CN211107439U - Gas-liquid buffer - Google Patents

Abstract

The utility model provides a gas-liquid buffer, include: a barrel; a cylinder body: partially inserted into the first barrel end; a clearance cavity is formed between the outer wall of the cylinder body and the inner wall of the cylinder body, a valve body is arranged on the outer wall of the cylinder body, and the valve body seals the clearance cavity between the valve body and the first cylinder body end to form a first liquid cavity; plunger: a cylinder body is inserted into one side of the end of the second cylinder body and can move relative to the cylinder body; an end cover is arranged at one end of the plunger positioned in the cylinder body; a piston is arranged in the plunger cavity; the end cover radially seals the inner diameter of the cylinder body, a second liquid cavity is formed between the end cover and the cylinder body, a third liquid cavity is formed between the end cover and the piston, and an air cavity is formed between the piston and the plunger; a force transmission member: is arranged on the outer side of the plunger; the force transmission component pushes the plunger piston when under pressure, and pulls the cylinder body when under tension; the second liquid cavity is respectively communicated with the first liquid cavity and the third liquid cavity. The buffer reduces the number of the liquid cavity and the air cavity, simplifies the integral structure of the gas-liquid buffer, and improves the reliability of work.

Description

Gas-liquid buffer

Technical Field

The utility model relates to a coupling buffering technical field, concretely relates to gas-liquid buffer.

Background

At present, a gas-liquid buffer is used as a main buffering energy absorption module for high-speed railways and subways, and the gas-liquid buffer has the excellent characteristics of large capacity, high energy absorption rate, capability of continuously and stably absorbing longitudinal impact kinetic energy of trains and the like, and can meet various performance requirements under the conditions of high speed, low speed and heavy load. The buffer energy-absorbing function of the gas-liquid buffer is mainly realized by the relative motion of two media, namely gas and liquid, when the buffer is pressed, the liquid medium in the buffer flows into the other liquid chamber from one liquid chamber through a fine throttling hole and a pressurizing valve, and simultaneously pushes a piston to compress gas, in the process, part of external impact kinetic energy is consumed by the friction between the liquid and the inner wall of metal, and the other part of impact energy is converted into the compression potential energy of the gas to be used as the restoring force of the buffer.

The traditional gas-liquid buffer can only realize the buffering energy-absorbing function when being impacted and compressed, and the vehicle can appear tensile and two kinds of operating modes of compression at any time in the actual operation process, and the traditional buffer does not have the buffering energy-absorbing function when the train is tensile, can only realize through drawing and pressing the shifter for the structure is complicated, and the cost is increased, and weight increase, and tensile energy-absorbing is less. Therefore, in order to meet the requirements of higher and higher comfort and energy absorption of high-speed trains, cost reduction, vehicle weight reduction and the like, a pull-press bidirectional energy absorption type gas-liquid buffer which is simple in structure and can continuously and efficiently absorb tensile and impact energy under any working condition is needed.

The utility model with publication number CN209064106U discloses a gas-liquid buffer with tension-compression bidirectional buffering energy-absorbing function, which comprises four liquid chambers and two air chambers, and when receiving pressure, the gas-liquid buffer realizes buffering energy-absorbing through the cooperation of the first air chamber and the first liquid chamber and the second liquid chamber; when the vehicle is under tension, the second air cavity is matched with the third liquid cavity and the fourth liquid cavity to achieve buffering and energy absorption. The gas-liquid buffer is complicated in structure due to the arrangement of excessive liquid cavities and air cavities.

SUMMERY OF THE UTILITY MODEL

An object of the utility model is to provide a simple structure, stable performance can all play the gas-liquid buffer of cushioning effect when receiving pulling force or pressure.

In order to achieve the above object, the utility model adopts the following technical scheme:

a gas-liquid damper comprising:

barrel: comprises a first cylinder end and a second cylinder end;

a cylinder body: part of the first cylinder end is inserted into the first cylinder end and can move relative to the cylinder; a clearance cavity is formed between the outer wall of the cylinder body and the inner wall of the cylinder body, a valve body is arranged on the outer wall of the cylinder body, and the valve body seals the clearance cavity between the valve body and the first cylinder body end to form a first liquid cavity;

plunger: a cylinder body is inserted into one side of the end of the second cylinder body and can move relative to the cylinder body; an end cover is arranged at one end of the plunger positioned in the cylinder body; a piston is arranged in the plunger cavity; the end cover radially seals the inner diameter of the cylinder body, a second liquid cavity is formed between the end cover and the cylinder body, a third liquid cavity is formed between the end cover and the piston, and an air cavity is formed between the piston and the plunger;

a force transmission member: the plunger is arranged on the outer side of the plunger, can move relative to the plunger and can be linked with the barrel; the force transmission part pushes the plunger piston when being stressed and pulls the cylinder body when being stressed by tensile force;

the second liquid cavity is respectively communicated with the first liquid cavity and the third liquid cavity.

Preferably, the force transmitting member is connected to the cylinder.

Preferably, the cross-sectional area of the first fluid chamber is smaller than the cross-sectional area of the second fluid chamber.

Preferably, a first fluid channel communicated with the second fluid cavity and the third fluid cavity is arranged on the end cover, the first fluid channel comprises a first branch and a second branch, a first conduction assembly is arranged on the first branch, a second conduction assembly is arranged on the second branch, and the first conduction assembly and the second conduction assembly are opposite in pressed conduction direction.

Preferably, the first branch and the second branch comprise main passages converging to a direction toward the second liquid chamber;

the first conduction assembly is a pressure increasing valve, the end surface of one side of the pressure increasing valve, which faces the second liquid cavity, is a conical surface, and the matching part of the fluid channel and the pressure increasing valve is a conical surface structure matched with the conical surface of the pressure increasing valve;

the second pass assembly is a check valve configured to open when the third fluid chamber pressure is greater than the second fluid chamber pressure.

Preferably, a second fluid channel is arranged along the side wall of the cylinder body, and the second fluid channel is communicated with the first fluid cavity and the second fluid cavity.

Preferably, the end cover is of a reducing structure, and a gap exists between one end of the end cover, which is far away from the plunger, and the inner wall of the cylinder body, so that the second fluid channel is communicated with the second liquid cavity in the movement process of the end cover.

Preferably, the end of the valve body facing the first cylinder end includes a notch section that covers the second fluid passage in the longitudinal direction.

Preferably, the force transmission component is inserted into the gap cavity, the force transmission component extends towards the inner wall of the cylinder body to form a first extending part, the cylinder body extends towards the force transmission component to form a second extending part, and the first extending part and the second extending part form a movement matching structure between the force transmission component and the cylinder body.

Preferably, the first cylinder end extends towards the cylinder outer wall to form a third extending portion, the cylinder outer wall further extends towards the outer side to form a fourth extending portion, and the third extending portion and the fourth extending portion form a movement matching structure between the cylinder and the cylinder.

The utility model provides a gas-liquid buffer's beneficial effect lies in:

the utility model provides a gas-liquid buffer can all play the cushioning effect when receiving pulling force or pressure. Compared with the pull-press conversion type gas-liquid buffer in the prior art, the utility model discloses reduce the quantity of sap cavity and air cavity, simplified the holistic structure of gas-liquid buffer, improved and changed into the reliability of energy absorption work.

Drawings

In order to more clearly illustrate the technical solutions of the embodiments of the present invention, the drawings required for the embodiments or the prior art descriptions will be briefly introduced below, and it is obvious that the drawings in the following description are only some embodiments of the present invention, and it is obvious for those skilled in the art to obtain other drawings without inventive labor.

FIG. 1 is a schematic structural view of a first embodiment of a gas-liquid damper;

FIG. 2 is a schematic view showing a configuration of a first embodiment of a gas-liquid damper in a compressed state;

FIG. 3 is a schematic structural view of a first embodiment of a gas-liquid damper in a stretched state;

FIG. 4 is a schematic structural diagram of a second embodiment of a gas-liquid damper;

FIG. 5 is a schematic view of a second embodiment of a gas-liquid damper in a compressed state;

FIG. 6 is a schematic structural view showing a stretched state of a third embodiment of the air-liquid damper;

FIG. 7 is a partial enlarged view of a valve body portion of the gas-liquid damper;

wherein, in the figures, the respective reference numerals:

1-cylinder, 101-second extension, 102-third extension;

2-cylinder, 201-fourth extension, 202-tank liquid hole, 203-second fluid channel;

3-plunger, 301-air hole;

4-a force transmitting member, 401-a first extension;

5-end cap, 501-first fluid channel;

6-valve body, 601-valve body gap section;

7-a pressure increasing valve;

8-a piston;

9-a one-way valve;

10-an air cavity;

11-a first fluid chamber;

12-a second fluid chamber;

13-a third fluid chamber;

14-taper gap;

15-second air cavity.

Detailed Description

In order to make the technical problem, technical solution and advantageous effects to be solved by the present invention more clearly understood, the following description is given in conjunction with the accompanying drawings and embodiments to illustrate the present invention in further detail. It should be understood that the specific embodiments described herein are merely illustrative of the invention and are not intended to limit the invention.

It will be understood that when an element is referred to as being "disposed on," "connected to" another element, it can be directly on the other element or be indirectly on the other element. When an element is referred to as being "connected to" another element, it can be directly connected to the other element or be indirectly connected to the other element.

It will be understood that the terms "upper", "lower", "vertical", "top", "bottom", "inner", "outer", and the like, are used in an orientation or positional relationship indicated in the drawings for convenience in describing the present invention and to simplify the description, and do not indicate or imply that the device or element so referred to must have a particular orientation, be constructed and operated in a particular orientation, and thus should not be construed as limiting the invention.

It should be noted that the terms "first", "second", "third" and "fourth" are used for descriptive purposes only and are not intended to imply relative importance.

The utility model provides an air liquid buffer, this air liquid buffer can be applied to various types of vehicles for the collision energy of buffering absorption vehicle plays the effect of protection vehicle safety.

The structure of the gas-liquid buffer comprises:

barrel 1: comprises a first cylinder end and a second cylinder end; both ends of the cylinder body 1 are of an open structure;

the cylinder body 2: one end of the cylinder body is open, the other end of the cylinder body is closed, the open end of the cylinder body is inserted into the cylinder body 1 at one side of the first cylinder body end and can move relative to the cylinder body 1, and the first cylinder body end is tightly matched with the outer wall of the cylinder body 2 to form a closed structure; a clearance cavity is formed between the outer wall of the cylinder body 2 and the inner wall of the cylinder body 1, a valve body 6 is arranged on the outer wall of the cylinder body 2, the valve body 6 seals the clearance cavity between the valve body and the first cylinder body end, and a first liquid cavity 11 is formed among the valve body 6, the outer wall of the cylinder body and the first cylinder body end. The valve body 6 is in threaded connection with the cylinder body 2, and the relative position of the valve body and the cylinder body can be adjusted. Besides the threaded connection, the two can also be fixedly connected.

Plunger 3: one end of the cylinder body is open, the other end of the cylinder body is closed, the open end of the cylinder body is inserted into the cylinder body 2 at one side of the second cylinder body end, and the cylinder body 2 and the cylinder body can move relatively; an end cover 5 is arranged at one end of the plunger 3 positioned in the cylinder body 2, and the end cover 5 closes the opening end of the plunger 3; a piston 8 is arranged in the plunger cavity, and the piston 8 can freely move in the plunger cavity; the end cover 5 further radially seals the inner cavity of the cylinder body 2, a second liquid cavity 12 is formed between the end cover 5 and the cylinder body 2, a third liquid cavity 13 is formed between the end cover 5 and the piston 3, and an air cavity 10 is formed between the piston 8 and the closed end of the plunger 3. An air hole 301 is formed in the closed end of the plunger 3, and the air hole 301 is communicated with the outside and the air cavity 10 so as to inflate the air cavity 10; a tank liquid hole 202 is formed along the side wall of the cylinder body 2, and the tank liquid hole 202 communicates with the outside and the second liquid chamber 12 so as to flush liquid into the second liquid chamber 12.

Force transmission member 4: the plunger is arranged on the outer side of the plunger 3, namely one side of the closed end of the plunger, can move relative to the plunger 3 and can be linked with the barrel 1; the force transmission member 4 pushes the plunger 3 in the direction of the inside of the cylinder 2 when receiving pressure, and pulls the cylinder 1 in the direction of the outside of the cylinder 2 when receiving tension.

The second liquid chamber 12 communicates with the first liquid chamber 11 and the third liquid chamber 13, respectively. Thus, a pull-press linkage buffering energy-absorbing structure is formed.

Specifically, the communication between the second liquid chamber 12 and the third liquid chamber 13 is achieved by the following structure. The end cover 5 is provided with a first fluid channel 501 communicated with the second fluid cavity 12 and the third fluid cavity 13, the first fluid channel 501 comprises a first branch and a second branch, the first branch and the second branch are Y-shaped in the embodiment, the first branch and the second branch are converged into a main channel, a port of the main channel is arranged at the end of the second fluid cavity 12, a port of the branch is arranged at the end of the third fluid cavity 13, one of the branches is provided with a booster valve 7, the other branch is provided with a check valve 8, and the check valve 8 is set to be opened when the pressure of the third fluid cavity 13 is greater than the pressure of the second fluid cavity 12.

In order to ensure better matching between the pressure increasing valve 7 and the first fluid channel 501, the end surface of one side of the pressure increasing valve 7 facing the second fluid cavity 12 is a conical surface, and the matching part of the first fluid channel 501 and the pressure increasing valve 7 is provided with a conical surface structure matched with the conical surface of the pressure increasing valve. This configuration ensures a more intimate fit between the booster valve 7 and the first fluid channel 501, and prevents fluid from flowing between the two fluid chambers under abnormal conditions. The booster valve 7 can amplify damping in the fluid flowing process, and the booster ratio of the booster valve 7 can be designed according to the buffering requirement during application.

In this way, when the pressure of the second liquid chamber 12 is higher than the pressure of the third liquid chamber 13, the tapered end surface 14 between the pressure increasing valve 7 and the first fluid passage 501 is opened, and the second liquid chamber 12 and the third liquid chamber 13 are communicated; when the pressure of the third liquid cavity 13 is higher than the pressure of the second liquid cavity, the conical end surface 14 between the booster valve 7 and the first fluid channel 501 is closed, but the check valve 8 is automatically opened, the liquid in the third liquid cavity 13 enters the second liquid cavity 12 through the check valve 8, and the two liquid cavities automatically recover to a pressure balance state.

Specifically, the communication between the first liquid chamber 11 and the second liquid chamber 12 is achieved by the following structure. The second fluid channel 203 is arranged along the side wall of the cylinder body 2, the second fluid channel 203 is communicated with the first liquid cavity 11 and the second liquid cavity 12, the second fluid channel 203 is a through hole penetrating through the side wall of the cylinder body, and the aperture/number of the second fluid channel 203 can be adjusted according to the working condition.

The gas-liquid damper is mounted on a vehicle and is subjected to an impact tensile force or a compression force, and both the cylinder 2 side and the force transmission member 4 side may serve as force application ends.

When the gas-liquid damper is subjected to an impact force, the movement of the end cap 5 may block the second fluid passage 203, so that the fluid cannot flow between the second fluid chamber 12 and the first fluid chamber 11. Premature plugging of the second fluid passage 203 by the end cap 5 may affect the pressure balance between the first fluid chamber 11 and the second fluid chamber 12 during the cushioning energy absorption process. To solve this problem, the structure of the end cap 5 is designed as follows. The end cover 5 is of a reducing structure, and a gap exists between one end of the end cover 5, which is far away from the plunger 3, and the inner wall of the cylinder body 2, and the gap can ensure that the end cover 5 does not block the second fluid channel 203, so that the second fluid channel 203 is communicated with the second liquid cavity 12 in the movement process of the end cover 5. Specifically, the whole end cover 5 can be divided into three parts according to different diameters, one part is an installation part of the end cover 5 and the port of the plunger 3, and the part needs to ensure that the end cover 5 seals the port of the plunger 3; the second part is a matching section of the end cover 5 and the cylinder body 2, and the second part needs to ensure that the end cover can form a seamless matching with the cylinder body 2 so as to distinguish the second liquid cavity 12 from the third liquid cavity 13; the diameter of the third portion, that is, the end portion of the end cover 5 facing the second liquid chamber 12, is smaller than that of the second portion, so as to ensure that a gap is formed between the end cover 5 and the inner wall of the cylinder 2, and the gap can be used as a liquid flow path, so that when the gas-liquid damper operates, liquid can flow to the first liquid chamber 11 through the second liquid chamber 12 before the end cover 5 blocks the second fluid passage 203.

When the gas-liquid damper is pulled, the cylinder 1 is pulled by the force transmission member or the cylinder 2 is pulled and the cylinder 1 moves relatively, and the movement of the cylinder 1 may cross the second fluid passage 203. To solve this problem, the structure of the valve body 6 is designed as follows. With particular reference to fig. 7, the end of the valve body 6 facing the first cylinder end comprises a notched section 601, the notched section 601 lengthwise covering the second fluid passage 203. Because the valve body 6 is fixedly arranged on the cylinder body 2, the cylinder body 1 is stopped by the valve body 6 after contacting with the valve body 6 in the moving process, so that the cylinder body 1 can be prevented from further moving to cross the second fluid channel 203.

The force transmission member 4 is a key component for the operation of the gas-liquid damper, and functions to transmit the tensile force or the pressure force on the side of the force transmission member 4. In this embodiment, the force transmission member 4 is in the shape of an end cap, and covers the closed end of the plunger 3. A second air cavity 15 is formed among the valve body 6, the second end of the cylinder body and the force transmission part 4, and the second air cavity 15 is communicated with the outside atmosphere and does not participate in the tension and compression buffering energy absorption work. The following two designs are made with respect to the fitting structure between the force transmission member 4 and the cylinder 1.

A first embodiment structure is described with reference to fig. 1 to 3.

The force transmission component 4 is inserted into a clearance cavity between the cylinder body 2 and the cylinder body 1, the force transmission component 4 extends towards the inner wall direction of the cylinder body 1 to form a first extension part 401, the cylinder body 1 extends towards the force transmission component 4 to form a second extension part 101, and the first extension part 401 and the second extension part 101 are matched to form an interlocking structure between the force transmission component 4 and the cylinder body 1.

The first cylinder end extends towards the direction of the outer wall of the cylinder 2 to form a third extending part 102, the outer wall of the cylinder 2 further extends outwards to form a fourth extending part 204, and the third extending part 102 and the fourth extending part 204 are matched to form a stop structure between the cylinder 1 and the cylinder 2.

Hereinafter, the operation principle of the gas-liquid damper will be described in detail.

In the initial state, oil is filled into the liquid cavity pipe, and gas is filled into the gas cavity pipe. The air cavity 10 space and the initial filling pressure are set as required. During filling, hydraulic oil is firstly filled into the second liquid cavity 12 through the liquid filling hole 202 and enters the first liquid cavity 11 through the second liquid channel; when the pressure of the second liquid cavity 12 is larger than the pressure of the third liquid cavity 13, the conical surface gap 14 between the booster valve 7 and the first fluid channel is opened, hydraulic oil smoothly flows into the third liquid cavity 13 through the first liquid cavity 11, and the pressure intensity of the three liquid cavities is equal when the oil filling is finished. Then, the air is filled from the air hole 301, and when the air pressure is increased to a certain degree, the tapered gap 11 is closed, and the first liquid chamber 11, the second liquid chamber 12 and the third liquid chamber 13 are separated.

a compression process

Referring to fig. 2, when the damper is compressed by an external force, i.e., the force transmission member 4 is compressed or the cylinder 2 is compressed, i.e., when the damper is compressed by an external force, the plunger 3 enters the cylinder 2, and the volume of the first liquid chamber 11 is not changed because the cylinder 2 moves synchronously with the cylinder 1 and the valve body 6 during compression. At this time, the plunger 3 pushes the end cover 5 to move, the second liquid chamber 12 is compressed, the pressure in the second liquid chamber 12 is increased, and the hydraulic oil in the second liquid chamber 12 flows into the 3 rd liquid chamber through the pressure increasing valve 7. Before the compression process is started, the pressure of the third liquid cavity 13 comes from the filling pressure, and in the compression process, namely, the pressure of the second liquid cavity 12 is successfully enabled to be higher than that of the third liquid cavity 13 through the pressurization function of the pressurization valve 7, so that the conical surface gap 14 is forced to be opened, the amount of the third liquid cavity oil 13 is increased, the pressure is increased, the piston 8 is pushed to move towards the air cavity 10, and the air in the air cavity 10 is compressed. In this process, since the volume of the first liquid chamber 11 is not changed, no fluid flow is generated between the first liquid chamber 11 and the second liquid chamber 12.

b compression recovery procedure

As described above, after the pressure-generated buffer is pressed to the stroke, the compression energy stored in the air cavity 10 needs to be released, the difference between the left and right stressed areas of the end cover 5 and the plunger 3 in the environment of the hydraulic oil pressure of the second liquid cavity 12 makes the plunger 3 forced to move back in the axial direction, the check valve 9 is opened, the second liquid cavity 12 is in undamped communication with the third liquid cavity 13, and the plunger 3 is smoothly pushed back to the original position.

c stretching process

Referring to fig. 3, when the damper is stretched by an external force, a tensile force is applied to the force transmission member 4 or the cylinder 2. The cylinder body 2 is separated from the cylinder body 1, the volume of the No. 2 liquid cavity is reduced, the pressure intensity is increased, the hydraulic oil in the liquid cavity flows into the second liquid cavity 12 through the second fluid channel 203, the volume of the second liquid cavity 12 is unchanged because the cylinder body 2, the plunger 3 and the valve body 6 move synchronously during stretching, and the hydraulic oil flowing into the second liquid cavity 12 flows into the third liquid cavity 13 through the booster valve 7. Before stretching begins, the pressure of the third liquid cavity 13 comes from filling pressure, namely, the pressure of the second liquid cavity 12 is successfully enabled to be higher than the pressure of the third liquid cavity 13 through the pressurizing function of the pressurizing valve 7, the conical surface gap 14 is forced to be opened, the oil quantity of the third liquid cavity 13 is increased, and the piston 8 is pushed to move towards the gas cavity direction to compress gas.

d process of stretch recovery

As mentioned above, when the buffer is stretched to the end of travel, the compression energy stored in the air cavity needs to be released, the difference between the left and right stressed areas of the inner end cap 5 and the plunger 3 in the environment of the pressure of the hydraulic oil in the 1 st hydraulic cavity makes the plunger 3 forced to move back in the axial direction, the one-way valve 9 is opened, the 1 st and 3 rd hydraulic cavities are not in damping communication, the hydraulic oil flows back to the 2 nd hydraulic cavity from the 3 rd hydraulic cavity through the 1 st hydraulic cavity, and the cylinder body 2 is smoothly pushed back to the original position.

A second structure of implementation, refer to fig. 4 to 6.

The connection between the force-transmitting member 4 and the second cylinder 101 end of the cylinder 1 may be a fixed or a detachable connection. In this embodiment, a threaded connection is used. With this embodiment, the force transfer member 4 and the cylinder 1 will move synchronously when the damper is under tension or compression.

The utility model discloses the technical scheme characteristic that takes is unanimous with former scheme characteristic, and 3 sap cavity, 1 air cavities are unanimous with former scheme. The difference is that in the alternative, the force transmission part 4 and the cylinder body 1 are in threaded connection, a stop structure is not arranged between the cylinder body 2 and the cylinder body 1, the cylinder body 2 and the cylinder body 1 can move mutually in the stretching and compressing processes, and the sectional area of the second liquid cavity 12 is larger than that of the first liquid cavity 11. Unlike the first embodiment, the volume of the first fluid chamber 11 changes during the pulling and pressing movement, and thus a fluid flow is generated between the first fluid chamber 11 and the second fluid chamber 12. Here, it should be noted that, under the same operating condition, if the volume change of the fluid in the first oil chamber 11 is larger than the volume change of the fluid in the second oil chamber 12, the fluid in the second oil chamber 12 cannot flow into the third oil chamber 13 during the compression process, and the energy absorption and buffering effect cannot be ensured.

The pressurizing function and the filling principle mechanism of the alternative scheme are consistent with those of the original scheme, and repeated description is omitted.

a compression process

Referring to fig. 5, when the buffer is compressed by an external force, that is, the force transmission part 4 or the cylinder body 2 is under pressure, the plunger 3 enters the cylinder body 2, the cylinder body 2 and the valve body 6 move synchronously during compression, but are separated from the cylinder body 1, and because the sectional area of the second liquid chamber 12 is larger than that of the first liquid chamber 11, the volume of the first liquid chamber 11 is continuously increased and the pressure of the first liquid chamber 11 is reduced during compression, so that a small part of hydraulic oil in the second liquid chamber 12 flows into the first liquid chamber 11, and most of hydraulic oil flows into the third liquid chamber 13 through the booster valve 7. Before compression begins, the pressure of the third liquid cavity 13 comes from filling pressure, namely, the pressure of the second liquid cavity 12 is successfully enabled to be higher than that of the third liquid cavity 13 through the pressurization function of the pressurization valve 7, the conical surface gap 11 is forced to be opened, the oil quantity of the third liquid cavity 13 is increased, the piston 8 is pushed to move towards the gas cavity, and gas in the gas cavity 10 is compressed.

b compression recovery procedure

When the external force disappears, as mentioned above, after the buffer is pressed to the stroke and is moved, the compression energy stored in the air cavity 10 needs to be released, the difference between the left and right stressed areas of the end cover 5 and the plunger 3 in the environment of the pressure of the hydraulic oil in the second liquid cavity 12 makes the plunger 3 forced to move back along the axial direction, the one-way valve 9 is opened, the second liquid cavity 12 and the third liquid cavity 13 are communicated without damping, and the plunger 3 is smoothly pushed back to the original position.

The stretching process and the stretch-recovery process of the buffer in this alternative are the same as those in the first embodiment, and will not be described repeatedly.

In comparison with the first embodiment, by connecting the force transmission member 4 to the cylinder 1, the return damping at the time of recovery after the shock absorber is compressed can be reduced.

Specifically, the following description is provided: in this embodiment, when the shock absorber is compressed to a certain stroke and is suddenly stretched by an external force, the force transmission member 4 is screwed into the cylinder 1, and the shock absorber immediately throttles through the second fluid passage 203, so that the shock absorbing effect is instantly achieved, and the shock absorbing effect is not started after the shock absorber is connected with the cylinder 1 after an idle stroke is first performed as in the first embodiment. In addition, when the buffer is compressed, the length of the plunger 3 can be shortened and the air cavity space can be reduced through the shunting action of the first liquid cavity 11 to the second liquid cavity 12, so that the total length of the buffer can be shortened, the compression and the stretching of a larger stroke can be realized, and more stretching and impact energy can be absorbed.

The utility model provides a gas-liquid buffer can all exert buffering energy-absorbing effect when receiving pulling force and pressure. Compared with the gas-liquid buffer in the prior art, the number of the liquid cavity and the gas cavity is reduced, the integral structure of the gas-liquid buffer is simplified, and the reliability of the energy absorption work can be improved.

The above description is only exemplary of the present invention and should not be taken as limiting the scope of the present invention, as any modifications, equivalents, improvements and the like made within the spirit and principles of the present invention are intended to be included within the scope of the present invention.

Claims (10)

1. A gas-liquid damper, comprising:

barrel: comprises a first cylinder end and a second cylinder end;

a cylinder body: part of the first cylinder end is inserted into the first cylinder end and can move relative to the cylinder; a clearance cavity is formed between the outer wall of the cylinder body and the inner wall of the cylinder body, a valve body is arranged on the outer wall of the cylinder body, and the valve body seals the clearance cavity between the valve body and the first cylinder body end to form a first liquid cavity;

plunger: a cylinder body is inserted into one side of the end of the second cylinder body and can move relative to the cylinder body; an end cover is arranged at one end of the plunger positioned in the cylinder body; a piston is arranged in the plunger cavity; the end cover radially seals the inner diameter of the cylinder body, a second liquid cavity is formed between the end cover and the cylinder body, a third liquid cavity is formed between the end cover and the piston, and an air cavity is formed between the piston and the plunger;

a force transmission member: the plunger is arranged on the outer side of the plunger, can move relative to the plunger and can be linked with the barrel; the force transmission part pushes the plunger piston when being stressed and pulls the cylinder body when being stressed by tensile force;

the second liquid cavity is respectively communicated with the first liquid cavity and the third liquid cavity.

2. The gas-liquid damper according to claim 1, characterized in that: the force transmission component is connected with the cylinder body.

3. The gas-liquid damper as claimed in claim 2, wherein: the cross-sectional area of the first fluid chamber is smaller than the cross-sectional area of the second fluid chamber.

4. The gas-liquid damper according to claim 1, characterized in that: the end cover is provided with a first fluid channel communicated with the second fluid cavity and the third fluid cavity, the first fluid channel comprises a first branch and a second branch, a first conduction assembly is arranged on the first branch, a second conduction assembly is arranged on the second branch, and the first conduction assembly and the second conduction assembly are opposite in pressed conduction direction.

5. The gas-liquid damper as claimed in claim 4, wherein: the first branch and the second branch comprise main passages converging to form a main passage facing the second liquid cavity;

the first conduction assembly is a pressure increasing valve, the end surface of one side of the pressure increasing valve, which faces the second liquid cavity, is a conical surface, and the matching part of the fluid channel and the pressure increasing valve is a conical surface structure matched with the conical surface of the pressure increasing valve;

the second pass assembly is a check valve configured to open when the third fluid chamber pressure is greater than the second fluid chamber pressure.

6. The gas-liquid damper according to claim 1, characterized in that: and a second fluid channel is arranged along the side wall of the cylinder body and is communicated with the first liquid cavity and the second liquid cavity.

7. The gas-liquid damper as claimed in claim 6, wherein: the end cover is of a reducing structure, and a gap exists between one end of the end cover, which is far away from the plunger, and the inner wall of the cylinder body, so that the second fluid channel is communicated with the second liquid cavity in the movement process of the end cover.

8. The gas-liquid damper as claimed in claim 6, wherein: the end of the valve body facing the first cylinder end comprises a notch section, and the notch section covers the second fluid channel along the length direction.

9. The gas-liquid damper according to claim 1, characterized in that: the force transmission component is inserted into the clearance cavity, the force transmission component extends towards the inner wall direction of the cylinder body to form a first extension part, the cylinder body extends towards the force transmission component to form a second extension part, and the first extension part and the second extension part form a movement matching structure between the force transmission component and the cylinder body.

10. The gas-liquid damper as claimed in claim 9, wherein: the first cylinder end extends towards the cylinder body outer wall to form a third extending portion, the cylinder body outer wall further extends towards the outer side to form a fourth extending portion, and the third extending portion and the fourth extending portion form a movement matching structure between the cylinder body and the cylinder body.

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