150mm. The predetermined distance between the stop 32 and the piston ring 22 may range in value from 10 to 20mm. When the piston ring 22 is located in the middle of the cavity of the cylinder tube 10, the distance between the stop table 32 and the hydraulic valve 31 may have a value ranging from 10 to 30mm.

Further, a sealing ring 33 is provided between the hydraulic valve 31 and the inner wall, the sealing ring 33 being located on the side of the hydraulic valve 31 remote from the piston ring 22. Due to the sealing action of the seal ring 33, the oil on both sides of the hydraulic valve 31 cannot flow directly between the hydraulic valve 31 and the inner wall of the cylinder 10, but can only flow through the orifice 312 and the diversion groove 311.

In this embodiment, the oil may be located between the piston ring 22 and the stopper 32, between the stopper 32 and the hydraulic valve 31, between the stopper 32 and the inner wall of the cylinder 10, and between the hydraulic valve 31 and the end of the cylinder 10.

In this embodiment, taking downward compression as an example, when the piston rod just begins to compress, the limiting table 32 and the hydraulic valve 31 are still in a separated state, and the oil can freely flow through the orifice 312, the upper opening (the first opening) of the diversion trench 311, and the side opening (the second opening) of the diversion trench 311, so that the oil flow velocity is large, and the damping of the shock absorber is small. When the stopper 32 is pressed further so that the stopper 32 abuts against the hydraulic valve 31, the stopper 32 blocks the upper opening of the flow guide groove 311, the liquid can flow only through the side opening (second opening) of the flow guide groove 311 and the orifice 312, the flow velocity of the oil is small, and the damping of the shock absorber is large.

Further, the damping assembly further comprises a spring 34, the spring 34 is sleeved outside the rod body 21, the spring 34 is located on one side of the hydraulic valve 31 away from the piston ring 22, and one end of the spring 34 away from the piston ring 22 abuts against the cylinder 10.

In this embodiment, when further compressed, the hydraulic valve 31 contacts the spring 34 and compresses the spring 34, further enhancing the damping of the shock absorber.

Further, the cylinder 10 is provided with a first cover 11, a second cover 12 and a cylinder body, the first cover 11 covers the first end of the cylinder body, the second cover 12 covers the second end of the cylinder body, and springs 34 of the two damping assemblies respectively abut against the first cover 11 and the second cover 12.

In this embodiment, when the piston ring 22 is located in the middle of the cavity of the cylinder tube 10, the distance between the piston ring 22 and the first cover 11 or the second cover 12 may be in the range of 100 to 150mm.

Further, the cylinder body comprises an inner cylinder 14 and an outer cylinder 13, the outer cylinder 13 is sleeved outside the inner cylinder 14, the first sealing cover 11 is respectively connected with the first end of the inner cylinder 14 and the first end of the outer cylinder 13, and the second sealing cover 12 is respectively connected with the second end of the inner cylinder 14 and the second end of the outer cylinder 13.

Still further, the inner barrel 14 includes a main body section 140, a first bending section 141, a second bending section 143, a first extension section 142, and a second extension section 144; the first end of the main body section 140 is connected with the first end of the first bending section 141, the first bending section 141 bends towards the rod body 21 and forms the second end of the first bending section 141, and the second end of the first bending section 141 is connected with the first extending section 142; the second end of the main body section 140 is connected with the first end of the second bending section 143, the second bending section 143 bends towards the rod body 21 and forms the second end of the second bending section 143, and the second end of the second bending section 143 is connected with the second extending section 144; the two springs 34 are respectively arranged between the first extension 142 and the rod body 21, and between the second extension 144 and the rod body 21.

In this embodiment, the inner diameter of the first extension section 142 is the same as the inner diameter of the second extension section 144, and the inner diameter of the main body section 140 is larger than the inner diameter of the first extension section 142. The seal 33 outside the hydraulic valve 31 has elasticity, and when the hydraulic valve 31 is located in the first extension 142, the seal 33 is pressed so that the seal 33 and the hydraulic valve 31 can be accommodated together in the first extension 142.

In the embodiment, the second sealing cover 12 is in sealing fit and fixedly connected with the damper outer cylinder 13, and the damper outer cylinder 13 is in sealing fit and fixedly connected with the first sealing cover 11; the inner cylinder 14 is fixedly connected with the outer cylinder 13; the piston rod can move up and down in the inner cylinder 14 to realize compression and extension of the shock absorber; the rod body 21 of the piston rod is fixedly provided with a piston ring 22, the piston ring 22 is in sealing fit with the inner wall of the inner cylinder 14, and the piston rod pushes oil to move in the moving process of the piston rod, so that damping force is generated. The limiting table 32 fixedly arranged on the rod body 21 of the piston rod can move together with the piston rod. The hydraulic valve 31 is movable in the axial direction of the piston rod with respect to the piston rod. The hydraulic valve 31 is provided with a diversion groove 311 and an orifice 312 for oil to pass through. The outer diameter ring of the hydraulic valve 31 is provided with the sealing ring 33, and the sealing ring 33 is in interference fit with the inner wall of the inner cylinder 14, so that after the limiting table 32 is contacted with the hydraulic valve 31, only oil flows out from the second opening of the hydraulic valve 31 and the throttle hole 312, and the effect of increasing damping force is achieved. A spring 34 is arranged between the damper inner cylinder 14 and the first sealing cover 11 and between the damper inner cylinder 14 and the second sealing cover 12, the spring 34 is sleeved on the rod body 21 of the piston rod, and the spring 34 can be contracted and expanded along the axial direction of the piston rod.

The embodiment can realize the technical effect that the damping force of the shock absorber can be adjusted in a large range. Taking the example that the piston rod in the present embodiment compresses and moves to the lower side in fig. 1, the working process of the present embodiment is analyzed, and specifically, the following three processes can be divided.

Process one: when the piston rod is compressed in the initial stage, the limiting table 32 assembled on the piston rod is separated from the hydraulic valve 31, and the limiting table 32 is not contacted with the hydraulic valve 31, so that the flow direction of oil in the inner cylinder 14 of the shock absorber is shown by an arrow in fig. 4; the oil flows from the space between the hydraulic valve 31 and the limiting table 32 to the side of the hydraulic valve 31 far away from the piston ring 22 through the diversion trench 311 and the throttle hole 312, and also flows to the side of the limiting table 32 near the piston ring 22 through the gap between the limiting table 32 and the inner cylinder 14; at this time, the damping force generated by the oil flow is very small or no hydraulic damping force is generated, the characteristic curve corresponds to a gentle variation section in the damping characteristic curve of the shock absorber, and the corresponding damping force curve is shown by a thickened section in a schematic diagram 5, wherein the vertical axis F in the diagram represents the damping force, and the horizontal axis d represents the movement speed of the piston rod.

At this time, in the first compression process, the piston rod moves downward, the limiting table 32 moves closer to the hydraulic valve 31, the liquid flow direction is as shown in fig. 4, the oil between the hydraulic valve 31 and the limiting table 32 mainly flows through the gap between the limiting table 32 and the inner wall of the inner cylinder 14 of the shock absorber, meanwhile, the volume of the inner cylinder 14 of the shock absorber corresponding to the lower side of the limiting table 32 gradually becomes smaller, the upper side volume gradually becomes larger, the lower side liquid pressure gradually and slowly increases, and the damping force generated in the process is smaller.

And a second process: compression continues, and at this time, the limiting table 32 is in contact with the hydraulic valve 31, and the flow direction of the oil in the inner cylinder 14 of the shock absorber is shown by an arrow in fig. 6; oil flows from the side of the hydraulic valve 31, which is far away from the piston ring 22, through the throttle hole 312, the second opening of the diversion trench 311, the gap between the limit table 32 and the inner wall of the inner cylinder 14, and flows to the side of the limit table 32, which is near to the piston ring 22; at this time, relatively large hydraulic pressure (more than 5kN can be achieved) is generated, and the damping force value in the damping force characteristic curve is rapidly increased; at the same time, the hydraulic valve 31 compresses in contact with the spring 34, and the spring 34 compresses in response to the compression, helping the hydraulic damping force to continue to increase linearly, which is the first stage in which the damping force is widely adjustable. The damping characteristics of the shock absorber are changed corresponding to the condition of large vertical vibration and displacement input of the wheel (the curve characteristics can be set according to different vehicle working condition calibration).

In the second compression process, the piston rod continues to move downward, the stop block 32 and the hydraulic valve 31 have contacted and together continue to move downward, the flow direction of the liquid is as shown in fig. 6, and the damping force generated in the process is larger because the volume of the inner cylinder 14 of the shock absorber corresponding to the lower side of the stop block 32 continues to be smaller, the volume of the upper side continues to be larger, the flow path of the liquid in the volume of the lower side is smaller.

In addition, the diameter of the structure of the inner cylinder 14 of the shock absorber is changed, the diameters of the two ends of the inner cylinder 14 are small, and the diameter of the middle is large. With the continuation of the second compression stroke, there is a sharp decreasing process in the oil volume cavity formed between the hydraulic valve 31 and the inner cylinder 14 of the shock absorber, and meanwhile, the spring 34 compresses to the limit position, at this time, the oil again generates a sudden change of a larger damping force (more than 10 kN), the damping force characteristic curve shows that the damping force value can rise to the limit, and the damping force is the maximum at this time, which corresponds to the variation of the damping characteristic of the shock absorber (the characteristic of the curve can be set according to different vehicle working condition calibration) under the extremely severe vertical vibration and displacement input condition of the wheel, and corresponds to the thickened section in the damping force curve diagram 7.

And a third process: after the hydraulic valve 31 and the spring 34 are compressed to the limit position, when the wheels also run through extremely severe road conditions, the vertical movement speed of the wheels and the shock absorber is reduced under the action of a large damping force, the hydraulic damping force generated by oil begins to be reduced, meanwhile, the spring 34 begins to provide a downward restoring force for the hydraulic valve 31, meanwhile, liquid on the upper side of the limiting table 32 flows back between the limiting table 32 and the shock absorber inner cylinder 14, the damping force is reduced along with the reduction of the speed in the process, and the spring 34 pushes the hydraulic valve 31 to the direction of the initial position, so that the hydraulic valve 31 returns to the initial position; the corresponding damping force curve is shown in bold section in figure 8.

For the stretching stroke of the upward movement of the piston rod in this embodiment, the damping force action curve is equally divided into three processes, but the movement direction of the piston rod, the hydraulic valve 31 and the limiting table 32 is opposite to the compression process, and the direction of the oil damping force is opposite, so that the description is omitted here.

In the embodiment, the damping force of the shock absorber can be adjusted in a large range according to the characteristics of the vehicle and the vertical runout displacement of the wheels in the running working condition. The compression stroke of the shock absorber is described in detail below according to the characteristics of vertical movement of wheels under different working conditions in the running process of the vehicle.

On small convex-concave pavement with good working condition, such as common urban highway or expressway, the damping force of the shock absorber acts as follows: when the vehicle runs under the working condition, the vertical runout of the wheels is extremely small, the motion displacement of the piston rod of the shock absorber is small, at the moment, when the compression amount of the piston rod is extremely small, the limiting table 32 on the piston rod is separated from the hydraulic valve 31, the small motion displacement of the piston rod can not enable the limiting table 32 to be in motion contact with the hydraulic valve 31, the flowing direction of damping oil in the inner cylinder 14 of the shock absorber is as shown in fig. 4, at the moment, the damping force generated by the oil flowing is extremely small or hydraulic damping force is not generated, and the characteristic curve corresponds to a gentle change section (as shown by a thickened section in fig. 5) in the damping characteristic curve of the shock absorber, so that small damping force is generated.

On uneven raised (or hollow) road surfaces with poor working conditions, such as broken roads of suburbs or rural roads, the vertical runout of wheels is large under the working conditions, the piston rod movement displacement of the shock absorber is large, when the piston rod compression amount is large, the piston rod compression movement displacement can enable the limit table 32 to be in contact with the hydraulic valve 31 and continue to compress, the flowing direction of damping oil in the inner cylinder 14 of the shock absorber is shown as in fig. 6, so that relatively large hydraulic pressure (more than 5kN can be achieved) is generated, and the damping force value in a damping force characteristic curve can be rapidly increased (as shown by a thickened section in fig. 7); simultaneously, the hydraulic valve 31 is contacted with the spring 34 to be compressed together, and the spring 34 is compressed together, so that the oil damping force is continuously and linearly increased, large vibration transmitted by wheels is effectively restrained, jolt of a vehicle body is effectively controlled, and comfortable riding feel is brought to people.

Under extremely severe working conditions, such as mountain roads and off-road roads with large ridges, the vehicle runs under the working conditions, the vertical runout of wheels is very large, the motion displacement of the piston rod of the shock absorber is very large, at the moment, when the compression amount of the piston rod is very large, the piston rod is compressed together when the hydraulic valve 31 is contacted with the spring 34, the spring 34 is compressed together, the oil damping force continues to linearly increase, and meanwhile, as the structural diameter of the inner cylinder 14 of the shock absorber is changed, the diameters of the two ends of the diameter of the inner cylinder 14 are small, and the middle diameter is large. With the continuation of the compression stroke, there is a sharp decrease in the volume of oil formed between the hydraulic valve 31 and the inner cylinder 14 of the shock absorber, and the spring 34 compresses to the limit position, at which time the oil again generates a sudden change in the larger damping force (up to more than 10 kN), which is shown in the damping force characteristic curve as the damping force value rising to the limit (as shown in the thickened section of fig. 8), and the damping force at this time is the maximum, which is also the damping characteristic required for the shock absorber corresponding to the extremely severe vertical shock of the wheel.

For the stretching working stroke of the shock absorber, the damping force action characteristic is equally divided into three working conditions, namely, in the stretching working process of the shock absorber, the movement direction of the piston rod, the hydraulic valve 31 and the limiting table 32 is opposite to the compression process, and the direction of the oil damping force is opposite, so that the description is omitted.

The damping force adjustable range of a general vehicle shock absorber in the current market is smaller, under the condition of larger vibration, the general shock absorber cannot efficiently absorb large vibration transmitted by wheels in the running process of the vehicle through the damping characteristic of the shock absorber, so that the vehicle jolts more, and the riding experience is influenced. The damper provided by the invention can realize large-scale adjustment of damping force, and has good damping effect; the structure is relatively simple, and the cost is low; the strength and fatigue reliability are high, and the damage is not easy.

The foregoing is only illustrative of the present invention and is not to be construed as limiting thereof, but rather as various modifications, equivalent arrangements, improvements, etc., within the spirit and principles of the present invention.

Claims

A shock absorber, comprising:

a cylinder barrel (10), wherein a cavity is arranged in the cylinder barrel (10);

the piston rod is inserted into the cavity and comprises a rod body (21) and a piston ring (22), the piston ring (22) is arranged outside the rod body (21), the piston ring (22) abuts against the inner wall of the cylinder barrel (10), and the piston ring (22) divides the cavity into a first cavity (101) and a second cavity (102);

the two damping components are respectively arranged in the first chamber (101) and the second chamber (102), and the damping components are used for adjusting the flow rate of liquid in the chambers.
The shock absorber according to claim 1, wherein the damping assembly comprises a hydraulic valve (31) and a stop table (32);

the limiting table (32) is arranged outside the rod body (21), and a gap is arranged between the limiting table (32) and the inner wall;

the hydraulic valve (31) is sleeved outside the rod body (21), the hydraulic valve (31) is located on one side, away from the piston ring (22), of the limiting table (32), and the side, away from the piston ring (22), of the hydraulic valve (31), the side, close to the piston ring (22) and the side, away from the rod body (21), of the hydraulic valve (31) are communicated.
The shock absorber as set forth in claim 2 wherein said hydraulic valve (31) is provided with an orifice (312) and a flow guiding groove (311), said orifice (312) penetrating said hydraulic valve (31) in an axial direction of said rod body (21), said flow guiding groove (311) being provided on a side surface of said hydraulic valve (31) near said piston ring (22), a first end of said flow guiding groove (311) being communicated with said orifice (312), a second end of said flow guiding groove (311) penetrating an edge of said hydraulic valve (31).
A shock absorber according to claim 3, wherein the hydraulic valve (31) and the stop table (32) are both disc-shaped.
The shock absorber according to claim 2, wherein a predetermined distance is provided between the stop table (32) and the piston ring (22).
A shock absorber according to claim 2, wherein a sealing ring (33) is arranged between the hydraulic valve (31) and the inner wall, the sealing ring (33) being located on the side of the hydraulic valve (31) remote from the piston ring (22).
The shock absorber according to claim 2, wherein the damping assembly further comprises a spring (34), the spring (34) is sleeved outside the rod body (21), the spring (34) is located on one side of the hydraulic valve (31) away from the piston ring (22), and one end of the spring (34) away from the piston ring (22) abuts against the cylinder (10).
The shock absorber according to claim 7, wherein the cylinder (10) is provided with a first cover (11), a second cover (12) and a cylinder body, the first cover (11) being arranged at a first end of the cylinder body, the second cover (12) being arranged at a second end of the cylinder body, the springs (34) of the two damping assemblies being respectively abutted against the first cover (11) and the second cover (12).
The shock absorber according to claim 8, wherein the cylinder comprises an inner cylinder (14) and an outer cylinder (13), the outer cylinder (13) is sleeved outside the inner cylinder (14), the first sealing cover (11) is respectively connected with a first end of the inner cylinder (14) and a first end of the outer cylinder (13), and the second sealing cover (12) is respectively connected with a second end of the inner cylinder (14) and a second end of the outer cylinder (13).
The shock absorber of claim 9, wherein the inner barrel (14) comprises a main body section (140), a first bending section (141), a second bending section (143), a first extension section (142) and a second extension section (144);

the first end of the main body section (140) is connected with the first end of the first bending section (141), the first bending section (141) is bent towards the rod body (21) and forms a second end of the first bending section (141), and the second end of the first bending section (141) is connected with the first extension section (142);

the second end of the main body section (140) is connected with the first end of the second bending section (143), the second bending section (143) is bent towards the rod body (21) and forms the second end of the second bending section (143), and the second end of the second bending section (143) is connected with the second extension section (144);

the two springs (34) are respectively arranged between the first extension section (142) and the rod body (21) and between the second extension section (144) and the rod body (21).