CN112406443B - Vibration damper - Google Patents

Vibration damper Download PDF

Info

Publication number
CN112406443B
CN112406443B CN202011234054.6A CN202011234054A CN112406443B CN 112406443 B CN112406443 B CN 112406443B CN 202011234054 A CN202011234054 A CN 202011234054A CN 112406443 B CN112406443 B CN 112406443B
Authority
CN
China
Prior art keywords
hole
throttling
piston
compression
conical cover
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Active
Application number
CN202011234054.6A
Other languages
Chinese (zh)
Other versions
CN112406443A (en
Inventor
吴柳杰
涂佳伟
单东升
陈赞
刘洋
张军晓
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Ningbo Yanqing Automobile Technology Co ltd
Original Assignee
Ningbo Yanqing Automobile Technology Co ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Ningbo Yanqing Automobile Technology Co ltd filed Critical Ningbo Yanqing Automobile Technology Co ltd
Priority to CN202011234054.6A priority Critical patent/CN112406443B/en
Priority to CN202110713019.0A priority patent/CN113400880B/en
Publication of CN112406443A publication Critical patent/CN112406443A/en
Application granted granted Critical
Publication of CN112406443B publication Critical patent/CN112406443B/en
Active legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G13/00—Resilient suspensions characterised by arrangement, location or type of vibration dampers
    • B60G13/02—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally
    • B60G13/06—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type
    • B60G13/08—Resilient suspensions characterised by arrangement, location or type of vibration dampers having dampers dissipating energy, e.g. frictionally of fluid type hydraulic
    • 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
    • B60G17/015—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 the regulating means comprising electric or electronic elements
    • B60G17/0152—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 the regulating means comprising electric or electronic elements characterised by the action on a particular type of suspension unit
    • 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
    • B60G17/015—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 the regulating means comprising electric or electronic elements
    • B60G17/016—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 the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input
    • B60G17/0164—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 the regulating means comprising electric or electronic elements characterised by their responsiveness, when the vehicle is travelling, to specific motion, a specific condition, or driver input mainly during accelerating or braking
    • 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
    • B60G17/06—Characteristics of dampers, e.g. mechanical dampers
    • B60G17/08—Characteristics of fluid dampers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/10—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium using liquid only; using a fluid of which the nature is immaterial
    • F16F9/14—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect
    • F16F9/16—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts
    • F16F9/18—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein
    • F16F9/19—Devices with one or more members, e.g. pistons, vanes, moving to and fro in chambers and using throttling effect involving only straight-line movement of the effective parts with a closed cylinder and a piston separating two or more working spaces therein with a single cylinder and of single-tube type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/34—Special valve constructions; Shape or construction of throttling passages
    • F16F9/348—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body
    • F16F9/3481—Throttling passages in the form of annular discs or other plate-like elements which may or may not have a spring action, operating in opposite directions or singly, e.g. annular discs positioned on top of the valve or piston body characterised by shape or construction of throttling passages in piston
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F9/00—Springs, vibration-dampers, shock-absorbers, or similarly-constructed movement-dampers using a fluid or the equivalent as damping medium
    • F16F9/32—Details
    • F16F9/50—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics
    • F16F9/516—Special means providing automatic damping adjustment, i.e. self-adjustment of damping by particular sliding movements of a valve element, other than flexions or displacement of valve discs; Special means providing self-adjustment of spring characteristics resulting in the damping effects during contraction being different from the damping effects during extension, i.e. responsive to the direction of movement
    • 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
    • B60G2202/20—Type of damper
    • B60G2202/24—Fluid damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2500/00—Indexing codes relating to the regulated action or device
    • B60G2500/10—Damping action or damper
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
    • B60G2800/20—Stationary vehicle
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60G—VEHICLE SUSPENSION ARRANGEMENTS
    • B60G2800/00—Indexing codes relating to the type of movement or to the condition of the vehicle and to the end result to be achieved by the control action
    • B60G2800/90—System Controller type
    • B60G2800/91—Suspension Control
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/0005—Attachment, e.g. to facilitate mounting onto confer adjustability
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/08—Sensor arrangement
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F2230/00—Purpose; Design features
    • F16F2230/18—Control arrangements

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Fluid-Damping Devices (AREA)
  • Vehicle Body Suspensions (AREA)

Abstract

The invention provides a shock absorber, and belongs to the field of vehicles. The shock absorber comprises an outer cylinder, a piston rod and two electromagnetic valves; the outer cylinder is connected with the suspension, the piston is arranged in the outer cylinder in a sliding mode, and one end, extending out of the outer cylinder, of the piston rod is connected with the frame. The upper cavity and the lower cavity of the piston are filled with hydraulic oil, the two electromagnetic valves are arranged on the piston, the flow area on the piston can be adjusted by adjusting the opening of the electromagnetic valves, and the damping force of the shock absorber is further adjusted; and the running stability of the vehicle is improved, and the riding experience is improved. The vehicle adopts the shock absorber, so that the comprehensive shock absorption performance of the vehicle is improved. By adopting the method for improving the running stability of the vehicle, the method is beneficial to increasing the adhesive force of the rear wheel to the ground and controlling the stability of the whole vehicle body in the case of emergency braking. When the brake is carried out under the general condition, the damping force is reduced, so that effective buffering can be formed, and the comfort during braking is improved.

Description

Vibration damper
Technical Field
The invention relates to the field of vehicles, in particular to a shock absorber.
Background
The running stability of the vehicle is one of the indexes of the driving experience, and in order to improve the running stability of the vehicle, a hydraulic shock absorber is additionally arranged between a wheel suspension and a vehicle frame, which is one of more important means. The existing hydraulic damper has poor damping performance and is difficult to meet the requirement of people on the running stability of the vehicle.
Disclosure of Invention
The invention aims to provide a shock absorber, which can adjust the damping force according to the actual vehicle condition so as to further improve the shock absorption performance.
The invention is realized by the following steps:
a shock absorber, said shock absorber comprising:
the outer cylinder is used for containing hydraulic oil and is connected with the corresponding suspension;
the piston is arranged in the outer cylinder in a sliding mode; two mounting through holes are formed in the piston;
one end of the piston rod is connected with the piston, and the other end of the piston rod is used for being connected with a corresponding frame;
the two electromagnetic valves are normally closed valves and are respectively arranged in the two installation through holes; the two electromagnetic valves are an upstream electromagnetic valve and a downstream electromagnetic valve, and when the piston moves downwards; the up-flow solenoid valve can be opened so that pressure oil can flow upward through the solenoid valve; when the piston moves upward, the downstream solenoid valve can be opened so that the pressure oil can flow downward through the solenoid valve.
Further, the method comprises the following steps of;
the electromagnetic valve comprises a compression fixed iron, a compression moving iron and a compression spring;
the compressed fixed iron is fixedly arranged in the corresponding installation through hole, the compressed moving iron is arranged in the corresponding installation through hole in a sliding manner, and the flow area of the corresponding installation through hole is correspondingly changed when the compressed moving iron slides;
and two ends of the compression spring are respectively abutted against the compression movable iron and the compression fixed iron.
Further, the method comprises the following steps of;
the mounting through holes are stepped holes and comprise large-diameter holes and small-diameter holes; the compression moving iron and the compression fixed iron are both cylindrical, an oil passing hole is formed in the middle of the compression fixed iron, and an oil passing groove is formed in the circumferential surface of the compression moving iron; the oil passing hole and the oil passing groove extend along the axial direction of the mounting through hole;
the compression fixed iron is fixedly installed in the large-diameter hole, the compression movable iron is arranged in the large-diameter hole in a sliding mode, and the compression movable iron can block the small-diameter hole in a natural state.
Further, the method comprises the following steps of;
the throttling assembly comprises an upper conical cover, a lower conical cover, a connecting rod and a throttling spring; the piston is provided with a throttling through hole;
the throttling through hole is a stepped hole and comprises a throttling large hole and a throttling small hole, the throttling large hole extends to the upper surface of the piston, and the throttling small hole extends to the lower surface of the piston; the end part of the throttling large hole is provided with a chamfer to form a conical surface;
the piston is also provided with a throttling channel, one end of the throttling channel extends to the hole wall or the bottom of the throttling large hole, and the other end of the throttling channel extends to the lower surface of the piston; the throttling channel is obliquely arranged, and the distance between the lower end of the throttling channel and the axis of the throttling small hole is greater than the radius of the lower conical cover;
the connecting rod penetrates through the throttling through hole and is arranged in the throttling small hole in a sliding mode, the upper end of the connecting rod is connected with the upper conical cover, and the lower end of the connecting rod is connected with the lower conical cover; the large end face of the upper conical cover faces upwards, and the large end face of the lower conical cover faces downwards;
the throttling spring is arranged in the throttling big hole, one end of the throttling spring is abutted with the upper conical cover, and the other end of the throttling spring is abutted with the bottom of the throttling big hole;
in a natural state of the throttling spring, a gap is reserved between the upper conical cover and the conical surface; and a gap is reserved between the lower conical cover and the lower surface of the piston.
Further, the method comprises the following steps of;
the piston is also provided with a first flow passage and a second flow passage, the first flow passage penetrates through the piston, one end of the second flow passage extends to the end face of the piston, and the other end of the second flow passage penetrates through the first flow passage;
an adjusting screw is further arranged at one end of the first flow channel, and when the adjusting screw is screwed in or out, the effective flow area of the second flow channel can be adjusted; hydraulic oil can pass through the piston through the first flow passage and the second flow passage.
Further, the method comprises the following steps of;
the two electromagnetic valves are installed in opposite directions, and the elastic force of the compression spring of the upstream electromagnetic valve is smaller than that of the compression spring of the downstream electromagnetic valve.
A vehicle comprises a frame, four damping springs and four suspensions, wherein the four suspensions are respectively provided with the dampers and are connected with the frame through the corresponding dampers and damping springs;
still be provided with on the frame:
a controller;
the speed sensor is used for detecting the moving speed of the frame;
an acceleration sensor for detecting an acceleration of the frame;
the four displacement sensors are respectively used for detecting displacement signals between the frame and the corresponding suspension;
the controller can receive detection signals of the speed sensor, the acceleration sensor and the four displacement sensors and can calculate the relative speed between the frame and the corresponding suspension according to the detection signals of the displacement sensors;
the controller is also capable of controlling the opening of the solenoid valves on the four shock absorbers.
A method for improving the smoothness of a vehicle, for said vehicle, comprising the steps of:
when the controller receives the braking signal, whether the braking is in a normal condition or an emergency condition is judged;
when the speed signal is greater than a preset speed value and the acceleration signal is greater than a preset acceleration value, emergency braking is determined; controlling the opening degrees of an upstream electromagnetic valve and a downstream electromagnetic valve on the four shock absorbers of the front wheel and the rear wheel to be reduced, and increasing damping force;
otherwise, judging to brake under the normal condition; the opening degrees of the upstream electromagnetic valve and the downstream electromagnetic valve on the two shock absorbers for controlling the front wheels are increased, and the damping force is reduced.
Further, the method comprises the following steps of;
when the received displacement signal in the displacement sensor is larger than a preset displacement value, judging that the road surface below the shock absorber corresponding to the displacement sensor is uneven;
judging whether the piston of the shock absorber moves downwards or upwards according to the positive and negative of the displacement signal;
when the vibration absorber moves downwards, the larger opening degree of an upstream electromagnetic valve of the vibration absorber is given, and the downstream electromagnetic valve is kept closed, so that the damping force is reduced; when the piston moves upwards, the lower flow electromagnetic valve of the shock absorber is given a smaller opening degree, so that the lower piston cavity generates negative pressure.
Further, the method comprises the following steps of;
when the received displacement signals of the four displacement sensors are all smaller than a preset displacement value, judging that the vehicle runs on a smooth road;
further judging whether the vehicle runs at a high speed or at a low speed, and keeping the electromagnetic valves of the four shock absorbers closed when the speed of the vehicle frame is less than a preset speed value; otherwise, controlling the electromagnetic valves of the four vibration absorbers to keep a preset opening;
when the vehicle turns left, the opening degree of the electromagnetic valve of the shock absorber corresponding to the left wheel is increased, the damping force of the left wheel is reduced, and the height of the right side of the vehicle is slightly higher than that of the left side of the vehicle; when the vehicle turns right, the opening degree of the electromagnetic valve of the shock absorber corresponding to the right wheel is increased.
The invention has the beneficial effects that:
according to the shock absorber obtained through the design, the opening degree of the two electromagnetic valves can be controlled by the external controller, so that the damping force of the shock absorber can be adjusted according to the actual vehicle condition; and then can improve the stationarity that promotes vehicle and travel and improve and experience by bus.
The vehicle adopts the shock absorber, and the damping force of the four shock absorbers on the four wheels can be adjusted according to the running condition of the vehicle and the condition of the road surface below the wheels; thereby improving the comprehensive vibration damping performance of the vehicle.
The method for improving the running stability of the vehicle can be used for the vehicle; when the vehicle is emergently braked, the damping force of the front and rear shock absorbers is increased, so that the tail tilting condition of the vehicle caused by the emergency brake is improved. The operation is beneficial to increasing the adhesive force of the rear wheel to the ground, controlling the stability of the whole vehicle body and reducing the probability of overturning. When the brake is carried out under the general condition, the damping force is reduced, so that effective buffering can be formed, and the comfort during braking is improved.
Drawings
In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings that are required to be used in the embodiments will be briefly described below, it should be understood that the following drawings only illustrate some embodiments of the present invention and therefore should not be considered as limiting the scope, and for those skilled in the art, other related drawings can be obtained according to the drawings without inventive efforts.
Fig. 1 is an overall structural schematic view of a shock absorber provided in embodiment 1 of the present invention;
fig. 2 is a sectional view showing the overall structure of a piston provided in embodiment 1 of the present invention;
fig. 3 is a cross-sectional view of the piston provided in embodiment 1 of the present invention along another vertical plane;
fig. 4 is an overall sectional view of a piston provided in embodiment 2 of the present invention.
Icon: 100-a shock absorber; 110-an outer barrel; 112-a piston tube; 114-a reservoir; 120-a piston; 121-mounting through holes; 1211-large diameter hole; 1212-small diameter hole; 122-a throttling through hole; 1221-throttling large hole; 1222-a flow orifice; 123-a throttling channel; 124-a first flow channel; 125-a second flow channel; 130-a piston rod; 140-an up-flow solenoid valve; 141-compacted fixed iron; 142-compression moving iron; 143-a compression spring; 144-proportional electromagnet; 150-a downstream solenoid valve; 160-a throttling assembly; 161-upper conical cover; 162-lower cone cover; 163-connecting rod; 164-a throttle spring; 165-a stop lever; 170-adjusting screws; 180-bottom valve.
Detailed Description
In order to make the objects, technical solutions and advantages of the embodiments of the present invention more apparent, the technical solutions of the embodiments of the present invention will be described clearly and completely with reference to the accompanying drawings of the embodiments of the present invention, and it is obvious that the described embodiments are some, but not all embodiments of the present invention. All other embodiments, which can be obtained by a person skilled in the art without any inventive step based on the embodiments of the present invention, are within the scope of the present invention.
In the description of the present invention, it is to be understood that the terms indicating an orientation or positional relationship are based on the orientation or positional relationship shown in the drawings only for the convenience of describing the present invention and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention.
In the present invention, unless otherwise expressly stated or limited, the terms "mounted," "connected," "secured," and the like are to be construed broadly and can, for example, be fixedly connected, detachably connected, or integrally formed; can be mechanically or electrically connected; either directly or indirectly through intervening media, either internally or in any other relationship. The specific meanings of the above terms in the present invention can be understood by those skilled in the art according to specific situations.
In the description of the present invention, it should be noted that the terms "center", "upper", "lower", "left", "right", "vertical", "horizontal", "inner", "outer", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings or the orientations or positional relationships that the products of the present invention are conventionally placed in use, and are only used for convenience in describing the present invention and simplifying the description, but do not indicate or imply that the devices or elements referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus, should not be construed as limiting the present invention. Furthermore, the terms "first," "second," "third," and the like are used solely to distinguish one from another and are not to be construed as indicating or implying relative importance.
Furthermore, the terms "horizontal", "vertical", "overhang" and the like do not imply that the components are required to be absolutely horizontal or overhang, but may be slightly inclined. For example, "horizontal" merely means that the direction is more horizontal than "vertical" and does not mean that the structure must be perfectly horizontal, but may be slightly inclined.
In the present invention, unless otherwise expressly stated or limited, the first feature may be present on or under the second feature in direct contact with the first and second feature, or may be present in the first and second feature not in direct contact but in contact with another feature between them. Also, the first feature being above, on or above the second feature includes the first feature being directly above and obliquely above the second feature, or merely means that the first feature is at a higher level than the second feature. A first feature that underlies, and underlies a second feature includes a first feature that is directly under and obliquely under a second feature, or simply means that the first feature is at a lesser level than the second feature.
In the present application, the terms "upper" and "lower" are used with reference to the damper of FIG. 1.
Example (b):
referring to fig. 1, the present embodiment provides a shock absorber 100 for mounting between a vehicle frame and a suspension, thereby reducing vibration between a vehicle body and a wheel. The damper 100 includes an outer cylinder 110, a piston 120 rod, and two solenoid valves; the outer cylinder 110 is connected with a suspension, the piston 120 is slidably arranged in the outer cylinder 110, and one end of the piston 120 extending out of the outer cylinder 110 is connected with a vehicle frame. The upper chamber and the lower chamber of the piston 120 are filled with hydraulic oil, and the two solenoid valves are disposed on the piston 120, and the flow area on the piston 120 can be adjusted by adjusting the opening degree of the solenoid valves, thereby adjusting the damping force of the shock absorber 100.
Specifically, the outer cylinder 110 includes a piston tube 112 and a liquid storage tube 114 coaxially arranged, the piston tube 112 is arranged in the liquid storage tube 114, and oil seals are arranged at the upper ends of the piston tube 112 and the liquid storage tube 114; a closed reservoir is formed between the piston tube 112 and the reservoir tube 114. The bottom of the piston tube 112 is further provided with a bottom valve 180, which is communicated with the liquid storage chamber and the inner cavity of the piston tube 112, and comprises two check valves with opposite directions and different spring forces, and which are used for absorbing and compensating the volume of the part of the piston 120 extending into or out of the rod. The upper and lower chambers of the piston 120 are filled with hydraulic oil, and the liquid storage chamber is filled with low-pressure nitrogen gas.
Referring to fig. 1 and 2, a piston 120 is slidably disposed in the piston tube 112, and two mounting through holes 121 are formed therein; the two mounting through-holes 121 are used to mount two solenoid valves. Both of the two solenoid valves are normally closed valves, and are divided into an upstream solenoid valve 140 and a downstream solenoid valve 150 for convenience of description. When the piston 120 moves downwards, the up-flow solenoid valve 140 can be opened, so that the pressure oil can flow upwards from the lower cavity of the piston 120 to the upper cavity of the piston 120 through the solenoid valve; when the piston 120 moves upward, the downstream solenoid valve 150 can be opened, so that the pressure oil can flow downward from the upper chamber of the piston 120 to the lower chamber of the piston 120 through the solenoid valve.
One end of the piston 120 rod is connected with the piston 120, and the other end of the piston 120 rod is connected with the frame by penetrating out of the outer cylinder 110; the piston 120 rod is a hollow shaft to facilitate routing.
The electromagnetic valve specifically comprises a compression fixed iron 141, a compression movable iron 142, a compression spring 143 and a proportional electromagnet 144; the compression fixed iron 141 is fixedly installed in the installation through hole 121, the compression movable iron 142 is slidably disposed in the installation through hole 121, both ends of the compression spring 143 are respectively abutted against the compression movable iron 142 and the compression fixed iron 141, and the solenoid valve is kept closed by the elastic force of the compression spring 143. By applying different currents to the proportional electromagnet 144, the displacement of the compression moving iron 142 can be precisely controlled, thereby adjusting the opening of the solenoid valve.
Specifically, the compacted moving iron 142 and the compacted fixed iron 141 are both cylindrical, the middle part of the compacted fixed iron 141 is provided with an oil passing hole, and the circumferential surface of the compacted moving iron 142 is provided with an oil passing groove; the oil passing hole and the oil passing groove extend along the axial direction of the mounting through hole 121.
The mounting through hole 121 is a stepped hole, and includes a large-diameter hole 1211 and a small-diameter hole 1212; the compression fixed iron 141 is fixedly installed in the large-diameter hole 1211, and the compression moving iron 142 is slidably disposed in the large-diameter hole 1211. In a natural state, the small diameter hole 1212 can be sealed by the compression movable iron 142 under the action of the compression spring 143. When the compression moving iron 142 moves, an overflowing gap is formed between the end surface of the compression moving iron 142 and the end surface of the small-diameter hole 1212; the greater the travel distance, the greater the overcurrent gap.
In the up-flow electromagnetic valve 140, the compression moving iron 142 is positioned below the compression fixed iron 141; in the downstream solenoid valve 150, the moving compression iron 142 is located above the fixed compression iron 141. Taking the above-mentioned solenoid valve 140 as an example, when the solenoid valve is opened, the hydraulic oil in the lower chamber of the piston 120 flows through the small-diameter hole 1212, then flows through the flow-through gap, and finally enters the upper chamber of the piston 120 through the oil-through hole on the compression stator 141.
The two electromagnetic valves have the same basic structure and opposite installation directions; the compression spring 143 of the upstream solenoid valve 140 has a smaller initial spring force and stiffness coefficient than the compression spring 143 of the downstream solenoid valve 150. When the controller fails to control, the two electromagnetic valves can be used as two one-way valves; further, the above design makes the damping force in the compression stroke smaller than the damping force in the recovery stroke. When the piston 120 moves downwards, a smaller damping force is set, so that a damping spring between the frame and the suspension can absorb vibration, and the impact is reduced; and when going upward, set up great damping force and be favorable to turning into the internal energy of pressure oil with damping spring's elastic potential energy to improve the stationarity of vehicle.
Further, referring to fig. 3, the shock absorber 100 is further provided with a throttling assembly 160, which can provide a certain damping force for the movement of the piston 120 when both solenoid valves are closed.
Specifically, the throttle assembly 160 includes an upper conical cover 161, a lower conical cover 162, a connecting rod 163, and a throttle spring 164, and the piston 120 is provided with a trapezoidal throttle through hole 122. The throttle through hole 122 is a stepped hole and comprises a throttle large hole 1221 and a throttle small hole 1222, the throttle large hole 1221 extends to the upper surface of the piston 120, and the throttle small hole 1222 extends to the lower surface of the piston 120; the end of the large throttling hole 1221 is provided with a chamfer to form a conical surface.
The piston 120 is also provided with a throttling channel 123, one end of the throttling channel 123 extends to the hole wall or the bottom of the throttling big hole 1221, and the other end of the throttling channel 123 extends to the lower surface of the piston 120; the throttle passage 123 is obliquely arranged, and the distance between the lower end of the throttle passage 123 and the axis of the throttle orifice 1222 is larger than the radius of the lower cone cover 162. When the piston 120 moves downwards, the design can avoid the resistance formed by the lower conical cover 162 on the upward flow of the pressure oil into the throttling channel 123; thereby reducing unnecessary damping force.
The connecting rod 163 penetrates through the throttling through hole 122 and is slidably arranged in the throttling small hole 1222, the upper end of the connecting rod 163 is connected with the upper conical cover 161, and the lower end of the connecting rod 163 is connected with the lower conical cover 162; the large end surface of the upper cone cover 161 faces upward, and the large end surface of the lower cone cover 162 faces downward. The throttle spring is a spring which can be stretched and compressed; which is disposed in the large throttling hole 1221, one end of the throttling spring 164 is connected to the upper conical cover 161, and the other end is connected to the bottom of the large throttling hole 1221.
The throttle spring 164 is in a natural state with a gap between the upper conical cover 161 and the conical surface. A gap is left between the lower cone cover 162 and the lower surface of the piston 120 to allow a margin for the connecting rod 163 to move up and down. At this time, the hydraulic oil in the lower chamber of the piston 120 can enter the large throttle hole 1221 through the throttle passage 123, and further enter the upper chamber of the piston 120 through the gap between the upper conical cover 161 and the conical surface at the end of the large throttle hole 1221. When the connecting rod 163 moves upward, the gap between the upper conical cover 161 and the conical surface increases, and the damping force thereof decreases with the same pressure difference; when moving downward, the gap is reduced, and the damping force is increased when the pressure difference is the same.
When the vehicle runs at a low speed on a stable road surface, in order to reduce the working time of the electromagnetic valve, the service life of the shock absorber 100 is prolonged; at this time, the vibration is small, and the solenoid valve may not be operated. And the throttling component can realize the automatic adjustment of the damping force within a certain range. Specifically, during the compression stroke, the piston 120 moves downward, and the pressure oil in the lower cavity of the piston 120 pushes the lower conical cover 162, the connecting rod 163 and the upper conical cover 161 to overcome the tension of the throttle spring and move upward, so that the gap between the upper conical cover 161 and the conical surface is increased, the damping force is reduced, and the vibration is absorbed by the damping spring; and, the larger the vibration, the larger the upward moving distance of the upper conical cover 161, and the smaller the damping force. During the return stroke, the piston 120 moves upward, and in order to convert the elastic potential energy of the damping spring into the internal energy of the pressure oil, the damping force needs to be increased; the pressure oil in the upper chamber of the piston 120 pushes the upper cone cover 161 against the supporting force of the throttle spring and moves downward, thereby reducing the gap between the upper cone cover 161 and the tapered surface and increasing the damping force.
Further, if the upper conical cover 161 moves downward by too large a distance, it may completely block the orifice, at which time the damping force increases sharply; the damping force is increased rapidly, so that the instant impact on the vehicle is larger, and the running stability of the vehicle is further reduced. Therefore, in order to further improve the running stability of the vehicle, the bottom of the upper conical cover 161 is connected with a limiting rod 165; when the upper conical cover 161 moves downwards to a certain distance, the limiting rod 165 is abutted to the piston 120, and at the moment, a certain gap is still formed between the upper conical cover 161 and the conical surface, so that the running stability of the vehicle can be ensured. When the vehicle is running on a smooth road surface at a high speed or on an uneven road surface; the controller can control the opening of the two electromagnetic valves according to specific working conditions, and further control the damping force of the piston 120 during ascending and descending to improve the overall stability of the vehicle.
Example 2:
referring to fig. 4, the present embodiment provides another shock absorber 100, which is substantially the same as embodiment 1 except that the throttling assembly has a different partial structure.
In the shock absorber 100 of the present embodiment, the throttling assembly is replaced by an adjusting screw 170, the piston 120 is further provided with a first flow passage 124 and a second flow passage 125, the first flow passage 124 penetrates through the piston 120, one end of the second flow passage 125 extends to an end surface of the piston 120, and the other end penetrates through the first flow passage 124. When the adjusting screw 170 is screwed in or out, the effective flow area of the second flow channel 125 can be adjusted; hydraulic oil can pass through the piston 120 through a first flow passage 124 and a second flow passage 125.
The adjusting screw 170 may be screwed to a certain depth in advance according to a specific model of a vehicle and a self-weight of the vehicle, thereby giving an open area. When the vehicle runs at a low speed on a smooth road surface, the two battery valves can be kept closed, and hydraulic oil flows through the first flow passage 124 and the second flow passage 125, so that a certain damping force can be provided for the piston 120.
Example 3:
the present embodiment provides a vehicle that includes a vehicle frame, four damper springs, and four suspensions, and employs the damper 100 of embodiment 1 or 2. The damper springs may be directly provided between the suspension and the vehicle frame, or may be integrated into the damper 100. The piston 120 of the shock absorber 100 is hinged to the frame, and the lower end of the outer tube 110 is hinged to the suspension.
The vehicle further comprises a controller, a speed sensor, an acceleration sensor and four displacement sensors. The controller can directly adopt a vehicle-mounted ECU, and a speed sensor and an acceleration sensor are used for detecting the moving speed and the acceleration of the vehicle frame. One end of the displacement sensor is connected to the outer cylinder 110 of the shock absorber 100, and the other end is connected to the piston 120 rod for a displacement signal between the vehicle frame and the corresponding suspension.
The controller can receive detection signals of the speed sensor, the acceleration sensor and the four displacement sensors and can calculate the relative speed between the frame and the corresponding suspension according to the detection signals of the displacement sensors; the controller is also capable of controlling the opening of the solenoid valves on the four shock absorbers 100.
Example 4:
the present embodiment provides a method for improving the running stability of a vehicle, which can be applied to the vehicle provided in embodiment 3; the method specifically comprises the following steps:
when the controller receives the braking signal, the controller judges whether the braking is normal braking or emergency braking. The judgment method comprises the following steps: when the speed signal is greater than a preset speed value and the acceleration signal is greater than a preset acceleration value, emergency braking is determined; the opening degrees of the upstream solenoid valve 140 and the downstream solenoid valve 150 on the four shock absorbers 100 for controlling the front and rear wheels are decreased, increasing the damping force. Otherwise, braking is normal. The corresponding operation under the emergency condition is beneficial to increasing the adhesive force of the rear wheel to the ground, controlling the stability of the whole vehicle body and reducing the probability of overturning. When the vehicle brakes in a general condition, the opening degrees of the upstream electromagnetic valve 140 and the downstream electromagnetic valve 150 on the two shock absorbers 100 for controlling the front wheels are increased, and the damping force is reduced; thereby reducing vibration and shock due to braking.
When the received displacement signal in the displacement sensor is larger than a preset displacement value, judging that the road surface below the shock absorber 100 corresponding to the displacement sensor is uneven; and whether the piston 120 of the shock absorber 100 moves down or up is determined by the positive or negative of the displacement signal. When the vibration absorber 100 moves downwards, the downstream electromagnetic valve 150 keeps closed to reduce the damping force given the larger opening degree of the upstream electromagnetic valve 140 of the vibration absorber 100, and the vibration is absorbed by the vibration absorption spring to reduce the impact force; when the vibration is ascending, a smaller opening degree is given to the downstream solenoid valve 150 of the shock absorber 100, so that a negative pressure is generated in the lower chamber of the piston 120, and the elastic force of the damping spring is converted into the internal energy of the pressure oil, thereby damping the vibration.
And when the received displacement signals of the four displacement sensors are all smaller than a preset displacement value, judging that the vehicle runs on a smooth road. Further judging whether the vehicle runs at a high speed or at a low speed, and keeping the electromagnetic valves of the four shock absorbers 100 closed when the frame speed is lower than a preset speed value; the throttling component is utilized to provide damping force, so that the service life of the shock absorber 100 is prolonged; otherwise, the solenoid valves of the four shock absorbers 100 are controlled to maintain a preset opening.
When the vehicle turns left, the opening degree of the electromagnetic valve of the shock absorber 100 corresponding to the left wheel is increased, the damping force on the left side is reduced, and the height of the right side of the vehicle is slightly higher than that of the left side. When the vehicle turns right, the opening degree of the electromagnetic valve of the shock absorber 100 corresponding to the right wheel is increased. The design can reduce the vibration caused by turning and the probability of overturning caused by turning.
The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention, and various modifications and changes may be made by those skilled in the art. Any modification, equivalent replacement, or improvement made within the spirit and principle of the present invention should be included in the protection scope of the present invention.

Claims (4)

1. A shock absorber, comprising:
the outer cylinder is used for containing hydraulic oil and is connected with the corresponding suspension;
the piston is arranged in the outer cylinder in a sliding mode; two mounting through holes are formed in the piston;
one end of the piston rod is connected with the piston, and the other end of the piston rod is used for being connected with a corresponding frame;
the two electromagnetic valves are normally closed valves and are respectively arranged in the two installation through holes; the two electromagnetic valves are an upstream electromagnetic valve and a downstream electromagnetic valve, and when the piston moves downwards; the up-flow solenoid valve can be opened so that pressure oil can flow upward through the solenoid valve; when the piston moves upwards, the downstream electromagnetic valve can be opened, so that the pressure oil can flow downwards through the electromagnetic valve;
the throttling assembly comprises an upper conical cover, a lower conical cover, a connecting rod, a throttling spring and a limiting rod; the piston is provided with a throttling through hole;
the throttling through hole is a stepped hole and comprises a throttling large hole and a throttling small hole, the throttling large hole extends to the upper surface of the piston, and the throttling small hole extends to the lower surface of the piston; the end part of the throttling large hole is provided with a chamfer to form a conical surface;
the piston is also provided with a throttling channel, one end of the throttling channel extends to the hole wall or the bottom of the throttling large hole, and the other end of the throttling channel extends to the lower surface of the piston; the throttling channel is obliquely arranged, and the distance between the lower end of the throttling channel and the axis of the throttling small hole is greater than the radius of the lower conical cover;
the connecting rod penetrates through the throttling through hole and is arranged in the throttling small hole in a sliding mode, the upper end of the connecting rod is connected with the upper conical cover, and the lower end of the connecting rod is connected with the lower conical cover; the large end face of the upper conical cover faces upwards, and the large end face of the lower conical cover faces downwards;
the throttling spring is arranged in the throttling big hole, one end of the throttling spring is connected with the upper conical cover, and the other end of the throttling spring is connected with the bottom of the throttling big hole;
in a natural state of the throttling spring, a gap is reserved between the upper conical cover and the conical surface; a gap is reserved between the lower conical cover and the lower surface of the piston;
one end of the limiting rod is connected with the upper conical cover, and when the limiting rod and the other end of the limiting rod are abutted to the piston, a gap is reserved between the upper conical cover and the conical surface.
2. The shock absorber according to claim 1, wherein said solenoid valve comprises a compression fixed iron, a compression moving iron and a compression spring;
the compressed fixed iron is fixedly arranged in the corresponding installation through hole, the compressed moving iron is arranged in the corresponding installation through hole in a sliding manner, and the flow area of the corresponding installation through hole is correspondingly changed when the compressed moving iron slides;
and two ends of the compression spring are respectively abutted against the compression movable iron and the compression fixed iron.
3. The shock absorber according to claim 2, wherein said mounting through hole is a stepped hole including a large diameter hole and a small diameter hole; the compression moving iron and the compression fixed iron are both cylindrical, an oil passing hole is formed in the middle of the compression fixed iron, and an oil passing groove is formed in the circumferential surface of the compression moving iron; the oil passing hole and the oil passing groove extend along the axial direction of the mounting through hole;
the compression fixed iron is fixedly installed in the large-diameter hole, the compression movable iron is arranged in the large-diameter hole in a sliding mode, and the compression movable iron can block the small-diameter hole in a natural state.
4. The damper according to claim 2, wherein the two solenoid valves are installed in opposite directions, and an elastic force of the compression spring of the upstream solenoid valve is smaller than an elastic force of the compression spring of the downstream solenoid valve.
CN202011234054.6A 2020-11-07 2020-11-07 Vibration damper Active CN112406443B (en)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN202011234054.6A CN112406443B (en) 2020-11-07 2020-11-07 Vibration damper
CN202110713019.0A CN113400880B (en) 2020-11-07 2020-11-07 Vehicle and method for improving driving stability of vehicle

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
CN202011234054.6A CN112406443B (en) 2020-11-07 2020-11-07 Vibration damper

Related Child Applications (1)

Application Number Title Priority Date Filing Date
CN202110713019.0A Division CN113400880B (en) 2020-11-07 2020-11-07 Vehicle and method for improving driving stability of vehicle

Publications (2)

Publication Number Publication Date
CN112406443A CN112406443A (en) 2021-02-26
CN112406443B true CN112406443B (en) 2021-06-15

Family

ID=74780581

Family Applications (2)

Application Number Title Priority Date Filing Date
CN202011234054.6A Active CN112406443B (en) 2020-11-07 2020-11-07 Vibration damper
CN202110713019.0A Active CN113400880B (en) 2020-11-07 2020-11-07 Vehicle and method for improving driving stability of vehicle

Family Applications After (1)

Application Number Title Priority Date Filing Date
CN202110713019.0A Active CN113400880B (en) 2020-11-07 2020-11-07 Vehicle and method for improving driving stability of vehicle

Country Status (1)

Country Link
CN (2) CN112406443B (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113427959A (en) * 2021-06-25 2021-09-24 湖南翰坤实业有限公司 Adsorption equipment is kept apart to car noise
CN114772479A (en) * 2022-03-31 2022-07-22 中联重科股份有限公司 Control method for suspension system, processor and tire crane

Family Cites Families (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0550826A (en) * 1991-08-19 1993-03-02 Mazda Motor Corp Suspension device for vehicle
DE102007039215A1 (en) * 2007-08-20 2009-02-26 Volkswagen Ag Twin-tube vibration damper has third valve unit, which is designed to allow working medium to flow through from compensation chamber to another chamber and in reverse direction
CN101408235A (en) * 2007-10-08 2009-04-15 贺勍 Novel adjustable vibration damper and follow-up damp-regulating volume control method
CA2608825A1 (en) * 2007-10-26 2009-04-26 Multimatic Inc. In wheel suspension system
DE102009002260A1 (en) * 2009-04-07 2010-10-21 Zf Friedrichshafen Ag Vibration damper with a device for generating electrical energy
CN104057797B (en) * 2013-03-22 2016-03-30 刘胜 Intelligent hydraulic suspension unit and control method thereof
CN103511537B (en) * 2013-09-29 2015-08-26 安徽工程大学 A kind of variable-damping shock
CN104747650A (en) * 2015-01-21 2015-07-01 杨富云 Shock absorbing method and shock absorber thereof
CN207388788U (en) * 2017-10-31 2018-05-22 西安科技大学 A kind of damp adjustable self energizing type active suspension actuator of electric
CN107630969B (en) * 2017-10-31 2023-08-18 西安科技大学 Composite damping adjustable self-energy-supply type active suspension actuator and control method thereof
CN209083890U (en) * 2018-09-21 2019-07-09 北京长城华冠汽车科技股份有限公司 A kind of ride control shock absorber
CN111238096A (en) * 2020-03-11 2020-06-05 格力电器（合肥）有限公司 Air conditioner and throttle valve thereof
CN211764787U (en) * 2020-03-11 2020-10-27 无锡职业技术学院 Semi-active suspension system
CN111267814B (en) * 2020-04-03 2023-04-21 湖南工学院 Brake and suspension integrated pitching prevention structure and control method

Also Published As

Publication number Publication date
CN113400880A (en) 2021-09-17
CN112406443A (en) 2021-02-26
CN113400880B (en) 2022-04-01

Similar Documents

Publication Publication Date Title
US5462140A (en) Acceleration sensitive shock absorber
US5080392A (en) Suspension unit
US6119830A (en) Flow sensitive, acceleration sensitive shock absorber
KR101629307B1 (en) Nested check high speed valve
JP5519502B2 (en) shock absorber
US5598903A (en) Acceleration sensitive flow sensitive mcpherson strut
CN112406443B (en) Vibration damper
JP2016531039A (en) Rebound passive and active suspension
JP2001180245A (en) Suspension for vehicle
WO2023125925A1 (en) Shock absorber assembly and vehicle having same
CN114987134B (en) Self-adjusting automobile suspension along with road conditions
CN100392282C (en) Damping force adjustable vibration damper
CN211501444U (en) Electromagnetic valve type shock absorber with built-in hollow piston rod
JPH051712Y2 (en)
JP4050076B2 (en) Motorcycle front fork
CN220668223U (en) Train continuous damping control vibration damper
CN221665184U (en) Shock absorber with adjustable preload damping
CN218266975U (en) Single-cylinder external damping adjustable shock absorber and control valve
CN220726952U (en) Damping air bag capable of regulating resistance
CN218229279U (en) Damping and shock-absorbing integrated wheelbarrow
CN220168432U (en) Hydro-pneumatic spring and vehicle suspension system
JPH051711Y2 (en)
KR960003117B1 (en) Shock-absorber for a vehicle
JPS5926817B2 (en) Vehicle shock absorber
JP3428619B2 (en) Vehicle damping force control device

Legal Events

Date Code Title Description
PB01 Publication
PB01 Publication
SE01 Entry into force of request for substantive examination
SE01 Entry into force of request for substantive examination
GR01 Patent grant
GR01 Patent grant