CN219954054U - Single-cylinder oil-gas mixed spring with variable damping - Google Patents

Abstract

The utility model discloses a damping-variable single-cylinder oil-gas hybrid spring, which belongs to the technical field of hydraulic machinery and comprises a cylinder barrel, a guide sleeve, a piston rod and a piston; wherein, one end of the cylinder barrel is closed and provided with an upper connecting piece, and the other end is open and provided with a guide sleeve; one end of the piston rod is closed and provided with a lower connecting piece, the other end of the piston rod is open and provided with a piston, and the piston rod is coaxially arranged in the inner cavity of the cylinder barrel through a guide sleeve; the side wall of the piston rod is provided with an orifice and a normal through hole, and a sphere is arranged in the orifice; the piston limits the sphere to move in the orifice; when the piston rod is in the compression limit position, the normal through hole is positioned outside the guide sleeve, and after the piston rod stretches to enable the normal through hole to completely enter the guide sleeve, a gap exists between the piston and the guide sleeve. The damping-variable single-cylinder oil-gas hybrid spring can ensure that the piston and the guide sleeve do not generate rigid impact, and avoid the problem that the service life of the oil-gas spring is influenced by the rigid impact.

Description

Single-cylinder oil-gas mixed spring with variable damping

Technical Field

The utility model belongs to the technical field of hydraulic machinery, and particularly relates to a damping-variable single-cylinder oil-gas hybrid spring.

Background

The hydro-pneumatic spring is mainly divided into a single cylinder hydro-pneumatic separation type, a double cylinder hydro-pneumatic separation type, a multi-stage pressure type, a single cylinder hydro-pneumatic mixing type and the like. Compared with other spring types, the hydro-pneumatic spring has the characteristics of typical nonlinear variable stiffness and gradual increase, for example, when the hydro-pneumatic spring is applied to a vehicle, the suspension dynamic travel is smaller, the stiffness generated by the instantaneous pressure born by an elastic medium is small, and the requirement of vehicle smoothness can be met; when the vehicle runs on a rough road, the elastic force is in nonlinear change and the rigidity is increased, so that more impact energy can be absorbed, the characteristic of large energy storage ratio of unit mass of the air outlet is exerted, the cushioning effect can be effectively achieved, the ground excitation is prevented from being directly transmitted to the vehicle body, the phenomenon of suspension breakdown is avoided, the off-road speed of the vehicle is improved, and the maneuverability is improved.

However, the damping force of the piston rod of the existing single-cylinder oil-gas hybrid spring is a fixed value during stretching, so that the piston on the piston rod and the guide sleeve are rigidly impacted during stretching of the piston rod of the oil-gas spring, and the service life of the oil-gas spring is finally affected. For example, vehicles in the mine field generally adopt an integral axle, a front suspension system is a structure of four connecting rods, transverse pull rods and single-cylinder oil-gas hybrid springs, the stroke design of the single-cylinder oil-gas hybrid springs is smaller in order to reduce the influence of the transverse pull rods, and tires frequently reach the lower jump limit position in the actual running process of the vehicles. Because the mining vehicle is not provided with a lower limiting device generally, a single-cylinder oil-gas hybrid spring is required to bear the impact force when the tire jumps downwards to the limit position, the impact force can stretch a piston rod of the oil-gas spring, and the stretching often causes rigid collision between the piston and a guide sleeve.

Disclosure of Invention

In view of the above, the utility model provides a variable damping single-cylinder oil-gas hybrid spring, which solves the technical problems that the damping force of a piston rod of the existing single-cylinder oil-gas hybrid spring is a fixed value when the piston rod is stretched, the rigid collision between the piston inside the oil-gas spring and a guide sleeve is easy to cause, and the service life of the single-cylinder oil-gas hybrid spring is finally influenced.

The utility model adopts the following technical scheme:

a damping-variable single-cylinder oil-gas hybrid spring comprises a cylinder barrel, a guide sleeve, a piston rod, a piston, an upper connecting piece and a lower connecting piece;

one end of the cylinder barrel is closed and provided with the upper connecting piece, and the other end of the cylinder barrel is open;

one end of the piston rod is closed and provided with the lower connecting piece, and the other end of the piston rod is open; the open end of the piston rod is coaxially arranged in the inner cavity of the cylinder barrel through the guide sleeve; an orifice is arranged on the side wall of the piston rod, and a sphere is arranged in the orifice; the side wall of the piston rod is also provided with a normal through hole;

the piston is coaxially fixedly connected to the open end of the piston rod; the piston is in sliding fit with the inner wall of the cylinder barrel, a main oil cavity is formed between the piston and the closed end of the cylinder barrel, an annular cavity is formed among the inner wall of the cylinder barrel, the outer wall of the piston rod, the piston and the guide sleeve, and the central through hole of the piston is used for communicating the main oil cavity with the inner cavity of the piston rod; the piston limits the sphere to move in the throttle hole;

when the piston rod is in a compression limit position, the normal through hole is positioned outside the guide sleeve, and after the piston rod stretches to enable the normal through hole to completely enter the guide sleeve, a gap exists between the piston and the guide sleeve.

Further, the plurality of the normal through holes are distributed along the axial direction of the piston rod.

Further, the plurality of the normal through holes are spirally distributed along the axial direction of the piston rod.

Further, the throttling hole is stepped and comprises a small throttling hole and a large throttling hole;

one end of the throttling large hole is positioned on the outer wall of the piston rod, the other end of the throttling large hole extends to be communicated with one end of the throttling small hole along the radial direction of the piston rod, and the other end of the throttling small hole is positioned on the inner wall of the piston rod;

the diameter of the sphere is between the diameter of the throttling macropores and the diameter of the throttling pinholes.

Further, the area of the throttling macropores, which is located at one end of the outer wall of the piston rod and is shielded, is not more than half of the cross-sectional area of the throttling macropores.

Further, the guide sleeve is coaxially arranged in an inner cavity at one end of the opening of the cylinder barrel, and one end of the guide sleeve is positioned outside the cylinder barrel and is connected with the end part at one end of the opening of the cylinder barrel through a bolt;

one end of the guide sleeve, which is positioned outside the cylinder barrel, is also provided with a process threaded hole.

Further, an inflation valve communicated with the main oil cavity is arranged on the upper connecting piece, and a protective cap is arranged on the inflation valve.

Further, the upper connecting piece and the lower connecting piece are provided with radial spherical plain bearings;

the upper connecting piece and the lower connecting piece are provided with oil holes for adding lubricating oil to the radial spherical plain bearing, and the oil holes on the upper connecting piece and the inflation valve on the upper connecting piece are positioned on the same side.

Further, the upper connecting piece is provided with an exhaust hole communicated with the main oil cavity; and a plug is arranged on the exhaust hole.

Further, the lower connecting piece is provided with an oil drain hole communicated with the inner cavity of the piston rod.

The beneficial effects are that:

1. one end of the cylinder barrel is closed and provided with an upper connecting piece, and the other end of the cylinder barrel is open; one end of the piston rod is closed and provided with a lower connecting piece, and the other end of the piston rod is open; the open end of the piston rod is coaxially arranged in the inner cavity of the cylinder barrel through the guide sleeve; the side wall of the piston rod is provided with an orifice, and a sphere is arranged in the orifice; the side wall of the piston rod is also provided with a normal through hole; the piston is coaxially fixedly connected to the open end of the piston rod; the piston is in sliding fit with the inner wall of the cylinder barrel, a main oil cavity is formed between the piston and the closed end of the cylinder barrel, an annular cavity is formed among the inner wall of the cylinder barrel, the outer wall of the piston rod, the piston and the guide sleeve, and the central through hole of the piston is used for communicating the main oil cavity with the inner cavity of the piston rod; the piston limits the sphere to move in the orifice; when the piston rod is in the compression limit position, the normal through hole is positioned outside the guide sleeve, and after the piston rod stretches to enable the normal through hole to completely enter the guide sleeve, a gap exists between the piston and the guide sleeve.

Therefore, when the piston rod of the hydro-pneumatic spring stretches to the longest process, the ball in the throttle hole is blocked by the oil pressure, the oil in the annular cavity can only flow into the main oil cavity through the normal through hole arranged on the piston rod, and the normal through hole gradually enters the inner cavity of the guide sleeve, so that the oil passing area of the normal through hole is gradually reduced, the damping force of the hydro-pneumatic spring gradually begins to be increased, and after the normal through hole completely enters the inner cavity of the guide sleeve, the oil in the annular cavity cannot flow into the main oil cavity, and the annular cavity at the moment can be considered to be closed. Considering the incompressibility of oil, when the hydro-pneumatic spring stretches to the inner cavity of the guide sleeve when the normal through hole on the piston rod completely enters the guide sleeve, the hydro-pneumatic spring cannot continue stretching, so that the piston and the guide sleeve can be prevented from rigid collision, and the problem that the service life of the hydro-pneumatic spring is influenced due to rigid collision is avoided.

2. The plurality of the normal through holes are distributed along the axial direction of the piston rod, which can lead the damping force of the hydro-pneumatic spring to have a longer gradual increasing process in the stretching process, and the plurality of the normal through holes are spirally distributed

3. The plurality of normal through holes are spirally distributed along the axial direction of the piston rod, so that the phenomenon that the strength of the cylinder barrel is influenced due to too close center distance of the normal through holes can be avoided.

4. The orifice is stepped and comprises a small orifice and a large orifice; one end of the throttling big hole is positioned on the outer wall of the piston rod, the other end of the throttling big hole extends to be communicated with one end of the throttling small hole along the radial direction of the piston rod, and the other end of the throttling small hole is positioned on the inner wall of the piston rod; the diameter of the sphere is between the diameter of the throttling macropore and the diameter of the throttling aperture.

Therefore, when the piston rod is compressed, the ball body can be jacked by oil, oil in the main oil cavity flows into the annular cavity from the throttle hole and the normal through hole simultaneously, when the piston rod is stretched, the ball body is impacted downwards by the oil, the throttle small hole can be plugged, so that the oil in the annular cavity can only flow into the main oil cavity through the normal through hole, and the structure is simple and compact.

5. The area of the throttling big hole, which is blocked at one end of the outer wall of the piston rod, is not more than half of the cross section area of the throttling big hole, so that obvious throttling phenomenon of oil liquid can be effectively avoided when the piston blocks the throttling big hole.

6. The guide sleeve is coaxially arranged in the inner cavity of the open end of the cylinder barrel, one end of the guide sleeve is positioned outside the cylinder barrel and fixedly connected with the open end of the cylinder barrel through a bolt, and one end of the guide sleeve positioned outside the cylinder barrel is further provided with a process threaded hole.

Therefore, when the components such as the piston, the guide sleeve, the sealing element and the like are to be replaced or maintained, the hydro-pneumatic spring is not required to be detached integrally from the vehicle body, the guide sleeve can be pulled out of the cylinder barrel by unscrewing the bolt for fixing the guide sleeve and screwing in and pulling out the bolt in the process threaded hole, and the replacement of the components such as the guide sleeve, the piston, the sealing element and the like can be realized, so that the convenience in operation in the field environment is greatly facilitated.

7. The upper connecting piece is provided with the inflation valve communicated with the main oil cavity, and the inflation valve is provided with the protective cap, so that an oil gas medium can be filled into the main oil cavity through the inflation valve, and the protective cap can prevent the inflation valve from being knocked and damaged.

8. The upper connecting piece and the lower connecting piece are provided with the radial spherical plain bearing, the upper connecting piece and the lower connecting piece are provided with oil injection holes for adding lubricating oil to the radial spherical plain bearing, and the oil injection holes on the upper connecting piece are positioned on the same side with the inflation valve on the upper connecting piece, so that the radial spherical plain bearing can be conveniently injected with oil and lubricated on a vehicle.

9. The upper connecting piece is provided with an exhaust hole communicated with the main oil cavity, so that when the oil gas spring is injected through the charging valve, the plug on the exhaust hole is opened to fully exhaust air in the cylinder barrel, and the plug is used for sealing after the injection is finished.

10. The lower connecting piece is provided with the oil drain hole communicated with the inner cavity of the piston rod, so that the oil in the hydro-pneumatic spring cylinder barrel is discharged completely in the field environment, and maintenance work such as oil-gas ratio and the like is carried out again.

Drawings

FIG. 1 is a diagram of a variable damping single cylinder gas-oil hybrid spring assembly provided by the present utility model;

FIG. 2 is a front view of the upper hinge structure of FIG. 1;

FIG. 3 is a left side view of the upper hinge structure of FIG. 1;

FIG. 4 is a front view of the lower hinge structure of FIG. 1;

FIG. 5 is a top view of the lower hinge structure of FIG. 1;

FIG. 6 is a schematic illustration of the piston structure of FIG. 1;

FIG. 7 is a schematic view of the piston rod of FIG. 1;

FIG. 8 is a right side view of the piston rod structure of FIG. 1;

FIG. 9 is a schematic view of the guide sleeve assembly of FIG. 1;

FIG. 10 is a left side view of the guide sleeve structure of FIG. 1;

wherein, 1-upper hinge; 2-cylinder barrel; 3-piston; 4-a guide sleeve; 5-a guide sleeve bolt; 6-a piston rod; 7-a lower hinge; 8-a radial spherical plain bearing; 9-an oil filling nozzle; 10-plugging; 11-a piston rod inner cavity; 12-a first ordinary through hole; 13-a second ordinary through hole; 14-a third normal through hole; 15-fourth normal through holes; 16-an annular cavity; 17-throttling macropores; 18-a throttle orifice; 19-steel balls; 20-an oil filling hole; 21-a piston bolt; 22-a main oil chamber; 23-protective cap; 24-an inflation valve; 25-exhaust holes; 26-a retainer ring for holes; 27-piston inner side wall; 28-an inner bottom wall of the piston; 29-a piston through hole; 30-a threaded hole of a piston rod; 31-a guide sleeve threaded hole; 32-a dust seal; 33-an oil seal; 34-lip seal; a 35-O-shaped ring; 36-a first guide belt; 37-a guide sleeve protection ring; 38-a second guide belt; 39-upper end face of upper hinge; 40-exhaust holes; 41-a process threaded hole; 42-small outer circle section of piston rod; 43-large outer circle section of piston rod.

Detailed Description

The utility model will now be described in detail by way of example with reference to the accompanying drawings. In the description of the present utility model, it should be understood that the azimuth or positional relationships indicated by the azimuth terms such as "front, rear, upper, lower, left, right", "lateral, vertical, horizontal", and "top, bottom", etc., are generally based on the azimuth or positional relationships shown in the drawings, merely to facilitate description of the present utility model and simplify the description, and these azimuth terms do not indicate and imply that the apparatus or elements referred to must have a specific azimuth or be constructed and operated in a specific azimuth, and thus should not be construed as limiting the scope of protection of the present utility model; the orientation word "inner and outer" refers to inner and outer relative to the contour of the respective component itself.

Referring to fig. 1 to 10, a damping-variable single-cylinder oil-gas hybrid spring includes a cylinder 2, a guide sleeve 4, a piston rod 6, a piston 3, an upper connector (an upper hinge 1 in this embodiment) and a lower connector (a lower hinge 7 in this embodiment), wherein:

one end of the cylinder barrel 2 is closed and provided with an upper hinge 1, and the other end is open; the guide sleeve 4 is coaxially arranged in the inner cavity of the cylinder barrel 2; the piston rod 6 is of a hollow structure (the middle part of the piston rod is a piston rod inner cavity 11), one end of the piston rod is closed and provided with a lower hinge 7, and the other end of the piston rod is open; the side wall of the piston rod 6 is provided with an orifice, and a sphere (a steel ball 19 in the embodiment) is arranged in the orifice; the side wall of the piston rod 6 is also provided with a normal through hole; one end of the piston 3 is coaxially sleeved outside the open end of the piston rod 6, and the inner side wall 27 of the end of the piston 3 is attached to the outer wall of the piston rod 6 and partially shields the throttle hole, so that the steel ball 19 is limited to move in the throttle hole; the open end of the piston rod 6 is coaxially sleeved in the cylinder barrel 2 in a sliding manner through the guide sleeve 4, so that the outer wall of the piston 3 is in sliding fit with the inner wall of the cylinder barrel 2, the outer wall of the piston rod 6 is in sliding fit with the inner cavity wall surface of the guide sleeve 4 (the outer wall of the piston rod 6 and the inner cavity wall surface of the guide sleeve 4 are both processed by adopting a chromium plating and grinding process), a main oil cavity 22 is formed between the closed end of the cylinder barrel 2 and the piston 3, and a central through hole of the piston 3 is used for communicating the main oil cavity 22 with the inner cavity 11 of the piston rod; an annular cavity 16 is formed among the inner wall of the cylinder barrel 2, the outer wall of the piston rod 6, the piston 3 and the guide sleeve 4; when the piston rod 6 is at the compression limit position, the normal through hole is positioned outside the guide sleeve 4 (i.e. between the piston 3 and the guide sleeve 4), when the piston rod 6 is stretched (in fig. 1, the piston rod 6 moves rightward to be stretched, and moves leftward to be compressed), the steel ball 19 is subjected to oil pressure in the annular cavity 16 to block the orifice, the normal through hole gradually enters the inner cavity of the guide sleeve 4, and when the normal through hole completely enters the guide sleeve 4, a gap is reserved between the piston 3 and the guide sleeve 4.

In this way, when the piston rod 6 of the hydro-pneumatic spring stretches to the longest process, the steel ball 19 in the throttle hole is blocked by the pressure of the oil, the oil in the annular cavity 16 can only flow into the main oil cavity 22 through the normal through hole arranged on the piston rod 6 and through the inner cavity 11 of the piston rod, and the normal through hole gradually enters the inner cavity of the guide sleeve 4 along with the stretching of the piston rod 6, so that the oil passing area of the normal through hole gradually decreases, the damping force of the hydro-pneumatic spring gradually begins to become larger, the damping force of the hydro-pneumatic spring is related to the displacement of the piston rod, and after the normal through hole completely enters the inner cavity of the guide sleeve 4, a gap remains between the piston 3 and the guide sleeve 4 (namely, the piston 3 and the guide sleeve 4 do not collide yet at this time), but the oil in the annular cavity 16 cannot flow into the main oil cavity 22 at this time, and the annular cavity 16 can be considered to be closed at this time. Considering the incompressibility of oil, when the hydro-pneumatic spring stretches to the normal through hole on the piston rod 6 and completely enters the inner cavity of the guide sleeve 4, the hydro-pneumatic spring cannot continue stretching, so that the piston 3 and the guide sleeve 4 can be prevented from rigid collision, and the problem that the service life of the hydro-pneumatic spring is influenced by the rigid collision is avoided. In addition, when the piston rod 6 is in a compressed state, the steel ball 19 is jacked by oil, and the oil in the main oil cavity 22 can pass through the normal through hole and the throttle simultaneously to enter the annular cavity 16.

In this embodiment, four normal through holes spaced from each other by a certain distance are provided along the axial direction of the piston rod 6, namely, a first normal through hole 12, a second normal through hole 13, a third normal through hole 14 and a fourth normal through hole 15, which can enable the damping force of the hydro-pneumatic spring in the stretching process to have a longer gradual increase process, and the multiple normal through holes are spirally distributed to avoid too close center distances of the normal through holes, so that the strength of the cylinder barrel 2 is affected. Specifically, at this time, when the piston rod 6 is in the tensile state, the first normal through hole 12 firstly enters the inner cavity of the guide sleeve 4, the oil passing area of the first normal through hole 12 is gradually reduced in the process, the damping force of the hydro-pneumatic spring in the tensile process begins to be increased, and similarly, when the second normal through hole 13, the third normal through hole 14 and the fourth normal through hole 15 sequentially enter the inner cavity of the guide sleeve 4, the total oil passing area of the normal through holes on the piston rod 6 is gradually reduced, the hydro-pneumatic spring generates larger damping force to attenuate impact vibration from the ground, and when the fourth normal through hole 15 completely enters the inner cavity of the guide sleeve 4, the oil in the annular cavity 16 cannot flow into the main oil cavity 22, and in this state, the hydro-pneumatic spring cannot continue to stretch, so that the structure can ensure that the right end face of the piston 3 and the left end face of the guide sleeve 4 do not generate rigid impact, and the condition debris that damages the sealing element due to the rigid impact is avoided.

Of course, if the four normal through holes are distributed on a straight line along the axis of the piston rod, the damping force of the hydro-pneumatic spring in the stretching process can be increased gradually for a long time, and the multiple normal through holes are distributed along the axial direction of the piston rod, so that the processing is simple, but the strength of the cylinder barrel is influenced due to the fact that the center distances of the normal through holes are too close. In addition, the number of the normal through holes can be one, the normal through holes are not limited to round holes, and the size of the normal through holes can be set reasonably according to working conditions.

In the embodiment, the throttling hole is in a step shape and comprises a throttling small hole 18 and a throttling large hole 17, one end of the throttling large hole 17 is positioned on the outer wall of the piston rod 6, the other end of the throttling large hole 17 extends along the radial direction of the piston rod 6 to be communicated with one end of the throttling small hole 18, and the other end of the throttling small hole 18 is positioned on the inner wall of the piston rod 6; the diameter of the steel ball 19 is between the diameter of the throttle large hole 17 and the diameter of the throttle small hole 18. Therefore, when the piston rod 6 is compressed, the steel ball 19 can be jacked by oil, oil in the main oil cavity 22 flows into the annular cavity 16 from the throttling hole and the normal through hole simultaneously, when the piston rod 6 is stretched, the steel ball 19 is impacted downwards by the oil, the throttling small hole 18 can be blocked, so that the oil in the annular cavity 16 can only flow into the main oil cavity 22 through the normal through hole, and the structure is simple and compact. It will be appreciated that in other possible embodiments the orifice need not be stepped, for example, the orifice 17 in this embodiment may be designed as an inverted cone, the orifice 18 in this embodiment may be designed as a bevel (i.e. not coaxial with the orifice 17), or the orifice may consist of more than the orifice 17 and orifice 18, etc.

In particular, with reference to fig. 1, 6 and 7, the above-mentioned piston rod 6 comprises a small piston rod outer circular section 42 and a large piston rod outer circular section 43, taking into account the assembly of the piston 3 with the piston rod 6. The piston 3 is in threaded connection with the piston rod threaded hole 30 at the end of the piston rod small outer circle section 42 through the piston bolt 21 which is circumferentially arranged, and the outer wall of the piston 3 is in sliding fit with the inner wall of the cylinder barrel 2, the inner bottom wall 28 of the piston is attached to the end of the piston rod small outer circle section 42, and the inner side wall 27 of the piston is attached to the outer wall of the piston rod small outer circle section 42. Here, the piston 3 and the piston rod 6 may be directly screwed or the piston 3 and the piston rod 6 may be integrally formed by an integral forging method.

In addition, a first guide belt 36, an oil seal 33, a lip seal 34, a second guide belt 38 and a dust seal 32 are sequentially arranged on the wall surface of the inner cavity of the guide sleeve 4 from left to right, and the first guide belt 36 and the second guide belt 38 are symmetrically arranged on two sides of the oil seal 33 and the lip seal 34 which are connected in series and are in sliding fit with the outer wall of the piston rod large outer circle section 43; an O-shaped ring 35 and a guide sleeve protection ring 37 are arranged on the outer wall of the guide sleeve 4, the guide sleeve protection ring 37 and the O-shaped ring 35 are arranged in the same groove, and the guide sleeve protection ring 37 is tightly attached to the O-shaped ring 35; the outer wall of the guide sleeve 4 is slidably engaged with the inner wall of the cylinder tube 2 to enable the O-ring 35 to be deformed by compression to seal the annular chamber 16.

More specifically, an inflation valve 24 communicating with the main oil chamber 22 is disposed near the upper end surface 39 of the upper hinge, and a protective cap 23 is disposed on the inflation valve 24, so that the main oil chamber 22 can be filled with oil-gas medium through the inflation valve 24, specifically, the protective cap 23 and the inflation valve 24 can be removed first, then the inflation valve 24 is installed for inflation, and of course, only the protective cap 23 can be removed and then the oil-gas medium can be directly filled through the inflation valve 24. The protective cap 23 can prevent the inflation valve 24 from being knocked and damaged. And be provided with radial joint bearing 8 (spacing through hole retainer ring 26) on upper hinge 1 and the lower hinge 7, be provided with the oil filler point 20 that is used for adding lubricating oil to radial joint bearing 8 on upper hinge 1 and the lower hinge 7, threaded connection has nozzle 9 on the oil filler point 20, and the oil filler point 20 on upper hinge 1 is located the homonymy with the inflation valve 24 on upper hinge 1, so, is convenient for in the car to radial joint bearing 8 oiling lubrication. In addition, the upper hinge 1 is further provided with an exhaust hole 25 (the exhaust hole 25 is provided with a blocking piece, such as a plug) which is communicated with the main oil cavity 22, so that when the oil gas spring is filled with oil through the charging valve 24, the blocking piece on the exhaust hole 25 is opened to fully exhaust the air in the cylinder barrel 2, and the blocking piece is arranged after the oil filling is finished. The lower hinge 7 is provided with an oil drain hole (a plug 10 is arranged on the oil drain hole) communicated with the inner cavity 11 of the piston rod, so that the oil in the hydro-pneumatic spring cylinder barrel 2 is discharged completely in a field environment, and maintenance work such as oil-gas volume proportioning (oil filling volume and inflation pressure proportioning) is carried out again.

As an improvement, in this embodiment, the guide sleeve 4 is coaxially disposed in the inner cavity of the open end of the cylinder barrel 2, and the right end of the guide sleeve 4 is located outside the cylinder barrel 2 and provided with guide sleeve threaded holes 31 distributed circumferentially, so that the guide sleeve 4 and the open right end (provided with threaded holes) of the cylinder barrel 2 can be screwed through the guide sleeve bolts 5. Moreover, the right end face of the guide sleeve 4 is further provided with the process threaded holes 41 which are circumferentially distributed, so that when the components such as the piston 3, the guide sleeve 4 and the sealing element are to be replaced or maintained, the hydro-pneumatic spring is not required to be detached integrally from a vehicle body (or other devices), the bolts for fixing the guide sleeve 4 are only required to be unscrewed, and then the guide sleeve can be pulled out of the cylinder barrel by screwing the pulling bolts into the process threaded holes 41, so that the components such as the guide sleeve 4, the piston 3 and the sealing element can be replaced, and convenience in operation in a field environment is greatly facilitated.

As a further improvement, in this embodiment, the area of the throttling macropores 17 at the end of the outer wall of the piston rod 6, which is shielded by the inner wall 27 of the piston, is not more than half of the cross-sectional area of the throttling macropores 17, which can effectively avoid the obvious throttling phenomenon of oil when the piston 3 shields the throttling macropores.

In summary, the above embodiments are only preferred embodiments of the present utility model, and are not intended to limit the scope of the present utility model. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present utility model should be included in the protection scope of the present utility model.

Claims (10)

1. A damping-variable single-cylinder oil-gas hybrid spring is characterized by comprising a cylinder barrel, a guide sleeve, a piston rod, a piston, an upper connecting piece and a lower connecting piece;

one end of the cylinder barrel is closed and provided with the upper connecting piece, and the other end of the cylinder barrel is open;

one end of the piston rod is closed and provided with the lower connecting piece, and the other end of the piston rod is open; the open end of the piston rod is coaxially arranged in the inner cavity of the cylinder barrel through the guide sleeve; an orifice is arranged on the side wall of the piston rod, and a sphere is arranged in the orifice; the side wall of the piston rod is also provided with a normal through hole;

the piston is coaxially fixedly connected to the open end of the piston rod; the piston is in sliding fit with the inner wall of the cylinder barrel, a main oil cavity is formed between the piston and the closed end of the cylinder barrel, an annular cavity is formed among the inner wall of the cylinder barrel, the outer wall of the piston rod, the piston and the guide sleeve, and the central through hole of the piston is used for communicating the main oil cavity with the inner cavity of the piston rod; the piston limits the sphere to move in the throttle hole;

when the piston rod is in a compression limit position, the normal through hole is positioned outside the guide sleeve, and after the piston rod stretches to enable the normal through hole to completely enter the guide sleeve, a gap exists between the piston and the guide sleeve.

2. The variable damping single cylinder gas and oil hybrid spring as set forth in claim 1 wherein said plurality of normally open holes are axially distributed along said piston rod.

3. The variable damping single cylinder oil and gas hybrid spring as set forth in claim 2 wherein said plurality of normally open holes are helically disposed along the axis of said piston rod.

4. The variable damping single-tube oil-gas hybrid spring according to claim 1, wherein the orifice is stepped and comprises a small orifice and a large orifice;

one end of the throttling large hole is positioned on the outer wall of the piston rod, the other end of the throttling large hole extends to be communicated with one end of the throttling small hole along the radial direction of the piston rod, and the other end of the throttling small hole is positioned on the inner wall of the piston rod;

the diameter of the sphere is between the diameter of the throttling macropores and the diameter of the throttling pinholes.

5. The variable damping single cylinder gas and oil hybrid spring as set forth in claim 4 wherein said orifice is no more than half the cross-sectional area of said orifice as said one end of said piston rod outer wall is occluded.

6. The damping-variable single-cylinder oil-gas hybrid spring according to claim 1, wherein the guide sleeve is coaxially arranged in an inner cavity of the open end of the cylinder barrel, and one end of the guide sleeve is positioned outside the cylinder barrel and is connected with the end part of the open end of the cylinder barrel through a bolt;

one end of the guide sleeve, which is positioned outside the cylinder barrel, is also provided with a process threaded hole.

7. The variable damping single-cylinder oil-gas hybrid spring according to claim 1, wherein an inflation valve communicated with the main oil cavity is arranged on the upper connecting piece, and a protective cap is arranged on the inflation valve.

8. The damping-variable single-cylinder oil-gas hybrid spring according to claim 6, wherein radial spherical bearings are arranged on the upper connecting piece and the lower connecting piece;

the upper connecting piece and the lower connecting piece are provided with oil holes for adding lubricating oil to the radial spherical plain bearing, and the oil holes on the upper connecting piece and the inflation valve on the upper connecting piece are positioned on the same side.

9. The variable damping single-cylinder oil-gas hybrid spring according to claim 1, wherein the upper connecting piece is provided with an exhaust hole communicated with the main oil cavity; and a plug is arranged on the exhaust hole.

10. A variable damping single cylinder gas and oil hybrid spring as set forth in any one of claims 1 through 9 wherein said lower connecting member is provided with an oil drain communicating with said piston rod interior.