CN212959640U

CN212959640U - Hydro-pneumatic spring

Info

Publication number: CN212959640U
Application number: CN202020210083.8U
Authority: CN
Inventors: 陈轶杰; 韩小玲; 高晓东; 张亚峰; 徐梦岩; 杜甫; 王乐; 李宝强
Original assignee: China North Vehicle Research Institute
Current assignee: China North Vehicle Research Institute
Priority date: 2020-02-25
Filing date: 2020-02-25
Publication date: 2021-04-13
Anticipated expiration: 2030-02-25

Abstract

The utility model discloses a hydro-pneumatic spring belongs to hydraulic machine technical field. The upper end of the cylinder barrel is fixedly connected with the upper hinge, the piston rod is fixedly connected with the lower hinge, the piston rod is of a hollow structure, and an inner hole of the piston rod is machined; the large outer circle of the piston rod is matched with the inner hole of the hollow annular guide sleeve, and the guide sleeve is fixedly connected with the lower end face of the cylinder barrel through guide sleeve bolts which are circumferentially arranged; the piston rod is connected with the main piston; a radial damping valve is processed on the piston rod, the rodless cavity of the hydro-pneumatic spring is communicated with the inner hole of the piston rod, and a check valve and a normally open hole of the damping valve are used for communicating the rod cavity of the hydro-pneumatic spring and the inner hole of the piston rod; the upper hinge and the lower hinge are respectively provided with a joint bearing, and oil filling holes are processed for performing centralized lubrication on the joint bearings. The utility model has the characteristics of simple structure, bearing capacity are big, are applicable to the structure of oil-gas mixture or external energy storage ware, have wide use prospect in fields such as mining machinery.

Description

Hydro-pneumatic spring

Technical Field

The utility model relates to a hydro-pneumatic spring belongs to hydraulic machine technical field.

Background

The hydro-pneumatic suspension mainly comprises a hydro-pneumatic spring, integrates an elastic element and a damping element, has a certain guiding function on a cylinder body, requires a smaller vehicle body arrangement space, and can meet the requirement of smoothness of an engineering vehicle to the maximum extent by virtue of excellent nonlinear elastic characteristic and good vibration damping performance of the hydro-pneumatic suspension. From the view of the integral structure, the existing oil-gas suspension system applied to the engineering vehicle mainly has two types of independent type and interconnection type; from the form of the oil-gas spring, the oil-gas spring is divided into a single-air-chamber oil-gas separation type, a double-air-chamber oil-gas separation type, a multi-stage pressure type, an oil-gas mixing type and the like. Compared with other suspension systems, the hydro-pneumatic suspension has the characteristics of typical nonlinear variable rigidity and increasement, when a vehicle runs on a flat road surface, the suspension moving stroke is small, the rigidity generated by the elastic medium bearing instantaneous pressure is small, and the requirement on smoothness can be met; when the vehicle runs on the undulating ground, the elastic force changes in a nonlinear way and the rigidity is increased, so that more impact energy can be absorbed, the characteristic of high energy storage ratio per unit mass of gas is exerted, the buffer effect is effectively realized, the phenomena of direct transmission of ground excitation to the vehicle body and 'suspension breakdown' are avoided, the off-road speed of the vehicle is increased, and the maneuverability is improved.

The prior art single-cylinder type oil-gas spring generally has two typical structures, namely a sealing element is arranged on a main piston, an annular cavity is a cavity, and the sealing element is arranged at a guide sleeve of a piston rod, and the sealing element and the annular cavity both need to be provided with a separate damping valve in a cylinder barrel for damping external vibration. The first structure provides very high requirements for the finish degree, the wear resistance and other processing qualities of the inner surface of the cylinder barrel, so that the cost is greatly increased, the hydro-pneumatic spring is not suitable for being popularized on a large-cylinder-diameter hydro-pneumatic spring, and the hydro-pneumatic spring in the prior art is used on a vehicle, and the rigidity limit is arranged outside the vehicle independently, so that the failure phenomenon caused by the fact that the spring body is damaged when the compression stroke and the recovery stroke reach the limit is prevented.

SUMMERY OF THE UTILITY MODEL

In view of this, the utility model provides a hydro-pneumatic spring has simple structure, the big characteristics of bearing capacity, is applicable to the structure of oil-gas mixture or external energy storage ware, and it is spacing about having built-in, is showing and has promoted hydro-pneumatic spring's reliability of shocking resistance, directly integrates the damping valve on the piston rod wall simultaneously, has reduced the processing cost, has wide use prospect in fields such as mining machinery.

An oil-gas spring comprises a cylinder barrel, a piston rod, a guide sleeve, a main piston, a lower hinge, an upper hinge and a guide sleeve bolt; the upper end of the cylinder barrel is fixedly connected with the upper hinge through bolts, welding or threaded connection, the piston rod is fixedly connected with the lower hinge through integral forging, welding or threaded connection, the piston rod is of a hollow structure, and an inner hole of the piston rod is machined; the large outer circle of the piston rod is matched with the inner hole of the hollow annular guide sleeve, and the guide sleeve is fixedly connected with the lower end face of the cylinder barrel through guide sleeve bolts which are circumferentially arranged; the piston rod is connected with the main piston; the piston rod is provided with a radial damping valve which consists of a one-way valve and a normally open hole, the rodless cavity of the hydro-pneumatic spring is communicated with the inner hole of the piston rod, and the one-way valve and the normally open hole of the damping valve are used for communicating the rod cavity of the hydro-pneumatic spring with the inner hole of the piston rod; the upper hinge and the lower hinge are respectively provided with a joint bearing, and oil filling holes are processed for performing centralized lubrication on the joint bearings.

Furthermore, the constant through hole is formed by serially connecting a small throttling hole and a large throttling hole, wherein the small throttling hole is close to one side of the inner hole of the piston rod, and oil in the rodless cavity sequentially enters the rod cavity through the small throttling hole and the large throttling hole; the check valve is characterized in that a steel ball is added into a normally-open hole, the diameter of the steel ball is between the diameter of a small throttling hole and the diameter of a large throttling hole, the position of the steel ball is limited through the hole wall of a piston inner hole of a main piston, the steel ball is prevented from falling out of the normally-open hole, and the area of the piston inner hole covering the large throttling hole is not more than half of the cross section area of the large throttling hole.

Furthermore, a first guide belt, a first oil seal, a second guide belt and a dust ring are sequentially assembled in an inner hole of the annular guide sleeve from one side of a rod cavity of the hydro-pneumatic spring, and the first guide belt and the second guide belt are symmetrically arranged on two sides of the first oil seal and the second oil seal which are connected in series; the outer circle of the guide sleeve is provided with a static seal and a protection ring, and the protection ring is arranged on the low-pressure side in a seal groove of the static seal; the outer circle of the guide sleeve is matched with the inner hole of the cylinder barrel, so that the static seal is extruded and deformed to achieve the aim of sealing high-pressure oil; the end of the guide sleeve close to the rod cavity of the hydro-pneumatic spring is provided with a small guide excircle, the outer diameter of the small guide excircle is smaller than the inner diameter of the cylinder barrel, a guide annular cavity is formed between the small guide excircle and the inner diameter of the cylinder barrel, a piston annular boss is arranged on the end face, facing the rod cavity of the hydro-pneumatic spring, of the main piston corresponding to the small guide excircle, and when the piston rod is pulled to the longest position, the piston annular boss enters the guide annular cavity.

Further, the piston rod and the main piston with the annular structure are processed by a method of threaded connection or integral forging forming.

Furthermore, an annular end face is processed at the upper end of a piston inner hole of the main piston, and after the piston rod is assembled in the piston inner hole, the top end of the piston rod is in contact with the side face of the annular end face; a circumferential piston through hole is processed on the annular end face of the main piston, a circumferential threaded hole is processed at the top end of the piston rod which is in contact with the annular end face, and the piston through hole is aligned with the circumferential threaded hole and then fixedly connected through a piston bolt during assembly; the excircle of the main piston is provided with a guide belt.

Furthermore, a communicating oil port is machined at the upper end of the cylinder wall of the cylinder barrel, an upper limit of an annular structure is machined at one end, facing the rodless cavity of the hydro-pneumatic spring, of the upper hinge, the diameter of an outer circle of the upper limit is smaller than that of an inner hole of the cylinder barrel, an oil passing groove arranged in the circumferential direction is machined on the side wall of the upper limit, and the oil passing groove is right opposite to the communicating oil port.

Further, the inflation valve and the oil filling hole on the upper hinge are arranged on the same side of the upper hinge; an inflation valve cap is arranged at the top end of the inflation valve and connected with the upper hinge through threads.

Furthermore, an oil drainage channel is processed at the end face of the lower hinge facing the inner hole of the piston rod and is sealed by a plug.

Has the advantages that:

1. the utility model provides a hydro-pneumatic spring structure mainly changes dress piston assembly, inside core assembly such as sealed through the uide bushing of dismouting cylinder lower extreme, compares with prior art and is convenient for operate on the car, need not hang the jar promptly and wholly dismantle from the automobile body, only need the unscrewing uide bushing bolt can directly tear out inside assembly such as piston rod and piston and maintain or maintain, greatly made things convenient for the simple operation nature under the field environment, possessed fine popularization advantage.

2. The utility model provides a hydro-pneumatic spring structure has hydraulic cushion stop device through the design of structure innovation at uide bushing and main piston contact terminal surface, when the main piston pulled the longest position, and the gap throttle through the spacing production of hydraulic pressure can effectively prevent the rigidity striking of main piston and uide bushing terminal surface, has avoided appearing the piece and has leaded to the product to damage. In addition, an oil drainage channel is arranged on the lower hinge, so that oil in the cylinder barrel can be drained conveniently when the hydro-pneumatic spring is maintained on a vehicle.

3. The hydro-pneumatic spring structure provided by the utility model is characterized in that a radial damping valve is processed on a piston rod and consists of a one-way valve and a normal through hole; the check valve and the normally open hole of the damping valve are used for communicating the oil gas suspension rod cavity and the rodless cavity; the check valve can be realized by adding the steel ball into the normally-open hole, particularly, the limit function of the steel ball can be realized by structural innovation when the main piston is assembled, and the check valve has the characteristics of simple structure, low cost and suitability for mass production. In addition, experiments prove that the area of the inner hole of the piston, which covers the throttling large hole, is not more than half of the cross section area of the throttling large hole, so that the obvious throttling phenomenon of the oil liquid caused by the limit of the main piston can be effectively avoided.

4. The utility model provides a hydro-pneumatic spring structure, the plug of oil filler point on the hinge, the usefulness of deoiling down when the installation on the car, arrange in same direction with last oil filler point and the inflation valve on the hinge to towards the car outside, be convenient for maintain hydro-pneumatic spring.

Drawings

FIG. 1 is a schematic diagram of a single-oil port balanced suspension structure of an energy accumulator;

FIG. 2 is a schematic diagram of a double-oil-port balanced suspension structure of the accumulator;

FIG. 3 is a main sectional view of a hydro-pneumatic spring;

FIG. 4 is a left side view of the hydro-pneumatic spring;

FIG. 5 is a schematic view of a hydro-pneumatic spring;

FIG. 6 is a front cross-sectional view of the guide sleeve;

FIG. 7 is a left side view of the guide sleeve;

FIG. 8 is a front cross-sectional view of the master piston;

FIG. 9 is a left side view of the master piston;

FIG. 10 is a front cross-sectional view of the upper hinge;

fig. 11 is a bottom view of the upper hinge.

In the figure: 21. the oil cylinder comprises a front oil-gas spring, 22 a rear oil-gas spring, 23 a rear balance pipeline, 24 a front balance pipeline, 25 a three-way joint, 26 an energy accumulator, 27 a pipeline joint, 1 a cylinder barrel, 2 a piston rod, 3 a guide sleeve, 4 a steel ball, 5 a main piston, 6 a lower hinge, 7 an oil filling hole, 8 a plug, 9 a piston bolt, 10 a piston rod inner hole, 11 an oil drainage channel, 12 an inflation valve cap, 13 an inflation valve, 14 an upper hinge, 15 a small throttling hole, 16 a large throttling hole, 17 a guide sleeve bolt, 18 a communication oil hole, 19 a large outer circle, 20 a small outer circle, 31 a guide through hole, 32 a first guide belt, 33 a static seal, 34 a protection ring, 35 a dust ring, 36 a first oil seal, 37 an annular cavity, 38 a second guide belt, 39 a small guide outer circle, 40 a guide, 51 a piston inner hole, 52. the piston comprises an annular end face, 53 piston through holes, 54 piston annular bosses, 81 oil filling channels, 82 oil passing grooves, 84 upper hinge excircle and 85 upper limit.

Detailed Description

The present invention will be described in detail below with reference to the accompanying drawings by way of examples.

The utility model discloses a balanced oil gas suspension structure possesses extensive application prospect in mining machinery and the heavy carrier loader field of multiaxis. As shown in fig. 1 and 5, a schematic of a transversely-arranged balanced hydro-pneumatic suspension structure of an energy accumulator is provided, a communication oil port 18 of a main oil chamber of a front hydro-pneumatic spring 21 is connected with one end of a front balance pipeline 24, a communication oil port 18 of a main oil chamber of a rear hydro-pneumatic spring 22 is connected with one end of a rear balance pipeline 23, further, the other end of the front balance pipeline 24 and the other end of the rear balance pipeline 23 are connected with an oil inlet of an energy accumulator 26 through a three-way joint 25, so that balanced suspension is formed, high-pressure oil inside the front hydro-pneumatic spring 21, the rear hydro-pneumatic spring 22 and the energy accumulator 26 can flow back and forth, the energy accumulator 26 is a piston-type energy accumulator.

As shown in fig. 2 and 5, a schematic diagram of a vertically-arranged balanced hydro-pneumatic suspension structure of an energy accumulator is shown, a communication oil port 18 of a main oil chamber of a front hydro-pneumatic spring 21 is connected with one end of a front balance pipeline 24, the other end of the front balance pipeline 24 is connected with a first oil inlet of the energy accumulator 26 through a pipeline joint 27, a communication oil port 18 of a main oil chamber of a rear hydro-pneumatic spring 22 is connected with one end of a rear balance pipeline 23, the other end of the rear balance pipeline 23 is also connected with a second oil inlet of the energy accumulator 26 through a pipeline joint 27 to form a balanced suspension, high-pressure oil inside the balanced hydro-pneumatic suspension structure can flow back and forth between the front hydro-pneumatic spring 21, the rear hydro-pneumatic spring 22 and the energy accumulator 26, and the energy.

As shown in fig. 1, 2, 3 and 5, after the balance oil gas is hung on a vehicle, the oil filling hole 7 on the lower hinge 6 and the plug 8 for oil discharge are arranged in the same direction with the oil filling hole 7 on the upper hinge 14 and the inflation valve 13, and generally face the outer side of the vehicle, so that the maintenance of the oil gas spring is facilitated, and the maintenance is perpendicular to the axial direction of the oil port 18 on the oil gas spring; normally, the communication ports 18 of the front hydro-pneumatic spring 21 and the rear hydro-pneumatic spring 22 are arranged in opposite directions, wherein the communication port 18 of the front hydro-pneumatic spring 21 faces the rear direction of the vehicle, and the communication port 18 of the rear hydro-pneumatic spring 22 faces the front direction of the vehicle.

The working principle of the balanced hydro-pneumatic suspension is as follows, when the front hydro-pneumatic spring 21 is compressed, the internal pressure of the front hydro-pneumatic spring 21 tends to rise, part of high-pressure oil in the front hydro-pneumatic spring 21 enters the rear hydro-pneumatic spring 22 through a pipeline firstly, so that the internal pressure of the two hydro-pneumatic springs is balanced, other redundant oil enters the energy accumulator 26 to compress a high-pressure air chamber, the pressure is balanced by compensating the oil between the front hydro-pneumatic spring 21 and the rear hydro-pneumatic spring 22 firstly, the amount of the oil entering the energy accumulator 26 is greatly reduced compared with that of the single hydro-pneumatic spring and the energy accumulator, the limit load of the single-wheel suspension when being subjected to external impact is greatly reduced, the use environments of the suspension and an axle are effectively improved, and the reliability of chassis parts is greatly improved.

In order to ensure that oil liquid in the balanced oil-gas suspension flows smoothly and compensates each other timely, and avoid the problem of idle stroke caused by compensation delay even too large loss along the stroke under the action of impact load, the inner diameters of the front balancing pipeline 24 and the rear balancing pipeline 23 cannot be smaller than 20 mm.

The structure diagram of the hydro-pneumatic spring is shown in fig. 3-11, the upper end of the cylinder barrel 1 is fixedly connected with the upper hinge 14 through bolts, welding or threaded connection, the piston rod 2 is fixedly connected with the lower hinge 6 through integral forging, welding or threaded connection, the piston rod 2 is of a hollow structure, and a piston rod inner hole 10 is machined; the large outer circle 19 of the piston rod 2 is matched with the inner hole of the hollow annular guide sleeve 3, and the guide sleeve 3 is fixedly connected with the lower end face of the cylinder barrel 1 through guide sleeve bolts 17 which are circumferentially arranged; the piston rod 2 and the main piston 5 with the annular structure are fixedly connected together through piston bolts 9 arranged on the circumferential direction of the end surface, and what needs to be mentioned, the piston rod can also be processed by a threaded connection or integrated forging forming method; the small outer circle 20 of the piston rod 2 is matched with a piston inner hole 51 of the main piston 5, an annular end face 52 is processed at the upper end of the piston inner hole 51, the inner diameter of the annular end face 52 is equivalent to the diameter of the piston rod inner hole 10, and after the piston rod 2 is assembled into the piston inner hole 51, the top end of the piston rod is fully contacted with the side face of the annular end face 52, so that the axial limit of the main piston 5 is realized; meanwhile, a circumferential piston through hole 53 is processed on the annular end face 52 of the main piston 5, a circumferential threaded hole is processed at the top end of the corresponding piston rod 2 in contact with the annular end face 52, and the piston rod is fixedly connected through a piston bolt 9 after alignment during assembly. The outer circle of the main piston 5 is provided with a guide belt.

A radial damping valve is machined at the transition position of the large excircle 19 and the small excircle 20 of the piston rod 2 and generally consists of a check valve and a normally through hole, a rodless cavity of the hydro-pneumatic spring is communicated with the inner hole 10 of the piston rod, and the check valve and the normally through hole of the damping valve are used for communicating the rodless cavity of the hydro-pneumatic spring with the inner hole 10 of the piston rod. The constant-through hole is formed by serially connecting a small throttling hole 15 and a large throttling hole 16, wherein the small throttling hole 15 is close to one side of the inner hole 10 of the piston rod, and oil in the rodless cavity sequentially enters the annular cavity with the rod through the small throttling hole 15 and the large throttling hole 16 to generate the damping throttling effect. The check valve is characterized in that a steel ball 4 is added into a normally-open hole, the diameter of the steel ball 4 is between the diameter of a small throttling hole 15 and the diameter of a large throttling hole 16, the position of the steel ball 4 is limited through the hole wall of a piston inner hole 51 of a main piston 5, the steel ball 4 is prevented from falling out of the normally-open hole, and the area of the piston inner hole 51 covering the large throttling hole 16 is not more than half of the cross section area of the large throttling hole 16.

When the hydro-pneumatic spring piston rod 2 is compressed, the steel ball 4 is jacked up by oil, and the oil in the rodless cavity can simultaneously pass through the normally open hole and the one-way valve and enter the rod cavity; when the hydro-pneumatic spring piston rod 2 is in a recovery stretching state, the steel ball 4 is impacted downwards by oil, the throttling small hole 15 can be blocked, so that the oil can only enter the rodless cavity through the normally through hole, and then a larger damping force value is generated to attenuate the vibration from the ground.

The lower hinge 6 is equipped with a knuckle bearing and oil holes 7 are machined for centralized lubrication of the knuckle bearing. An oil drainage channel 11 is processed at the end face of the lower hinge 6 facing the inner hole 10 of the piston rod, the inner hole 10 of the piston rod is communicated with the outside and is sealed by a plug 8. When oil drainage is needed, the plug 8 is opened, and oil in the cylinder barrel can be drained conveniently due to the fact that the oil drainage channel 11 is located at the lower end of the oil-gas spring.

As shown in fig. 6-8, a first guide belt 32, a first oil seal 36, a second oil seal 37, a second guide belt 38 and a dust ring 35 are sequentially assembled in an inner hole of the annular guide sleeve 3 from a rod cavity of the hydro-pneumatic spring to the outside, a structure that two oil seals are connected in series is adopted, the guide belts are symmetrically arranged on two sides of the oil seals connected in series to enable the guide capability to be exerted to the best, a static seal 33 and a protection ring 34 are installed on the outer circle of the guide sleeve 3, and the protection ring is arranged on the low-pressure side in the seal groove; the excircle of the guide sleeve 3 is matched with the inner hole of the cylinder barrel 1, so that the static seal 33 is extruded and deformed to achieve the purpose of sealing high-pressure oil. The end, close to the rod cavity of the hydro-pneumatic spring, of the guide sleeve 3 is provided with a small guide outer circle 39, the outer diameter of the small guide outer circle is smaller than the inner hole of the cylinder barrel 1, a guide annular cavity 40 is formed between the small guide outer circle and the inner hole of the cylinder barrel 1, the end face, facing the rod cavity of the hydro-pneumatic spring, of the main piston 5 corresponding to the small guide outer circle is provided with a piston annular boss 54 in a machining mode, when the piston rod 2 is pulled to the longest position, the piston annular boss 54 enters the guide annular cavity 40, hydraulic buffering limiting is formed by squeezing oil, and rigid impact between the.

In addition, as shown in fig. 3, 5, 10 and 11, the communicating oil port 18 of the hydro-pneumatic spring is arranged on the cylinder barrel 1, in order to avoid the situation that the main piston 5 interferes with the communicating oil port 18 or even is blocked when being compressed to the limit position and the damage of a guide belt on the excircle of the main piston 5, an upper limit 85 of an annular structure is processed at one end of the upper hinge 14 facing the rodless oil chamber of the hydro-pneumatic spring, the excircle diameter of the upper limit 85 is smaller than the inner hole of the cylinder barrel 1, an annular gap for oil passing is formed between the excircle of the upper limit 85 and the inner hole of the cylinder barrel 1, an oil passing groove 82 which is circumferentially arranged is processed on the side wall of the upper limit 85, the oil passing groove 82 is opposite to the communicating oil port 18, oil in the balanced suspension pipeline can be communicated with the rodless cavity of the hydro-pneumatic spring through the annular gap and the oil passing groove 82 at the same time, so, the mutual compensation of oil between the communicated oil-gas spring and the energy accumulator is also ensured to the maximum extent, and the stability of the balanced suspension in the working at the extreme position is ensured. An inflation valve 13 is mounted on the upper hinge 14, is communicated with the rodless cavity of the hydro-pneumatic spring and is used for inflating and deflating a hydro-pneumatic medium, an inflation valve cap 12 is further arranged at the top end of the inflation valve 13 and is used for preventing the inflation valve 13 from being collided and damaged, and the inflation valve cap 12 is connected with the upper hinge 14 through threads; the upper hinge 14 is equipped with a knuckle bearing and is provided with an oil filler hole 7 for centralized lubrication of the knuckle bearing, and the inflation valve 13 and the oil filler hole 7 are generally arranged on the same side of the upper hinge 14 for convenient operation on the vehicle.

In summary, the above is only a preferred embodiment of the present invention, and is not intended to limit the scope of the present invention. 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

1. The utility model provides a hydro-pneumatic spring, includes cylinder (1), piston rod (2), uide bushing (3), main piston (5), lower hinge (6), goes up hinge (14), uide bushing bolt (17), its characterized in that: the upper end of the cylinder barrel (1) is fixedly connected with the upper hinge (14) through bolts, welding or threaded connection, the piston rod (2) is fixedly connected with the lower hinge (6) through integral forging, welding or threaded connection, the piston rod (2) is of a hollow structure, and a piston rod inner hole (10) is machined; the large outer circle (19) of the piston rod (2) is matched with the inner hole of the hollow annular guide sleeve (3), and the guide sleeve (3) is fixedly connected with the lower end face of the cylinder barrel (1) through guide sleeve bolts (17) which are circumferentially arranged; the piston rod (2) is connected with the main piston (5); a radial damping valve is processed on the piston rod (2) and consists of a one-way valve and a normally open hole, a rodless cavity of the hydro-pneumatic spring is communicated with the inner hole (10) of the piston rod, and the one-way valve and the normally open hole of the damping valve are used for communicating the rodless cavity of the hydro-pneumatic spring with the inner hole (10) of the piston rod; the upper hinge (14) and the lower hinge (6) are respectively provided with a joint bearing, and an oil filling hole (7) is machined for performing centralized lubrication on the joint bearings.

2. The hydrocarbon spring of claim 1, wherein: the constant-through hole is formed by connecting a small throttling hole (15) and a large throttling hole (16) in series, wherein the small throttling hole (15) is close to one side of the inner hole (10) of the piston rod, and oil in the rodless cavity sequentially enters the rod cavity through the small throttling hole (15) and the large throttling hole (16); the check valve is characterized in that a steel ball (4) is added into a normally-open hole, the diameter of the steel ball (4) is between the diameter of a small throttling hole (15) and the diameter of a large throttling hole (16), the position of the steel ball is limited through the hole wall of a piston inner hole (51) of a main piston (5), the steel ball (4) is prevented from falling out of the normally-open hole, and the area of the piston inner hole (51) covering the large throttling hole (16) is not more than half of the cross-sectional area of the large throttling hole (16).

3. The hydrocarbon spring of claim 1, wherein: a first guide belt (32), a first oil seal (36), a second oil seal (37), a second guide belt (38) and a dust ring (35) are sequentially assembled in an inner hole of the annular guide sleeve (3) from one side of a rod cavity of the hydro-pneumatic spring, and the first guide belt and the second guide belt are symmetrically arranged on two sides of the first oil seal (36) and the second oil seal (37) which are connected in series; a static seal (33) and a protective ring (34) are arranged at the excircle of the guide sleeve (3), and the protective ring (34) is arranged at the low-pressure side in a seal groove of the static seal (33); the excircle of the guide sleeve (3) is matched with the inner hole of the cylinder barrel (1), so that the static seal (33) is extruded and deformed to achieve the purpose of sealing high-pressure oil; a small guide outer circle (39) is machined at one end, close to a rod cavity of the hydro-pneumatic spring, of the guide sleeve (3), the outer diameter of the small guide outer circle is smaller than an inner hole of the cylinder barrel (1), a guide annular cavity (40) is formed between the small guide outer circle and the inner hole of the cylinder barrel (1), a piston annular boss (54) is machined on the end face, facing the rod cavity of the hydro-pneumatic spring, of the main piston (5) corresponding to the guide outer circle, and when the piston rod (2) is pulled to the longest position, the piston annular boss (54) enters the guide.

4. The hydrocarbon spring of claim 1, wherein: the piston rod (2) and the main piston (5) with the annular structure are processed by a method of threaded connection or integral forging forming.

5. The hydrocarbon spring of claim 1, wherein: an annular end face (52) is machined at the upper end of a piston inner hole (51) of the main piston (5), and after the piston rod (2) is assembled into the piston inner hole (51), the top end of the piston rod is contacted with the side face of the annular end face (52); a circumferential piston through hole (53) is processed on the annular end face (52) of the main piston (5), a circumferential threaded hole is processed at the top end of the piston rod (2) which is in contact with the annular end face (52), and the piston through hole (53) is aligned with the circumferential threaded hole and then fixedly connected through a piston bolt (9) during assembly; the excircle of the main piston (5) is provided with a guide belt.

6. The hydrocarbon spring of claim 1, wherein: the oil cylinder is characterized in that a communicating oil port (18) is machined at the upper end of the cylinder wall of the cylinder barrel (1), an upper limit (85) of an annular structure is machined at one end, facing an oil-gas spring rodless cavity, of an upper hinge (14), the outer circle diameter of the upper limit (85) is smaller than an inner hole of the cylinder barrel (1), an oil passing groove (82) which is circumferentially arranged is machined on the side wall of the upper limit (85), and the oil passing groove (82) is right opposite to the communicating oil port (18).

7. The hydrocarbon spring of claim 1, wherein: the inflation valve (13) and the oil filling hole (7) on the upper hinge (14) are arranged on the same side of the upper hinge (14); an inflation valve cap (12) is further arranged at the top end of the inflation valve (13), and the inflation valve cap (12) is connected with the upper hinge (14) through threads.

8. The hydrocarbon spring of claim 1, wherein: an oil drainage channel (11) is processed at the end face of the lower hinge (6) facing the inner hole (10) of the piston rod and is sealed by a plug (8).