阅读说明：本技术 蓄能器竖置平衡油气悬挂 (Accumulator vertical balance hydro-pneumatic suspension ) 是由 陈轶杰 韩小玲 郑冠慧 张亚峰 张旭 赵宁 徐梦岩 万义强 于 2020-02-25 设计创作，主要内容包括：本发明公开了一种蓄能器竖置平衡油气悬挂,属于液压机械技术领域。悬挂包括前油气弹簧、前平衡管路、后油气弹簧、后平衡管路、蓄能器和管路接头；前油气弹簧的主油腔油口与前平衡管路的一端连接,前平衡管路的另一端通过管路接头与蓄能器的第一进油口连接；后油气弹簧的主油腔油口与后平衡管路的一端连接,后平衡管路的另一端也通过管路接头与蓄能器的第二进油口连接,形成平衡悬挂。通过前后轮油气弹簧油室连通并外置蓄能器的方式实现单轮冲击载荷的大幅下降,以及轮胎接地能力的显著提升,在矿山机械等领域有着广阔的使用前景。(The invention discloses an energy accumulator vertical balance hydro-pneumatic suspension, and belongs to the technical field of hydraulic machinery. The suspension comprises a front hydro-pneumatic spring, a front balance pipeline, a rear hydro-pneumatic spring, a rear balance pipeline, an energy accumulator and a pipeline joint; the oil port of the main oil cavity of the front hydro-pneumatic spring is connected with one end of a front balance pipeline, and the other end of the front balance pipeline is connected with a first oil inlet of the energy accumulator through a pipeline joint; the oil port of the main oil cavity of the rear hydro-pneumatic spring is connected with one end of a rear balance pipeline, and the other end of the rear balance pipeline is also connected with a second oil inlet of the energy accumulator through a pipeline joint to form a balance suspension. The single-wheel impact load is greatly reduced by communicating the oil chambers of the hydro-pneumatic springs of the front wheel and the rear wheel and externally arranging the energy accumulator, the grounding capacity of the tire is remarkably improved, and the single-wheel impact load-reducing device has a wide application prospect in the fields of mining machinery and the like.)

1. The energy storage ware is erected and is put balanced hydro-pneumatic suspension, including preceding hydro-pneumatic spring (21), preceding balanced pipeline (24), back hydro-pneumatic spring (22), back balanced pipeline (23), energy storage ware (26), pipe joint (27), its characterized in that: an oil port of a main oil cavity of the front hydro-pneumatic spring (21) is connected with one end of a front balance pipeline (24), and the other end of the front balance pipeline (24) is connected with a first oil inlet of an energy accumulator (26) through a pipeline joint (27); an oil port of a main oil cavity of the rear hydro-pneumatic spring (22) is connected with one end of a rear balance pipeline (23), and 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 balance suspension.

2. The accumulator vertical balance hydro-pneumatic suspension of claim 1, wherein: the energy accumulator (26) is a piston type energy accumulator and is arranged vertically.

3. The accumulator vertical balance hydro-pneumatic suspension of claim 1, wherein: the inner diameters of the front balance pipeline (24) and the rear balance pipeline (23) are not less than 20 mm.

4. The accumulator vertical balance hydro-pneumatic suspension of claim 1, wherein: the front hydro-pneumatic spring (21) and the rear hydro-pneumatic spring (22) comprise a cylinder barrel (1), oil filling holes (7), plug screws (8) for oil drainage, inflation valves (13), upper hinges (14), communication oil ports (18), upper limiting positions (85), oil passing grooves (82) and lower hinges (6), the upper ends of the cylinder barrels (1) of the front hydro-pneumatic spring (21) and the rear hydro-pneumatic spring (22) are provided with the communication oil ports (18), the oil filling holes (7) on the lower hinges (6) and the plug screws (8) for oil drainage are arranged in the same direction as the oil filling holes (7) on the upper hinges (14) and the inflation valves (13), face the outer side of the vehicle and are perpendicular to the axial direction of the communication oil ports (18) on the front hydro-pneumatic spring (21) and the rear hydro-pneumatic spring (22); the communication oil ports (18) of the front hydro-pneumatic spring (21) and the rear hydro-pneumatic spring (22) are arranged in opposite directions, wherein the communication oil port (18) of the front hydro-pneumatic spring (21) faces the rear direction of the vehicle, and the communication oil port (18) of the rear hydro-pneumatic spring (22) faces the front direction of the vehicle.

5. The accumulator vertical balance hydro-pneumatic suspension of claim 4, wherein: an upper limit (85) of an annular structure is machined at one end, facing the rodless oil cavity of the hydro-pneumatic spring, of the upper hinge (14), and the diameter of the outer circle of the upper limit (85) is smaller than that of the inner hole of the cylinder barrel (1).

6. The accumulator vertical balance hydro-pneumatic suspension of claim 5, wherein: an oil passing groove (82) which is circumferentially arranged is machined in the side wall of the upper limit (85), and the oil passing groove (82) is right opposite to the communicating oil port (18).

Technical Field

The invention relates to a vertically-arranged balanced hydro-pneumatic suspension of an energy accumulator, and belongs to the technical field of hydraulic machinery.

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.

At present, most domestic mining vehicles adopt a 6X4 driving mode, the two rear axles are relatively close in distance, mainly used for bearing the weight of cargos, the prior art mostly adopts a structure of a steel plate spring, the function of balanced suspension is realized through a structural part, namely, the bearing capacity of the two axles is mutually compensated, the limit impact load of a single axle is effectively inhibited, and the phenomenon of axle damage is avoided.

Disclosure of Invention

In view of the above, the invention provides an energy accumulator vertically-arranged balanced hydro-pneumatic suspension, which realizes the great reduction of single-wheel impact load and the obvious improvement of tire grounding capacity in a mode of communicating a front wheel hydro-pneumatic spring oil chamber and a rear wheel hydro-pneumatic spring oil chamber and externally arranging an energy accumulator, and has wide application prospect in the fields of mining machinery and the like.

A vertically-arranged balanced hydro-pneumatic suspension for an energy accumulator comprises a front hydro-pneumatic spring, a front balance pipeline, a rear hydro-pneumatic spring, a rear balance pipeline, the energy accumulator and a pipeline joint; an oil port of a main oil cavity of the front hydro-pneumatic spring is connected with one end of a front balance pipeline, and the other end of the front balance pipeline is connected with a first oil inlet of the energy accumulator through a pipeline joint; the oil port of the main oil cavity of the rear hydro-pneumatic spring is connected with one end of a rear balance pipeline, and the other end of the rear balance pipeline is also connected with a second oil inlet of the energy accumulator through a pipeline joint to form a balance suspension.

Further, the energy accumulator is a piston type energy accumulator and is arranged vertically.

Further, the inner diameter of the front balance pipeline and the inner diameter of the rear balance pipeline are not less than 20 mm.

Furthermore, the front hydro-pneumatic spring and the rear hydro-pneumatic spring comprise cylinder barrels, oil filling holes, plugs for oil drainage, inflation valves, upper hinges, communicating oil ports, upper limit positions, oil passing grooves and lower hinges, the upper ends of the cylinder barrels of the front hydro-pneumatic spring and the rear hydro-pneumatic spring are provided with the communicating oil ports, the oil filling holes and the plugs for oil drainage on the lower hinges are arranged in the same direction with the oil filling holes and the inflation valves on the upper hinges, face the outer side of the vehicle and are perpendicular to the axial direction of the communicating oil ports on the front hydro-pneumatic spring and the rear hydro-pneumatic spring; the front hydro-pneumatic spring and the rear hydro-pneumatic spring are arranged in opposite directions, wherein the front hydro-pneumatic spring is communicated towards the rear direction of the vehicle, and the rear hydro-pneumatic spring is communicated towards the front direction of the vehicle.

Furthermore, an upper limit of an annular structure is processed at one end, facing the rodless oil cavity of the hydro-pneumatic spring, of the upper hinge, and the diameter of an outer circle of the upper limit is smaller than that of an inner hole of the cylinder barrel.

Furthermore, an oil passing groove which is circumferentially arranged is machined in the side wall of the upper limit and is right opposite to the communicating oil port.

Has the advantages that:

1. the invention provides a balanced hydro-pneumatic suspension structure, which is characterized in that main oil cavities of hydro-pneumatic springs on the same sides of two axles are respectively communicated with two oil ports processed on an energy accumulator through pipelines.

2. The inner diameter of the front and rear balance pipelines is not less than 20mm, the on-way resistance loss of the pipelines can be effectively inhibited, and the superiority of balanced suspension can be fully embodied by testing that the compensation time difference of oil gas spring oil of the front and rear axles is less than 0.05 s.

3. The invention creatively provides that the upper limit is arranged at the hinge position of the hydro-pneumatic spring, so that the condition that the oil compensation is not smooth due to the interference of a communicating oil port with a balanced suspension when a suspension piston is compressed to a limit position is avoided.

4. Compared with the traditional bag type or diaphragm type energy accumulator (the compression ratio is 1: 8), the piston type or diaphragm type energy accumulator has no limitation of the compression ratio, can absorb more impact energy, and prevents the energy accumulator from being broken down and damaged; in addition, when the energy accumulator is vertically arranged, the energy accumulator is conveniently communicated with the front hydro-pneumatic spring and the rear hydro-pneumatic spring respectively, and the optimized pipeline arrangement is realized.

5. The invention adopts the scheme of vertically arranging the piston type energy accumulator, after the balance oil gas is hung on a vehicle, the oil filling hole and the plug for oil drainage on the lower hinge are arranged in the same direction with the oil filling hole and the inflation valve on the upper hinge and face the outer side of the vehicle, so that the oil gas spring is convenient to maintain; in addition, the communication oil ports of the front hydro-pneumatic spring and the rear hydro-pneumatic spring are arranged in opposite directions, wherein the communication oil port of the front hydro-pneumatic spring faces the rear direction of the vehicle, and the communication oil port of the rear hydro-pneumatic spring faces the front direction of the vehicle, so that the lengths of the front balance pipeline and the rear balance pipeline can be shortened to the maximum extent, and the influence of the on-way loss on the balance suspension performance is reduced.

Drawings

FIG. 1 is a schematic diagram of a transversely-arranged balanced hydro-pneumatic suspension structure of an energy accumulator;

FIG. 2 is a schematic diagram of a vertically-arranged balanced hydro-pneumatic suspension structure of an energy accumulator;

FIG. 3 is a front cross-sectional view of the hydro-pneumatic suspension;

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

FIG. 5 is a profile view of the hydro-pneumatic suspension;

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 annular cavity, 14 an upper hinge, 15 a small throttling hole, 16 a large throttling hole, 17 a guide sleeve bolt, 18 a communication oil port, 19 a large outer circle, 20 a small outer circle, 31 a guide threaded 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 a second oil seal, 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 thread 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 invention is described in detail below by way of example with reference to the accompanying drawings.

The invention designs a balanced hydro-pneumatic suspension structure, which has wide application prospect in the fields of mining machinery and multi-shaft heavy-duty carrier vehicles. 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 in a welding or threaded connection mode, the piston rod 2 is fixedly connected with the lower hinge 6 in a welding or threaded connection mode, 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 the piston inner hole 51, the upper end of the piston inner hole 51 is provided with an annular end face 52, 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 in 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 limiting of the main piston 5 is realized; meanwhile, a circumferential through hole 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 the 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 processed at the transition position of a large excircle 19 and a small excircle 20 of a piston rod 2 and generally consists of a one-way valve and a normally through hole, the normally through hole is formed by connecting a small throttling hole 15 and a large throttling hole 16 in series, the small throttling hole 15 is close to an inner hole 10 of the piston rod, a rodless cavity of an oil-gas spring is communicated with the inner hole 10 of the piston rod, and oil in the rodless cavity sequentially enters the rod-shaped annular cavity 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 central position of 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 description 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.