CN117227383A

CN117227383A - Double-acting integrated type oil-gas suspension hydraulic system for special vehicle

Info

Publication number: CN117227383A
Application number: CN202311027449.2A
Authority: CN
Inventors: 侯秉睿; 王飞; 陈亮; 李大让; 蒋博文
Original assignee: Beijing Institute of Specialized Machinery
Current assignee: Beijing Institute of Specialized Machinery
Priority date: 2022-12-30
Filing date: 2023-08-15
Publication date: 2023-12-15
Also published as: CN116141904A

Abstract

The invention discloses a double-acting integrated hydro-pneumatic suspension hydraulic system for a special vehicle, which comprises an integrated hydraulic pump station, a first bridge left hydro-pneumatic spring cylinder, a first bridge right hydro-pneumatic spring cylinder, a second bridge left hydro-pneumatic spring cylinder and a second bridge right hydro-pneumatic spring cylinder, wherein a total oil supply pipeline and a total oil return pipeline are connected to the integrated hydraulic pump station, the total oil supply pipeline is respectively connected with rod cavities of the first bridge left hydro-pneumatic spring cylinder, the first bridge right hydro-pneumatic spring cylinder, the second bridge left hydro-pneumatic spring cylinder and the second bridge right hydro-pneumatic spring cylinder, and the total oil return pipeline is respectively connected with rodless cavities of the first bridge left hydro-pneumatic spring cylinder, the first bridge right hydro-pneumatic spring cylinder, the second bridge left hydro-pneumatic spring cylinder and the second bridge right hydro-pneumatic spring cylinder. The double-acting integrated type hydro-pneumatic suspension hydraulic system is comprehensive in function and reliable in performance and is used for special vehicles.

Description

Double-acting integrated type oil-gas suspension hydraulic system for special vehicle

The invention is claimed to be the priority of the application with the name of a hydro-pneumatic suspension hydraulic system, which is proposed by the applicant, and has the application date of 2022, 12 and 30, the application number of CN 202211730231.9. The entire contents of the above application are incorporated herein by reference in their entirety.

Technical Field

The invention relates to the field of hydraulic machinery, in particular to a double-acting integrated type oil-gas suspension hydraulic system for a special vehicle.

Background

The suspension system is an important component of special vehicles and common commercial vehicles, and plays an active role in damping and buffering the chassis, ensuring the stable running of the vehicles and the like. The special vehicle has more complex and various use conditions, for example: driving working condition, active lifting working condition, trench-crossing working condition, wall climbing working condition and the like. Special vehicles need to have excellent environmental and functional adaptability to each special condition. Therefore, in order to effectively ensure that the special vehicle can stably run under various complex working conditions and normally complete various special function indexes, the suspension system plays a vital role.

Currently, conventionally used suspension systems are mainly composed of spring suspensions, air suspensions, and hydro-pneumatic suspensions. The spring suspension and the air suspension have buffering functions, and vibration reduction in the normal running process of the vehicle can be basically guaranteed. The hydro-pneumatic suspension is generally composed of a hydraulic system and an energy storage system, and realizes the function of shock absorption under the combined action of compressed nitrogen and hydraulic oil, so the hydro-pneumatic suspension is also called a hydro-pneumatic suspension hydraulic system; meanwhile, the hydro-pneumatic suspension hydraulic system can realize the function of active driving under the control of the hydraulic system, and provides more active control capability for the chassis of the vehicle. Therefore, the hydro-pneumatic suspension hydraulic system is more suitable for special vehicles. As a key subsystem, the main function of the hydro-pneumatic suspension hydraulic system is to provide an optimal vehicle attitude state for a special vehicle through active driving and passive control.

With the improvement of the requirements on the running capability of special vehicles, the improvement of the requirements on the function diversity, the improvement of the adaptability to complex road conditions and the improvement of the operational adaptability, the existing hydro-pneumatic suspension hydraulic system can not meet the requirements, so that the research and development of the hydro-pneumatic suspension hydraulic system with comprehensive functions and reliable performance becomes particularly important.

Disclosure of Invention

The invention aims to solve the technical problem of providing a double-acting integrated type hydro-pneumatic suspension hydraulic system which has comprehensive functions and reliable performance and is used for special vehicles.

The invention relates to a double-acting integrated type hydro-pneumatic suspension hydraulic system for special vehicles, which comprises an integrated hydraulic pump station, a first bridge left hydro-pneumatic spring cylinder, a first bridge right hydro-pneumatic spring cylinder, a second bridge left hydro-pneumatic spring cylinder and a second bridge right hydro-pneumatic spring cylinder, wherein the integrated hydraulic pump station is connected with a total oil supply pipeline and a total oil return pipeline, the total oil supply pipeline is respectively connected with rod-free cavities of the first bridge left hydro-pneumatic spring cylinder, the first bridge right hydro-pneumatic spring cylinder, the second bridge left hydro-pneumatic spring cylinder and the second bridge right hydro-pneumatic spring cylinder through a first bridge left oil return pipeline, a first bridge right oil return pipeline, a second bridge left oil return pipeline and a second bridge right oil return pipeline,

The first bridge left oil-dividing and returning pipeline is connected with a first electromagnetic valve, the first bridge left oil-dividing and returning pipeline is connected with a second electromagnetic valve, a first pipeline and a second pipeline are respectively connected between the first bridge left oil-dividing and returning pipeline and the first bridge left oil-dividing and returning pipeline, a connecting point between the first pipeline and the first bridge left oil-dividing and returning pipeline is positioned at one side of the first electromagnetic valve, which is far away from the first bridge left oil-gas spring cylinder, a connecting point between the first pipeline and the first bridge left oil-returning pipeline is positioned at one side of the second electromagnetic valve, which is near to the first bridge left oil-gas spring cylinder, a third electromagnetic valve is connected to the first pipeline, a connecting point between the second pipeline and the first bridge left oil-dividing and-returning pipeline is positioned at one side of the first electromagnetic valve, which is far away from the first bridge left oil-gas spring cylinder, a fourth electromagnetic valve is connected to the second pipeline,

the second bridge left oil-dividing and returning pipeline is connected with a fifth electromagnetic valve, the second bridge left oil-dividing and returning pipeline is connected with a sixth electromagnetic valve, a third pipeline and a fourth pipeline are respectively connected between the second bridge left oil-dividing and returning pipeline and the second bridge left oil-dividing and returning pipeline, the connection point between the third pipeline and the second bridge left oil-dividing and returning pipeline is positioned at one side of the fifth electromagnetic valve far away from the second bridge left oil-gas spring cylinder, the connection point between the third pipeline and the second bridge left oil-returning pipeline is positioned at one side of the sixth electromagnetic valve near the second bridge left oil-gas spring cylinder, the third pipeline is connected with a seventh electromagnetic valve, the connection point between the fourth pipeline and the second bridge left oil-dividing and returning pipeline is positioned at one side of the fifth electromagnetic valve near the second bridge left oil-gas spring cylinder, the connection point between the fourth pipeline and the second bridge left oil-dividing and returning pipeline is positioned at one side of the sixth electromagnetic valve far away from the second bridge left oil-gas spring cylinder, the fourth pipeline is connected with an eighth electromagnetic valve,

A first balance pipeline is connected between the first bridge left branch oil return pipeline and the second bridge left branch oil return pipeline, a connection point between the first balance pipeline and the first bridge left branch oil return pipeline is positioned at one side of the second electromagnetic valve close to the first bridge left oil gas spring cylinder, a connection point between the first balance pipeline and the second bridge left branch oil return pipeline is positioned at one side of the sixth electromagnetic valve close to the second bridge left oil gas spring cylinder, a ninth electromagnetic valve is connected on the first balance pipeline,

the first bridge right oil-dividing and returning pipeline is connected with a tenth electromagnetic valve, the first bridge right oil-dividing and returning pipeline is connected with an eleventh electromagnetic valve, a fifth pipeline and a sixth pipeline are respectively connected between the first bridge right oil-dividing and returning pipeline and the first bridge right oil-dividing and returning pipeline, the connection point between the fifth pipeline and the first bridge right oil-dividing and returning pipeline is positioned at one side of the tenth electromagnetic valve far away from the first bridge right oil-gas spring cylinder, the connection point between the fifth pipeline and the first bridge right oil-dividing and returning pipeline is positioned at one side of the eleventh electromagnetic valve near the first bridge right oil-gas spring cylinder, the fifth pipeline is connected with a twelfth electromagnetic valve, the connection point between the sixth pipeline and the first bridge right oil-dividing and returning pipeline is positioned at one side of the tenth electromagnetic valve near the first bridge right oil-gas spring cylinder, the sixth pipeline is connected with a thirteenth electromagnetic valve,

The second bridge right oil-dividing and returning pipeline is connected with a fourteenth electromagnetic valve, the second bridge right oil-dividing and returning pipeline is connected with a fifteenth electromagnetic valve, a seventh pipeline and an eighth pipeline are respectively connected between the second bridge right oil-dividing and returning pipeline and the second bridge right oil-dividing and returning pipeline, the connection point between the seventh pipeline and the second bridge right oil-dividing pipeline is positioned at one side of the fourteenth electromagnetic valve far away from the second bridge right oil spring cylinder, the connection point between the seventh pipeline and the second bridge right oil-dividing and returning pipeline is positioned at one side of the fifteenth electromagnetic valve near the second bridge right oil spring cylinder, the seventh pipeline is connected with a sixteenth electromagnetic valve, the connection point between the eighth pipeline and the second bridge right oil-dividing and returning pipeline is positioned at one side of the fourteenth electromagnetic valve near the second bridge right oil spring cylinder, the eighth pipeline is connected with a seventeenth electromagnetic valve,

a second balance pipeline is connected between the first bridge right branch oil return pipeline and the second bridge right branch oil return pipeline, the connection point between the second balance pipeline and the first bridge right branch oil return pipeline is positioned at one side of the eleventh electromagnetic valve close to the first bridge right oil gas spring cylinder, the connection point between the second balance pipeline and the second bridge right branch oil return pipeline is positioned at one side of the fifteenth electromagnetic valve close to the second bridge right oil gas spring cylinder, the second balance pipeline is connected with an eighteenth electromagnetic valve,

The rodless cavity of the first bridge left hydro-pneumatic spring cylinder is connected with the first bridge left accumulator through a first bridge left energy storage pipeline, a first bridge left one-way throttle valve and a first bridge left electromagnetic valve are connected on the first bridge left energy storage pipeline, the rodless cavity of the second bridge left hydro-pneumatic spring cylinder is connected with the second bridge left accumulator through a second bridge left energy storage pipeline, a second bridge left one-way throttle valve and a second bridge left electromagnetic valve are connected on the second bridge left energy storage pipeline, the rodless cavity of the first bridge right hydro-pneumatic spring cylinder is connected with the first bridge right accumulator through a first bridge right energy storage pipeline, a first bridge right one-way throttle valve and a first bridge right electromagnetic valve are connected on the first bridge right energy storage pipeline, the rodless cavity of the second bridge right hydro-pneumatic spring cylinder is connected with the second bridge right accumulator through a second bridge right energy storage pipeline, and a second bridge right one-way throttle valve and a second bridge right electromagnetic valve are connected on the second bridge right energy storage pipeline.

The invention relates to a double-acting integrated hydro-pneumatic suspension hydraulic system for special vehicles, which also comprises a third bridge left hydro-pneumatic spring cylinder and a third bridge right hydro-pneumatic spring cylinder, wherein the total oil supply pipeline is respectively connected with rod cavities of the third bridge left hydro-pneumatic spring cylinder and the third bridge right hydro-pneumatic spring cylinder through a third bridge left oil distribution pipeline and a third bridge right oil distribution pipeline, the total oil return pipeline is respectively connected with rodless cavities of the third bridge left hydro-pneumatic spring cylinder and the third bridge right hydro-pneumatic spring cylinder through a third bridge left oil return pipeline and a third bridge right oil return pipeline,

The third bridge left branch oil supply pipeline is connected with a nineteenth electromagnetic valve, the third bridge left branch oil return pipeline is connected with a twenty-first electromagnetic valve, a ninth pipeline and a tenth pipeline are respectively connected between the third bridge left branch oil supply pipeline and the third bridge left branch oil return pipeline, the connection point between the ninth pipeline and the third bridge left branch oil supply pipeline is positioned at one side of the nineteenth electromagnetic valve far away from the third bridge left oil gas spring cylinder, the connection point between the ninth pipeline and the third bridge left branch oil return pipeline is positioned at one side of the twenty-first electromagnetic valve near the third bridge left oil gas spring cylinder, the ninth pipeline is connected with a twenty-first electromagnetic valve, the connection point between the tenth pipeline and the third bridge left branch oil supply pipeline is positioned at one side of the nineteenth electromagnetic valve near the third bridge left oil gas spring cylinder, the connection point between the tenth pipeline and the third bridge left branch oil return pipeline is positioned at one side of the twenty-first electromagnetic valve far away from the third bridge left oil gas spring cylinder, the tenth pipeline is connected with a twenty-second electromagnetic valve,

the third bridge right oil-dividing and returning pipeline is connected with a twenty-third electromagnetic valve, the third bridge right oil-dividing and returning pipeline is connected with a twenty-fourth electromagnetic valve, an eleventh pipeline and a twelfth pipeline are respectively connected between the third bridge right oil-dividing and returning pipeline and the third bridge right oil-dividing and returning pipeline, the connection point between the eleventh pipeline and the third bridge right oil-dividing and returning pipeline is positioned at one side of the twenty-third electromagnetic valve far away from the third bridge right oil-gas spring cylinder, the connection point between the eleventh pipeline and the third bridge right oil-dividing and returning pipeline is positioned at one side of the twenty-fourth electromagnetic valve near the third bridge right oil-gas spring cylinder, the eleventh pipeline is connected with a twenty-fifth electromagnetic valve, the connection point between the twelfth pipeline and the third bridge right oil-dividing and returning pipeline is positioned at one side of the twenty-third electromagnetic valve near the third bridge right oil-gas spring cylinder, the twelfth pipeline is connected with a twenty-sixth electromagnetic valve,

The rodless cavity of the third bridge left hydro-pneumatic spring cylinder is connected with a third bridge left energy accumulator through a third bridge left energy storage pipeline, a third bridge left one-way throttle valve and a third bridge left electromagnetic valve are connected on the third bridge left energy storage pipeline, the rodless cavity of the third bridge right hydro-pneumatic spring cylinder is connected with a third bridge right energy accumulator through a third bridge right energy storage pipeline, and a third bridge right one-way throttle valve and a third bridge right electromagnetic valve are connected on the third bridge right energy storage pipeline.

The invention relates to a double-acting integrated hydro-pneumatic suspension hydraulic system for special vehicles, which also comprises a fourth bridge left hydro-pneumatic spring cylinder and a fourth bridge right hydro-pneumatic spring cylinder, wherein the total oil supply pipeline is connected with rod cavities of the fourth bridge left hydro-pneumatic spring cylinder and the fourth bridge right hydro-pneumatic spring cylinder through a fourth bridge left oil distribution pipeline and a fourth bridge right oil distribution pipeline respectively, the total oil return pipeline is connected with rodless cavities of the fourth bridge left hydro-pneumatic spring cylinder and the fourth bridge right hydro-pneumatic spring cylinder through a fourth bridge left oil return pipeline and a fourth bridge right oil return pipeline respectively,

the twenty-seventh electromagnetic valve is connected on the fourth bridge left branch oil supply pipeline, the twenty-eighth electromagnetic valve is connected on the fourth bridge left branch oil return pipeline, a thirteenth pipeline and a fourteenth pipeline are respectively connected between the fourth bridge left branch oil supply pipeline and the fourth bridge left branch oil return pipeline, the connection point between the thirteenth pipeline and the fourth bridge left branch oil supply pipeline is positioned at one side of the twenty-seventh electromagnetic valve far away from the fourth bridge left oil spring cylinder, the connection point between the thirteenth pipeline and the fourth bridge left branch oil return pipeline is positioned at one side of the twenty-eighth electromagnetic valve near the fourth bridge left oil spring cylinder, the twenty-ninth electromagnetic valve is connected on the thirteenth pipeline, the connection point between the fourteenth pipeline and the fourth bridge left branch oil return pipeline is positioned at one side of the twenty-seventh electromagnetic valve near the fourth bridge left oil spring cylinder, the connection point between the fourteenth pipeline and the fourth bridge left branch oil return pipeline is positioned at one side of the twenty-eighth electromagnetic valve far away from the fourth bridge left oil spring cylinder, the thirty-eighth electromagnetic valve is connected on the fourteenth pipeline,

The fourth bridge right oil-dividing and returning pipeline is connected with a thirty-first electromagnetic valve, the fourth bridge right oil-dividing and returning pipeline is connected with a thirty-second electromagnetic valve, a fifteenth pipeline and a sixteenth pipeline are respectively connected between the fourth bridge right oil-dividing and returning pipeline and the fourth bridge right oil-dividing and returning pipeline, the connection point between the fifteenth pipeline and the fourth bridge right oil-dividing pipeline is positioned at one side of the thirty-first electromagnetic valve far away from the fourth bridge right oil-gas spring cylinder, the connection point between the fifteenth pipeline and the fourth bridge right oil-dividing and returning pipeline is positioned at one side of the thirty-second electromagnetic valve near the fourth bridge right oil-gas spring cylinder, the fifteenth pipeline is connected with a thirty-third electromagnetic valve, the connection point between the sixteenth pipeline and the fourth bridge right oil-dividing and returning pipeline is positioned at one side of the thirty-second electromagnetic valve near the fourth bridge right oil-gas spring cylinder, the sixteenth pipeline is connected with the thirty-fourth electromagnetic valve,

the rodless cavity of the fourth bridge left hydro-pneumatic spring cylinder is connected with a fourth bridge left energy accumulator through a fourth bridge left energy storage pipeline, a fourth bridge left one-way throttle valve and a fourth bridge left electromagnetic valve are connected on the fourth bridge left energy storage pipeline, the rodless cavity of the fourth bridge right hydro-pneumatic spring cylinder is connected with a fourth bridge right energy accumulator through a fourth bridge right energy storage pipeline, and a fourth bridge right one-way throttle valve and a fourth bridge right electromagnetic valve are connected on the fourth bridge right energy storage pipeline.

The invention discloses a double-acting integrated oil-gas suspension hydraulic system for a special vehicle, wherein a third balance pipeline is connected between a third bridge left branch oil return pipeline and a fourth bridge left branch oil return pipeline, a connection point between the third balance pipeline and the third bridge left branch oil return pipeline is positioned at one side of a twenty-eighth electromagnetic valve close to a third bridge left oil-gas spring cylinder, a connection point between the third balance pipeline and the fourth bridge left branch oil return pipeline is positioned at one side of a twenty-eighth electromagnetic valve close to a fourth bridge left oil-gas spring cylinder, and a thirty-fifth electromagnetic valve is connected to the third balance pipeline.

The invention discloses a double-acting integrated oil-gas suspension hydraulic system for a special vehicle, wherein a fourth balance pipeline is connected between a third bridge right branch oil return pipeline and a fourth bridge right branch oil return pipeline, a connection point between the fourth balance pipeline and the third bridge right branch oil return pipeline is positioned at one side of a twenty-fourth electromagnetic valve close to a third bridge right oil-gas spring cylinder, a connection point between the fourth balance pipeline and the fourth bridge right branch oil return pipeline is positioned at one side of a thirty-second electromagnetic valve close to the fourth bridge right oil-gas spring cylinder, and a thirty-sixth electromagnetic valve is connected to the fourth balance pipeline.

The invention discloses a double-acting integrated oil-gas suspension hydraulic system for a special vehicle, wherein the integrated hydraulic pump station comprises an oil tank, a double-pump and a three-position four-way electromagnetic reversing valve, the oil supply port of the oil tank is connected with an overall oil supply pipeline, the oil return port of the oil tank is connected with an overall oil return pipeline, the double-pump and the three-position four-way electromagnetic reversing valve are sequentially connected onto the overall oil supply pipeline along the oil supply direction, the double-pump is driven by a servo motor, two ends of the overall oil supply pipeline between the double-pump and the three-position four-way electromagnetic reversing valve are respectively connected onto a large-flow pump of the double-pump and a first inlet of the three-position four-way electromagnetic reversing valve, the overall oil supply pipeline, which is far away from one side of the double-pump, of the three-position four-way electromagnetic reversing valve is connected onto a first outlet of the three-position four-way electromagnetic reversing valve, a small-flow pump of the double-pump is connected with a second inlet of the three-position four-way electromagnetic reversing valve through the first pipeline, a second outlet of the three-position four-way electromagnetic reversing valve is connected with the overall oil supply pipeline through a second pipeline, and an overflow pump station is connected onto the third pump station.

The invention relates to a double-acting integrated oil-gas suspension hydraulic system for a special vehicle, wherein an oil supply filter is connected to a total oil supply pipeline between an oil tank and a duplex pump, an oil return filter is connected to a total oil return pipeline, and a second pump station pipeline is connected to a total oil return pipeline of one side of the oil return filter, which is far away from the oil tank.

The invention relates to a double-acting integrated type oil-gas suspension hydraulic system for a special vehicle, wherein an air filter and a liquid level meter are further arranged on an oil tank.

The invention discloses a double-acting integrated type hydro-pneumatic suspension hydraulic system for a special vehicle, which further comprises a first angle sensor, a second angle sensor, a third angle sensor and a fourth angle sensor, wherein the first angle sensor is arranged near a left hydro-pneumatic spring cylinder of a first bridge, the second angle sensor is arranged near a right hydro-pneumatic spring cylinder of the first bridge, the third angle sensor is arranged near a left hydro-pneumatic spring cylinder of a fourth bridge, the fourth angle sensor is arranged near a right hydro-pneumatic spring cylinder of the fourth bridge, and the first angle sensor, the second angle sensor, the third angle sensor and the fourth angle sensor are all used for measuring the height of a chassis of the special vehicle.

The invention provides a double-acting integrated type oil-gas suspension hydraulic system for a special vehicle, wherein the fourth electromagnetic valve, the eighth electromagnetic valve, the thirteenth electromagnetic valve, the seventeenth electromagnetic valve, the twenty-second electromagnetic valve, the twenty-sixth electromagnetic valve, the thirty-first electromagnetic valve, the thirty-second electromagnetic valve, the thirty-third electromagnetic valve, the thirteenth electromagnetic valve, the sixth electromagnetic valve, the seventh electromagnetic valve, the ninth electromagnetic valve, the tenth electromagnetic valve, the eleventh electromagnetic valve, the twelfth electromagnetic valve, the fourteenth electromagnetic valve, the fifteenth electromagnetic valve, the sixteenth electromagnetic valve, the eighteenth electromagnetic valve, the nineteenth electromagnetic valve, the twenty-first electromagnetic valve, the twenty-third electromagnetic valve, the twenty-fourth electromagnetic valve, the twenty-fifth electromagnetic valve, the twenty-seventh electromagnetic valve, the twenty-eighth electromagnetic valve, the twenty-ninth electromagnetic valve, the thirty-first electromagnetic valve, the thirty-second electromagnetic valve, the thirty-third electromagnetic valve, the thirty-fifth electromagnetic valve and the thirty-sixth electromagnetic valve are all normally-closed two-second electromagnetic valves.

The double-acting integrated type hydro-pneumatic suspension hydraulic system for the special vehicle is different from the prior art in that the hydraulic system has an active driving mode and a passive damping mode. In the active driving mode, the lifting active control function, namely the single-cylinder independent lifting function, the whole vehicle rapid lifting function, the traction preparation function, the side tilting function and the like, is completed through the integrated hydraulic pump station, the electromagnetic valve group and the hydro-pneumatic spring cylinder. Under the passive damping mode, the passive self-adaptive elastic damping function is completed through the energy accumulator and the hydro-pneumatic spring cylinders, and the two hydro-pneumatic spring cylinders on each side are communicated through the balance pipeline, so that balance of oil liquid between rodless cavities of the two hydro-pneumatic spring cylinders is realized. The invention has the characteristics of self-adaptive elastic shock absorption and impact resistance under the passive shock absorption mode, and provides stable and safe guarantee for the operation of special vehicles under various complex road conditions.

The invention is further described below with reference to the accompanying drawings.

Drawings

Fig. 1 is a schematic diagram of the dual-acting integrated hydro-pneumatic suspension hydraulic system for a specialty vehicle of the present invention.

Detailed Description

As shown in fig. 1, the double-acting integrated type hydro-pneumatic suspension hydraulic system for a special vehicle comprises an integrated hydraulic pump station 1, a first bridge left hydro-pneumatic spring cylinder 22, a first bridge right hydro-pneumatic spring cylinder 18, a second bridge left hydro-pneumatic spring cylinder 23 and a second bridge right hydro-pneumatic spring cylinder 19, wherein a total oil supply pipeline 119 and a total oil return pipeline 111 are connected to the integrated hydraulic pump station 1, the total oil supply pipeline 119 is respectively connected with the first bridge left hydro-pneumatic spring cylinder 22, the first bridge right hydro-pneumatic spring cylinder 18, the second bridge left hydro-pneumatic spring cylinder 23 and the second bridge right hydro-pneumatic spring cylinder 19 through a first bridge left oil supply pipeline 602, a first bridge right oil supply pipeline 206, a second bridge left oil supply pipeline 702 and a second bridge right oil supply pipeline 302, and rod cavities of the first bridge left hydro-pneumatic spring cylinder 22, the first bridge right hydro-pneumatic spring cylinder 18, the second bridge left hydro-pneumatic spring cylinder 23 and the second bridge right hydro-pneumatic spring cylinder 19 through a first bridge left oil return pipeline 606, a first bridge right oil return pipeline 201, a second bridge left oil return pipeline 706 and a second bridge right oil return pipeline 306, and a second bridge left oil supply pipeline 23.

The first bridge left branch oil supply pipeline 602 is connected with a first electromagnetic valve 601, the first bridge left branch oil return pipeline 606 is connected with a second electromagnetic valve 607, a first pipeline 603 and a second pipeline 605 are respectively connected between the first bridge left branch oil supply pipeline 602 and the first bridge left branch oil return pipeline 606, a connecting point between the first pipeline 603 and the first bridge left branch oil supply pipeline 602 is located at one side, far away from the first bridge left spring cylinder 22, of the first electromagnetic valve 601, a connecting point between the first pipeline 603 and the first bridge left branch oil return pipeline 606 is located at one side, close to the first bridge left spring cylinder 22, of the second electromagnetic valve 607, a third electromagnetic valve 608 is connected to the first pipeline 603, a connecting point between the second pipeline 605 and the first bridge left branch oil return pipeline 602 is located at one side, close to the first bridge left spring cylinder 22, of the second electromagnetic valve 601, a connecting point between the second pipeline 605 and the first bridge left branch oil return pipeline 606 is located at one side, far away from the first bridge left spring cylinder 22, of the second electromagnetic valve 605 is connected with a fourth electromagnetic valve 604.

The second bridge left oil distribution pipeline 702 is connected with a fifth electromagnetic valve 701, the second bridge left oil distribution pipeline 706 is connected with a sixth electromagnetic valve 707, a third pipeline 703 and a fourth pipeline 705 are respectively connected between the second bridge left oil distribution pipeline 702 and the second bridge left oil distribution pipeline 706, a connection point between the third pipeline 703 and the second bridge left oil distribution pipeline 702 is located at one side, far away from the second bridge left oil vapor spring cylinder 23, of the fifth electromagnetic valve 701, a connection point between the third pipeline 703 and the second bridge left oil distribution pipeline 706 is located at one side, close to the second bridge left oil vapor spring cylinder 23, of the sixth electromagnetic valve 707, a seventh electromagnetic valve 708 is connected to the third pipeline 703, a connection point between the fourth pipeline 705 and the second bridge left oil distribution pipeline 702 is located at one side, close to the second bridge left oil vapor spring cylinder 23, of the sixth electromagnetic valve 701 is located at one side, far away from the second bridge left oil vapor spring cylinder 23, and the fourth electromagnetic valve 704 is connected with the eighth electromagnetic valve.

The first balance pipeline 30 is connected between the first bridge left branch oil return pipeline 606 and the second bridge left branch oil return pipeline 706, a connection point between the first balance pipeline 30 and the first bridge left branch oil return pipeline 606 is located on one side, close to the first bridge left hydro-pneumatic spring cylinder 22, of the second electromagnetic valve 607, a connection point between the first balance pipeline 30 and the second bridge left branch oil return pipeline 706 is located on one side, close to the second bridge left hydro-pneumatic spring cylinder 23, of the sixth electromagnetic valve 707, and a ninth electromagnetic valve 609 is connected to the first balance pipeline 30.

The first bridge right oil distribution and return pipeline 206 is connected with a tenth electromagnetic valve 205, the first bridge right oil distribution and return pipeline 201 is connected with an eleventh electromagnetic valve 202, a fifth pipeline 207 and a sixth pipeline 209 are respectively connected between the first bridge right oil distribution and return pipeline 206 and the first bridge right oil distribution and return pipeline 201, a connection point between the fifth pipeline 207 and the first bridge right oil distribution and return pipeline 206 is located at one side, far away from the first bridge right oil and gas spring cylinder 18, of the tenth electromagnetic valve 205, a connection point between the fifth pipeline 207 and the first bridge right oil distribution and return pipeline 201 is located at one side, close to the first bridge right oil and gas spring cylinder 18, of the eleventh electromagnetic valve 202, a twelfth electromagnetic valve 203 is connected to the fifth pipeline 207, a connection point between the sixth pipeline 209 and the first bridge right oil distribution and return pipeline 206 is located at one side, close to the first bridge right oil and gas spring cylinder 18, a connection point between the sixth pipeline 209 and the first bridge right oil distribution and return pipeline 201 is located at one side, far away from the first bridge right oil and gas spring cylinder 18, of the eleventh electromagnetic valve 202, and a thirteenth electromagnetic valve 208 is connected to the sixth electromagnetic valve 208.

The fourteenth electromagnetic valve 301 is connected to the second bridge right oil distribution and return pipeline 302, the fifteenth electromagnetic valve 307 is connected to the second bridge right oil distribution and return pipeline 306, a seventh pipeline 303 and an eighth pipeline 305 are connected between the second bridge right oil distribution and return pipeline 302 and the second bridge right oil distribution and return pipeline 306, a connection point between the seventh pipeline 303 and the second bridge right oil distribution and return pipeline 302 is located at one side, away from the second bridge right oil and gas spring cylinder 19, of the fourteenth electromagnetic valve 301, a connection point between the seventh pipeline 303 and the second bridge right oil distribution and return pipeline 306 is located at one side, close to the second bridge right oil and gas spring cylinder 19, of the fifteenth electromagnetic valve 307, a sixteenth electromagnetic valve 308 is connected to the seventh pipeline 303, a connection point between the eighth pipeline 305 and the second bridge right oil distribution and return pipeline 302 is located at one side, close to the second bridge right oil and gas spring cylinder 19, of the fifteenth electromagnetic valve 307 is located at one side, away from the second bridge right oil and gas spring cylinder 19, of the eighth electromagnetic valve 305 is connected to the seventeenth electromagnetic valve 305.

A second balance pipeline 32 is connected between the first bridge right branch oil return pipeline 201 and the second bridge right branch oil return pipeline 306, a connection point between the second balance pipeline 32 and the first bridge right branch oil return pipeline 201 is located on one side, close to the first bridge right hydro-pneumatic spring cylinder 18, of the eleventh electromagnetic valve 202, a connection point between the second balance pipeline 32 and the second bridge right branch oil return pipeline 306 is located on one side, close to the second bridge right hydro-pneumatic spring cylinder 19, of the fifteenth electromagnetic valve 307, and an eighteenth electromagnetic valve 204 is connected to the second balance pipeline 32.

The rodless cavity of the first bridge left hydro-pneumatic spring cylinder 22 is connected with the first bridge left accumulator 14 through a first bridge left energy storage pipeline 34, a first bridge left one-way throttle valve 36 and a first bridge left electromagnetic valve 35 are connected on the first bridge left energy storage pipeline 34, the rodless cavity of the second bridge left hydro-pneumatic spring cylinder 23 is connected with the second bridge left accumulator 15 through a second bridge left energy storage pipeline 37, a second bridge left one-way throttle valve 39 and a second bridge left electromagnetic valve 38 are connected on the second bridge left energy storage pipeline 37, the rodless cavity of the first bridge right hydro-pneumatic spring cylinder 18 is connected with the first bridge right accumulator 10 through a first bridge right energy storage pipeline 55, a first bridge right one-way throttle valve 57 and a first bridge right electromagnetic valve 56 are connected on the first bridge right energy storage pipeline 55, the rodless cavity of the second bridge right hydro-pneumatic spring cylinder 19 is connected with the second bridge right accumulator 11 through a second bridge right energy storage pipeline 52, and a second bridge right one-way throttle valve 53 and a second bridge right electromagnetic valve 54 are connected on the second bridge right energy storage pipeline 52.

The invention relates to a double-acting integrated type hydro-pneumatic suspension hydraulic system for a special vehicle, which also comprises a third bridge left hydro-pneumatic spring cylinder 24 and a third bridge right hydro-pneumatic spring cylinder 20, wherein the total oil supply pipeline 119 is connected with rod cavities of the third bridge left hydro-pneumatic spring cylinder 24 and the third bridge right hydro-pneumatic spring cylinder 20 through a third bridge left sub oil supply pipeline 802 and a third bridge right sub oil supply pipeline 402 respectively, and the total oil return pipeline 111 is connected with rod-free cavities of the third bridge left hydro-pneumatic spring cylinder 24 and the third bridge right hydro-pneumatic spring cylinder 20 through a third bridge left sub oil return pipeline 806 and a third bridge right sub oil return pipeline 406 respectively.

The nineteenth electromagnetic valve 801 is connected to the third bridge left branch oil supply pipeline 802, the twenty-first electromagnetic valve 808 is connected to the third bridge left branch oil return pipeline 806, a ninth pipeline 803 and a tenth pipeline 805 are connected between the third bridge left branch oil supply pipeline 802 and the third bridge left branch oil return pipeline 806, a connection point between the ninth pipeline 803 and the third bridge left branch oil supply pipeline 802 is located at one side, far from the third bridge left oil gas spring cylinder 24, of the nineteenth electromagnetic valve 801, a connection point between the ninth pipeline 803 and the third bridge left branch oil return pipeline 806 is located at one side, close to the third bridge left oil gas spring cylinder 24, of the twenty-first electromagnetic valve 808 is connected to the ninth pipeline 803, a connection point between the tenth pipeline 805 and the third bridge left branch oil supply pipeline 802 is located at one side, close to the third bridge left oil gas spring cylinder 24, of the twenty-first electromagnetic valve 801 is located at one side, far from the third bridge left oil gas spring 24, and the twenty-first electromagnetic valve 805 is connected to the twenty-first electromagnetic valve 803.

The third bridge right oil distribution and return pipeline 402 is connected with a twenty-third electromagnetic valve 401, the third bridge right oil distribution and return pipeline 406 is connected with a twenty-fourth electromagnetic valve 407, an eleventh pipeline 403 and a twelfth pipeline 405 are respectively connected between the third bridge right oil distribution and return pipeline 402 and the third bridge right oil distribution and return pipeline 406, a connection point between the eleventh pipeline 403 and the third bridge right oil distribution and return pipeline 402 is located at one side, far from the third bridge right oil and gas spring cylinder 20, of the twenty-third electromagnetic valve 401, a connection point between the eleventh pipeline 403 and the third bridge right oil distribution and return pipeline 406 is located at one side, near to the third bridge right oil and gas spring cylinder 20, of the twenty-fourth electromagnetic valve 407, a twenty-fifth electromagnetic valve 408 is connected to the eleventh pipeline 403, a connection point between the twelfth pipeline 405 and the third bridge right oil distribution and return pipeline 406 is located at one side, near to the third bridge right oil and gas spring cylinder 20, a connection point between the twelfth pipeline 405 and the third bridge right oil and return pipeline 406 is located at one side, far from the third bridge right oil and gas spring cylinder 20, and the twenty-fifth electromagnetic valve 405 is connected with the twenty-fifth electromagnetic valve 404.

The rodless cavity of the third bridge left hydro-pneumatic spring cylinder 24 is connected with the third bridge left accumulator 16 through a third bridge left energy storage pipeline 40, a third bridge left one-way throttle valve 42 and a third bridge left electromagnetic valve 41 are connected on the third bridge left energy storage pipeline 40, the rodless cavity of the third bridge right hydro-pneumatic spring cylinder 20 is connected with the third bridge right accumulator 12 through a third bridge right energy storage pipeline 49, and a third bridge right one-way throttle valve 51 and a third bridge right electromagnetic valve 50 are connected on the third bridge right energy storage pipeline 49.

The invention relates to a double-acting integrated hydro-pneumatic suspension hydraulic system for special vehicles, which also comprises a fourth bridge left hydro-pneumatic spring cylinder 25 and a fourth bridge right hydro-pneumatic spring cylinder 21, wherein the total oil supply pipeline 119 is connected with rod cavities of the fourth bridge left hydro-pneumatic spring cylinder 25 and the fourth bridge right hydro-pneumatic spring cylinder 21 through a fourth bridge left sub oil supply pipeline 902 and a fourth bridge right sub oil supply pipeline 505 respectively, and the total oil return pipeline 111 is connected with rod-free cavities of the fourth bridge left hydro-pneumatic spring cylinder 25 and the fourth bridge right hydro-pneumatic spring cylinder 21 through a fourth bridge left sub oil return pipeline 906 and a fourth bridge right sub oil return pipeline 508 respectively.

The twenty-seventh electromagnetic valve 901 is connected to the fourth bridge left oil distribution and return pipeline 902, the twenty-eighth electromagnetic valve 907 is connected to the fourth bridge left oil distribution and return pipeline 906, a thirteenth pipeline 903 and a fourteenth pipeline 905 are connected between the fourth bridge left oil distribution and return pipeline 902 and the fourth bridge left oil distribution and return pipeline 906, a connection point between the thirteenth pipeline 903 and the fourth bridge left oil distribution and return pipeline 902 is located at one side, far from the fourth bridge left oil and gas spring cylinder 25, of the twenty-seventh electromagnetic valve 901, a connection point between the thirteenth pipeline 903 and the fourth bridge left oil distribution and return pipeline 906 is located at one side, near to the fourth bridge left oil and gas spring cylinder 25, of the twenty-eighth electromagnetic valve 907, a twenty-ninth electromagnetic valve 908 is connected to the thirteenth pipeline 903, a connection point between the fourteenth pipeline 905 and the fourth bridge left oil distribution and return pipeline 906 is located at one side, near to the fourth bridge left oil and gas spring cylinder 25, a connection point between the fourteenth pipeline 905 and the fourth bridge left oil and return pipeline 906 is located at one side, far from the fourth bridge left oil and gas spring cylinder 25, and the thirty-eighth electromagnetic valve 903 is connected to the thirty-eighth electromagnetic valve 904.

The fourth bridge right oil distribution and return pipeline 505 is connected with a thirty-first electromagnetic valve 501, the fourth bridge right oil distribution and return pipeline 508 is connected with a thirty-second electromagnetic valve 504, a fifteenth pipeline 506 and a sixteenth pipeline 507 are respectively connected between the fourth bridge right oil distribution and return pipeline 505 and the fourth bridge right oil distribution and return pipeline 508, a connection point between the fifteenth pipeline 506 and the fourth bridge right oil distribution and return pipeline 505 is positioned on one side of the thirty-first electromagnetic valve 501 far away from the fourth bridge right oil and gas spring cylinder 21, a connection point between the fifteenth pipeline 506 and the fourth bridge right oil distribution and return pipeline 508 is positioned on one side of the thirty-second electromagnetic valve 504 near the fourth bridge right oil and gas spring cylinder 21, a thirty-third electromagnetic valve 503 is connected to the fifteenth pipeline 506, a connection point between the sixteenth pipeline 507 and the fourth bridge right oil distribution and return pipeline 505 is positioned on one side of the thirty-first electromagnetic valve 501 near the fourth bridge right oil and gas spring cylinder 21, a connection point between the sixteenth pipeline 507 and the fourth bridge right oil distribution and return pipeline 508 is positioned on one side of the thirty-second electromagnetic valve 504 far away from the fourth bridge right oil and gas spring cylinder 21, and the thirty-first electromagnetic valve 502 is connected with the fourth electromagnetic valve 502.

The rodless cavity of the fourth bridge left hydro-pneumatic spring cylinder 25 is connected with the fourth bridge left accumulator 17 through a fourth bridge left energy storage pipeline 43, a fourth bridge left one-way throttle valve 45 and a fourth bridge left electromagnetic valve 44 are connected on the fourth bridge left energy storage pipeline 43, the rodless cavity of the fourth bridge right hydro-pneumatic spring cylinder 21 is connected with the fourth bridge right accumulator 13 through a fourth bridge right energy storage pipeline 46, and a fourth bridge right one-way throttle valve 48 and a fourth bridge right electromagnetic valve 47 are connected on the fourth bridge right energy storage pipeline 46.

The invention relates to a double-acting integrated type hydro-pneumatic suspension hydraulic system for a special vehicle, wherein a third balance pipeline 31 is connected between a third bridge left branch oil return pipeline 806 and a fourth bridge left branch oil return pipeline 906, a connection point between the third balance pipeline 31 and the third bridge left branch oil return pipeline 806 is positioned on one side of a twenty-eighth electromagnetic valve 807 close to a third bridge left hydro-pneumatic spring cylinder 24, a connection point between the third balance pipeline 31 and the fourth bridge left branch oil return pipeline 906 is positioned on one side of a twenty-eighth electromagnetic valve 907 close to a fourth bridge left hydro-pneumatic spring cylinder 25, and a thirty-fifth electromagnetic valve 809 is connected on the third balance pipeline 31.

The invention relates to a double-acting integrated type hydro-pneumatic suspension hydraulic system for a special vehicle, wherein a fourth balance pipeline 33 is connected between a third bridge right branch oil return pipeline 406 and a fourth bridge right branch oil return pipeline 508, a connection point between the fourth balance pipeline 33 and the third bridge right branch oil return pipeline 406 is positioned at one side of a twenty-fourth electromagnetic valve 407 close to a third bridge right hydro-pneumatic spring cylinder 20, a connection point between the fourth balance pipeline 33 and the fourth bridge right branch oil return pipeline 508 is positioned at one side of a thirty-second electromagnetic valve 504 close to a fourth bridge right hydro-pneumatic spring cylinder 21, and a thirty-sixth electromagnetic valve 409 is connected to the fourth balance pipeline 33.

The invention discloses a double-acting integrated oil-gas suspension hydraulic system for special vehicles, wherein the integrated hydraulic pump station 1 comprises an oil tank 109, a double-pump 120 and a three-position four-way electromagnetic reversing valve 108, wherein an oil supply port of the oil tank 109 is connected with a total oil supply pipeline 119, an oil return port of the oil tank 109 is connected with a total oil return pipeline 111, the double-pump 120 and the three-position four-way electromagnetic reversing valve 108 are sequentially connected to the total oil supply pipeline 119 along an oil supply direction, the double-pump 120 is driven by a servo motor 101, two ends of the total oil supply pipeline 119 between the double-pump 120 and the three-position four-way electromagnetic reversing valve 108 are respectively connected to a large-flow pump 110 of the double-pump 120 and a first inlet 117 of the three-position four-way electromagnetic reversing valve 108, the total oil supply pipeline 119 of one side of the three-position four-way electromagnetic reversing valve 108 is connected to a first outlet 116 of the three-position four-way electromagnetic reversing valve 108, a small-flow pump 102 of the double-pump 120 is connected to a second inlet 118 of the three-position four-way electromagnetic reversing valve 108 through a first pipeline 112, the second inlet 113 is connected to the three-position four-way electromagnetic reversing valve 108 through a second inlet 118 of the first pipeline 112 and a third pipeline 113, and the third pump station 114 is connected to the third pump station 114 through the third pipeline 114.

The invention relates to a double-acting integrated type oil-gas suspension hydraulic system for a special vehicle, wherein an oil supply filter 103 is connected to a total oil supply pipeline 119 between an oil tank 109 and a duplex pump 120, an oil return filter 106 is connected to a total oil return pipeline 111, and a second pump station pipeline 113 is connected to the total oil return pipeline 111 of the oil return filter 106 on the side far away from the oil tank 109.

The invention is a double-acting integrated type hydro-pneumatic suspension hydraulic system for special vehicles, wherein an air filter 104 and a liquid level meter 105 are also arranged on the oil tank 109.

The invention relates to a double-acting integrated hydro-pneumatic suspension hydraulic system for a special vehicle, which further comprises a first angle sensor 26, a second angle sensor 27, a third angle sensor 29 and a fourth angle sensor 28, wherein the first angle sensor 26 is arranged near a first bridge left hydro-pneumatic spring cylinder 22, the second angle sensor 27 is arranged near a first bridge right hydro-pneumatic spring cylinder 18, the third angle sensor 29 is arranged near a fourth bridge left hydro-pneumatic spring cylinder 25, the fourth angle sensor 28 is arranged near a fourth bridge right hydro-pneumatic spring cylinder 21, and the first angle sensor 26, the second angle sensor 27, the third angle sensor 29 and the fourth angle sensor 28 are all used for measuring the height of a chassis of the special vehicle.

The present invention provides a double-acting integrated hydro-pneumatic suspension hydraulic system for a special vehicle, wherein the fourth solenoid valve 604, the eighth solenoid valve 704, the thirteenth solenoid valve 208, the seventeenth solenoid valve 304, the twenty-second solenoid valve 804, the twenty-sixth solenoid valve 404, the thirty-fifth solenoid valve 904 and the thirty-fourth solenoid valve 502 are all normally open two-position two-way solenoid valves, and the first solenoid valve 601, the second solenoid valve 607, the third solenoid valve 608, the fifth solenoid valve 701, the sixth solenoid valve 707, the seventh solenoid valve 708, the ninth solenoid valve 609, the tenth solenoid valve 205, the eleventh solenoid valve 202, the twelfth solenoid valve 203, the fourteenth solenoid valve 301, the fifteenth solenoid valve 307, the sixteenth solenoid valve 308, the eighteenth solenoid valve 204, the nineteenth solenoid valve 801, the twenty-eighth solenoid valve 807, the twenty-first solenoid valve 808, the twenty-third solenoid valve 401, the twenty-fifth solenoid valve 408, the twenty-seventh solenoid valve 901, the twenty-eighth solenoid valve 907, the twenty-ninth solenoid valve 908, the thirty-first solenoid valve 501, the thirty-second solenoid valve 504, the thirty-third solenoid valve 503, the thirty-fifth solenoid valve 809 and the thirty-sixth solenoid valve 409 are all normally closed two-position two-way solenoid valves.

The double-acting integrated type hydro-pneumatic suspension hydraulic system for the special vehicle is different from the prior art in that the hydraulic system has an active driving mode and a passive damping mode. In the active driving mode, the lifting active control function, namely the single-cylinder independent lifting function, the whole vehicle rapid lifting function, the traction preparation function, the side tilting function and the like, is completed through the integrated hydraulic pump station 1, the electromagnetic valve group and the hydro-pneumatic spring cylinder. Under the passive damping mode, the passive self-adaptive elastic damping function is completed through the energy accumulator and the hydro-pneumatic spring cylinders, and the two hydro-pneumatic spring cylinders on each side are communicated through the balance pipeline, so that balance of oil liquid between rodless cavities of the two hydro-pneumatic spring cylinders is realized. The invention has the characteristics of self-adaptive elastic shock absorption and impact resistance under the passive shock absorption mode, and provides stable and safe guarantee for the operation of special vehicles under various complex road conditions.

The invention can provide a multifunctional and self-adaptive suspension system for special vehicles and a powerful support for the special vehicles to adapt to various complex working conditions.

In the aspect of integration of the hydro-pneumatic suspension hydraulic system, in order to improve the integration degree of the system and facilitate arrangement and later maintenance in a special vehicle, the integrated hydraulic pump station 1 adopts a modularized design, and the servo motor 101, the duplex pump 120, the oil supply filter 103, the air filter 104, the liquid level meter 105, the oil return filter 106, the overflow valve 107 and the three-position four-way electromagnetic directional valve 108 are arranged in a centralized manner, so that the occupied space is small and the maintenance is convenient.

In addition, the electromagnetic valve for controlling the action of each hydro-pneumatic spring cylinder adopts an integrated design. The first solenoid valve 601, the second solenoid valve 607, the third solenoid valve 608, the fourth solenoid valve 604 and the ninth solenoid valve 609 at the first bridge left stitch valve cylinder 22 together form the first bridge left integrated control valve bank 6, the fifth solenoid valve 701, the sixth solenoid valve 707, the seventh solenoid valve 708 and the eighth solenoid valve 704 at the second bridge left stitch valve cylinder 23 together form the second bridge left integrated control valve bank 7, the tenth solenoid valve 205, the eleventh solenoid valve 202, the twelfth solenoid valve 203, the thirteenth solenoid valve 208 and the eighteenth solenoid valve 204 at the first bridge right stitch valve cylinder 18 together form the first bridge right integrated control valve bank 2, the fourteenth solenoid valve 301, the fifteenth solenoid valve 307, the sixteenth solenoid valve 308 and the seventeenth solenoid valve 304 at the second bridge right stitch valve cylinder 19 together form the second bridge right integrated control valve bank 3, the nineteenth solenoid valve 801, the twentieth solenoid valve 807, the twenty first solenoid valve 808, the twenty second solenoid valve 804, and the thirty fifth solenoid valve 809 at the third bridge left spring cylinder 24 collectively form the third bridge left integrated control valve bank 8, the twenty third solenoid valve 401, the twenty fourth solenoid valve 407, the twenty fifth solenoid valve 408, the twenty sixth solenoid valve 404, and the thirty sixth solenoid valve 409 at the third bridge right spring cylinder 20 collectively form the third bridge right integrated control valve bank 4, the twenty seventh solenoid valve 901, the twenty eighth solenoid valve 907, the twenty ninth solenoid valve 908, and the thirty fifth solenoid valve 904 at the fourth bridge left spring cylinder 25 collectively form the fourth bridge left integrated control valve bank 9, the thirty first solenoid valve 501, the thirty second solenoid valve 504, the thirty third solenoid valve 503, and the thirty fourth solenoid valve 502 at the fourth bridge right spring cylinder 21 collectively form the fourth bridge right integrated control valve bank 5, the pipeline connection of the whole system is simple and clear, the integration level is high, and the later maintenance is convenient.

The oil-gas suspension hydraulic system adopts a symmetrical design thought, and pipeline connection is clear and tidy; due to symmetrical system arrangement, the oil supply path consistency of the integrated hydraulic pump station 1 to each hydro-pneumatic spring cylinder is ensured, and the problem of the asynchronous property of multiple cylinders is avoided.

In the aspect of double acting of the hydro-pneumatic suspension hydraulic system, the invention has both an active driving mode and a passive damping mode.

In the present invention, the active driving modes of the first bridge left, the second bridge left, the third bridge left, the fourth bridge left, the first bridge right, the second bridge right, the third bridge right, and the fourth bridge right are the same; the passive damping mode between the first bridge left and the second bridge left, the passive damping mode between the third bridge left and the fourth bridge left, the passive damping mode between the first bridge right and the second bridge right, and the passive damping mode between the third bridge right and the fourth bridge right are the same.

In an active driving mode, the hydro-pneumatic suspension hydraulic system completes an active lifting control function through an integrated hydraulic pump station 1, an integrated control valve group and a hydro-pneumatic spring cylinder, and provides lifting in-place signals through an angle sensor; and a controller sends a control command, and a corresponding electromagnetic valve in the integrated control valve group realizes switching action according to the command, so that the active control function of multiple modes is realized. The active control function is as follows: single cylinder independent lift function (in this mode, single cylinder independent control is required to have low speed, so the small flow pump 102 of the dual pump 120 needs to be controlled to work, and the low speed fine adjustment of a single hydro-pneumatic spring cylinder is controlled), whole vehicle rapid lift function, traction preparation function, roll function, and the like.

As described above, since the manner in which each of the hydro-pneumatic spring cylinders is driven to expand and contract to complete the lifting is the same, the hydro-pneumatic spring cylinder at the left of the first bridge will be described below as an example. In the initial state, the first bridge left integrated control valve group 6 is not electrified, and since the first solenoid valve 601, the second solenoid valve 607, the third solenoid valve 608 and the ninth solenoid valve 609 are all normally closed two-position two-way solenoid valves, and the fourth solenoid valve 604 is a normally open two-position two-way solenoid valve, the first solenoid valve 601, the second solenoid valve 607, the third solenoid valve 608 and the ninth solenoid valve 609 are all in the closed state when not electrified, and the fourth solenoid valve 604 is in the on state. When the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 is extended, the third electromagnetic valve 608 is electrified and turned on, the first bridge left electromagnetic valve 35 is closed, then the duplex pump 120 is started, hydraulic oil from the oil tank 109 sequentially enters the rodless cavity of the first bridge left hydro-pneumatic spring cylinder 22 through the total oil supply pipeline 119, a part of the first bridge left branch oil supply pipeline 602, the first pipeline 603 and the third electromagnetic valve 608 thereon, and a part of the first bridge left branch oil return pipeline 606, and then the piston rod is extended, and meanwhile, the hydraulic oil in the rod cavity of the first bridge left hydro-pneumatic spring cylinder 22 sequentially returns to the oil tank 109 through the part of the first bridge left branch oil supply pipeline 602, the second pipeline 605 and the fourth electromagnetic valve 604 thereon, and the part of the first bridge left branch oil return pipeline 606 and the total oil return pipeline 111; when the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 is retracted, the first electromagnetic valve 601 is electrified and conducted, the fourth electromagnetic valve 604 is electrified and closed, the second electromagnetic valve 607 is electrified and conducted and the first bridge left electromagnetic valve 35 is closed, then the duplex pump 120 is started, hydraulic oil from the oil tank 109 sequentially enters the rod cavity of the first bridge left hydro-pneumatic spring cylinder 22 through the total oil supply pipeline 119, the first bridge left sub oil supply pipeline 602 and the first electromagnetic valve 601 thereon, then the piston rod is retracted, and meanwhile, the hydraulic oil in the rodless cavity of the first bridge left hydro-pneumatic spring cylinder 22 sequentially returns to the oil tank 109 through the first bridge left sub oil return pipeline 606, the second electromagnetic valve 607 thereon and the total oil return pipeline 111.

Under the passive damping mode, the hydro-pneumatic suspension hydraulic system completes the passive self-adaptive elastic damping function through the energy accumulator and the hydro-pneumatic spring cylinder. The buffer function is realized through gas-liquid interaction between the energy accumulator and the hydro-pneumatic spring cylinder; the two hydro-pneumatic spring cylinders on each side are communicated through a balance pipeline, so that balance of oil liquid between rodless cavities of the two hydro-pneumatic spring cylinders is realized. The hydro-pneumatic suspension hydraulic system has the characteristics of self-adaptive elastic shock absorption and impact resistance under the elastic link, and provides stable and safe guarantee for the operation of special vehicles under various complex road conditions.

As described above, since the passive damping mode between the first bridge left and the second bridge left, the passive damping mode between the third bridge left and the fourth bridge left, the passive damping mode between the first bridge right and the second bridge right, and the passive damping mode between the third bridge right and the fourth bridge right are the same, only the passive damping mode between the first bridge left and the second bridge left will be described below.

During the running process of the vehicle, the passive damping mode is started, at this time, the duplex pump 120 is not operated, the first, second and third electromagnetic valves at the left of the first bridge are all in the non-electrified closed state, the fourth electromagnetic valve 604 is in the non-electrified conducting state, the ninth electromagnetic valve 609 is in the electrified conducting state, the left electromagnetic valve 35 of the first bridge is in the conducting state, and at the same time, the fifth, sixth and seventh electromagnetic valves at the left of the second bridge are all in the non-electrified closed state, and the eighth electromagnetic valve 704 is in the non-electrified conducting state. When the vehicle wheel set at the left of the first bridge runs to the raised pavement, the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 moves upwards to retract, so that one part of hydraulic oil in the rodless cavity of the first bridge left hydro-pneumatic spring cylinder 22 enters the first bridge left accumulator 14 through the first bridge left energy storage pipeline 34, and the other part of hydraulic oil enters the rodless cavity of the second bridge left hydro-pneumatic spring cylinder 23 through the first balance pipeline 30 and one part of the second bridge left oil return pipeline 706 in turn, so that the piston rod of the second bridge left hydro-pneumatic spring cylinder 23 moves downwards to extend to enable the vehicle wheel set at the left of the second bridge to be supported on the pavement (in the process, the hydraulic oil in the rod cavity of the second bridge left hydro-pneumatic spring cylinder 23 sequentially returns to the oil tank 109 through one part of the second bridge left oil supply pipeline 702, the fourth pipeline 704 and an eighth electromagnetic valve thereon, and a part of the second bridge left oil return pipeline 706 and the total oil return pipeline 111), and the vehicle wheel set at the left of the second bridge can adapt to the condition that the vehicle wheel set at the left of the first bridge runs to the raised pavement; after the vehicle wheelset on the left of the first axle has traveled over the raised road surface, the hydraulic oil in the first axle left accumulator 14 (i.e., the hydraulic oil that was previously admitted into the first axle left accumulator 14 by the rodless cavity of the first axle left hydro-pneumatic cylinder 22) returns to the rodless cavity of the first axle left hydro-pneumatic cylinder 22 via the first axle left accumulator line 34, while the hydraulic oil in the rodless cavity of the second axle left hydro-pneumatic cylinder 23 (i.e., the hydraulic oil that was previously admitted into the rodless cavity of the second axle left hydro-pneumatic cylinder 23 by the rodless cavity of the first axle left hydro-pneumatic cylinder 22) returns to the rodless cavity of the first axle left hydro-pneumatic cylinder 22 via the first balance line 30, whereupon the piston rod of the first axle left hydro-pneumatic cylinder 22 moves downward to extend, and the piston rod of the second axle left hydro-pneumatic cylinder 23 moves upward to retract, i.e., the vehicle wheelsets on the left of the first axle and second axle are both restored to the initial travel condition. When the vehicle wheel set at the left of the second axle runs to the raised road surface, the working principle of the vehicle wheel set at the left of the second axle is the same as that of the vehicle wheel set at the left of the first axle, and the description is omitted here. In summary, when the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 is moved upward to be retracted, the piston rod of the second bridge left hydro-pneumatic spring cylinder 23 is moved downward to be extended, and when the piston rod of the second bridge left hydro-pneumatic spring cylinder 23 is moved upward to be retracted, the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 is moved downward to be extended, so that the vehicle can adapt to a rough road surface.

Because the first bridge left energy storage pipeline 34 is connected with the first bridge left one-way throttle valve 36, when the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 moves upwards to retract, hydraulic oil in a rodless cavity can slowly enter the first bridge left energy storage 14 through the first bridge left energy storage pipeline 34; when the piston rod of the first bridge left hydro-pneumatic spring cylinder 22 is required to move downwards to extend, hydraulic oil in the first bridge left energy accumulator 14 can be quickly returned to the rodless cavity of the first bridge left hydro-pneumatic spring cylinder 22 through the first bridge left energy storage pipeline 34, so that the piston rod moves downwards to extend quickly.

The dual pump 120 of the present invention includes a large flow pump 110 and a small flow pump 102, the large flow pump 110 is activated when the lifting of the whole vehicle needs to be controlled, and the small flow pump 102 is activated when the lifting of only one or a plurality of bridges needs to be regulated. Before the servo motor 101 is started, the three-position four-way electromagnetic directional valve 108 is in the middle position, namely, the first inlet 117 and the second inlet 118 are communicated with the second outlet 115, then the servo motor 101 is started, no matter the servo motor 101 drives the large-flow pump 110 or the small-flow pump 102, the large-flow pump 110 or the small-flow pump 102 pumps hydraulic oil in the oil tank 109, the hydraulic oil enters the three-position four-way electromagnetic directional valve 108 through the first inlet 117 or the second inlet 118, then the hydraulic oil exits from the second outlet 115, and then returns to the oil tank 109 through the second pump station pipeline 113 and a part of the total oil return pipeline 111 in sequence, namely, the duplex pump 120 does not supply oil to the hydraulic system in the initial stage of starting the duplex pump 120. When the large-flow pump 110 is needed to supply oil to the hydraulic system, the three-position four-way electromagnetic reversing valve 108 is adjusted to the left position, and the first inlet 117 is communicated with the first outlet 116 at the moment, so that the hydraulic oil from the oil tank 109 directly supplies oil to the hydraulic system through the total oil supply pipeline 119 and the large-flow pump 110 thereon; when the small-flow pump 102 is required to supply oil to the hydraulic system, the three-position four-way electromagnetic directional valve 108 is adjusted to the right position, and the second inlet 118 is communicated with the first outlet 116 at this time, so that hydraulic oil from the oil tank 109 sequentially passes through a part of the total oil supply pipeline 119, the small-flow pump 102, the first pump station pipeline 112 and the three-position four-way electromagnetic directional valve 108 and then enters the total oil supply pipeline 119 again so as to supply oil to the hydraulic system.

When the load of the vehicle is excessive, the overflow valve 107 is opened, and the hydraulic oil in the total oil supply pipeline 119 is returned to the oil tank 109 through the third pump station pipeline 114 and a part of the total oil return pipeline 111 in sequence, so that the overflow valve 107 can play a role of overload protection.

As for the oil supply filter 103, the oil return filter 106, the liquid level gauge 105 and the air filter 104, they are all of the prior art, and the structure and the working principle thereof will not be described herein.

The integrated hydraulic pump station 1 configured by the invention can realize rapid full-stroke expansion and contraction of 8 hydro-pneumatic spring cylinders in an active driving mode, the total expansion and contraction time is not more than 10s, and the time for adjusting the posture of a special vehicle is shortened to a great extent.

When the special vehicle is parked to launch the rocket, each hydro-pneumatic spring cylinder is in a pressure maintaining state, and the pressure maintaining mode of each hydro-pneumatic spring cylinder is the same, only the first bridge left hydro-pneumatic spring cylinder 22 is taken as an example for illustration. All solenoid valves in the first bridge left integrated control valve bank 6 are in a closed state, namely hydraulic oil communication between the first bridge left hydro-pneumatic spring cylinder 22 and the integrated hydraulic pump station 1 is cut off, and meanwhile, the first bridge left solenoid valve 35 is also in a closed state, namely hydraulic oil communication between the first bridge left hydro-pneumatic spring cylinder 22 and the first bridge left accumulator 14 is cut off, so that piston rods of the first bridge left hydro-pneumatic spring cylinder 22 cannot stretch out and draw back, namely in a pressure maintaining state, and the hydraulic oil storage device can adapt to rocket launching.

In summary, the invention provides the hydro-pneumatic suspension hydraulic system with high integration degree, double-acting mode, good synchronism and high driving efficiency, and compared with the prior art, the hydro-pneumatic suspension hydraulic system has the advantages and characteristics of high integration degree, double-driving mode, good motion synchronism and high driving efficiency.

The beneficial results of the invention are:

(1) The hydro-pneumatic suspension hydraulic system designed by the invention has the functions of active driving, single-cylinder active control, multiple vehicle posture adjusting and passive damping, and is fully suitable for various complex working conditions of special vehicles;

(2) The integrated hydraulic pump station 1 and the integrated control valve group are subjected to modularized design through integrated design, so that the pipeline connection of the whole system is simple and clear, and the integration level is high;

(3) In the designed hydro-pneumatic suspension hydraulic system, in an active driving mode, the lifting active control function is completed through the integrated hydraulic pump station 1, the integrated control valve group and the hydro-pneumatic spring cylinder, so that the lifting and adjusting functions of the whole special vehicle are realized;

(4) In the passive damping mode, the hydro-pneumatic suspension hydraulic system provided by the invention completes a passive self-adaptive elastic damping function through the energy accumulator and the hydro-pneumatic spring cylinder, and provides a stable running posture for running of a special vehicle;

(5) The hydro-pneumatic suspension hydraulic system designed by the invention has high response speed in an active driving mode, and can realize full-stroke lifting motion within 10 seconds;

(6) The oil-gas suspension hydraulic system designed by the invention has the characteristics of convenient maintenance, the whole system is symmetrically arranged, the pipeline connection is clear, and each maintenance part can be rapidly and accurately positioned according to a schematic diagram and a pipeline connection diagram.

It should be noted that, the positional or positional relationship indicated by the terms such as "center", "upper", "lower", "front", "rear", "left", "right", "middle", etc. are based on the positional or positional relationship shown in the drawings, are merely for convenience of describing the present invention and simplifying the description, and do not indicate or imply that the apparatus or element referred to must have a specific orientation, be configured and operated in a specific orientation, and thus should not be construed as limiting the present invention.

In the description of the present invention, it should be noted that, unless explicitly specified and limited otherwise, the terms "connected," "connected," and "connected" are to be construed broadly, and may be either fixedly connected, detachably connected, or integrally connected, for example; can be mechanically or electrically connected; can be directly connected or indirectly connected through an intermediate medium. The specific meaning of the above terms in the present invention will be understood in specific cases by those of ordinary skill in the art.

The above examples are only illustrative of the preferred embodiments of the present invention and are not intended to limit the scope of the present invention, and various modifications and improvements made by those skilled in the art to the technical solution of the present invention should fall within the scope of protection defined by the claims of the present invention without departing from the spirit of the present invention.

Claims

1. A double-acting integrated type hydro-pneumatic suspension hydraulic system for special type vehicle, its characterized in that: comprises an integrated hydraulic pump station, a first bridge left oil-gas spring cylinder, a first bridge right oil-gas spring cylinder, a second bridge left oil-gas spring cylinder and a second bridge right oil-gas spring cylinder, wherein the integrated hydraulic pump station is connected with a total oil supply pipeline and a total oil return pipeline, the total oil supply pipeline is respectively connected with rod cavities of the first bridge left oil-gas spring cylinder, the first bridge right oil-gas spring cylinder, the second bridge left oil-gas spring cylinder and the second bridge right oil-gas spring cylinder through a first bridge left oil supply pipeline, a first bridge right oil supply pipeline, a second bridge left oil-gas spring cylinder and a second bridge right oil-gas spring cylinder respectively, the total oil return pipeline is respectively connected with the rod-free cavities of the first bridge left oil-gas spring cylinder, the first bridge right oil-gas spring cylinder, the second bridge left oil-gas spring cylinder and the second bridge right oil-gas spring cylinder through a first bridge left oil-gas spring pipeline,

2. The dual acting integrated hydro-pneumatic suspension hydraulic system for specialty vehicles of claim 1, wherein: the hydraulic oil system further comprises a third bridge left hydro-pneumatic spring cylinder and a third bridge right hydro-pneumatic spring cylinder, wherein the total oil supply pipeline is connected with rod cavities of the third bridge left hydro-pneumatic spring cylinder and the third bridge right hydro-pneumatic spring cylinder through a third bridge left oil distribution pipeline and a third bridge right oil distribution pipeline respectively, the total oil return pipeline is connected with rod-free cavities of the third bridge left hydro-pneumatic spring cylinder and the third bridge right hydro-pneumatic spring cylinder through a third bridge left oil return pipeline and a third bridge right oil return pipeline respectively,

3. The dual acting integrated hydro-pneumatic suspension hydraulic system for a specialty vehicle of claim 2, wherein: the hydraulic oil system further comprises a fourth bridge left hydro-pneumatic spring cylinder and a fourth bridge right hydro-pneumatic spring cylinder, wherein the total oil supply pipeline is connected with rod cavities of the fourth bridge left hydro-pneumatic spring cylinder and the fourth bridge right hydro-pneumatic spring cylinder through a fourth bridge left oil distribution pipeline and a fourth bridge right oil distribution pipeline respectively, the total oil return pipeline is connected with rodless cavities of the fourth bridge left hydro-pneumatic spring cylinder and the fourth bridge right hydro-pneumatic spring cylinder through a fourth bridge left oil return pipeline and a fourth bridge right oil return pipeline respectively,

4. A double acting integrated hydro-pneumatic suspension hydraulic system for specialty vehicles as set forth in claim 3 wherein: the hydraulic oil return device is characterized in that a third balance pipeline is connected between the third bridge left branch oil return pipeline and the fourth bridge left branch oil return pipeline, a connection point between the third balance pipeline and the third bridge left branch oil return pipeline is located at one side of the twenty-eighth electromagnetic valve, which is close to the third bridge left oil gas spring cylinder, a connection point between the third balance pipeline and the fourth bridge left branch oil return pipeline is located at one side of the twenty-eighth electromagnetic valve, which is close to the fourth bridge left oil gas spring cylinder, and a thirty-fifth electromagnetic valve is connected to the third balance pipeline.

5. The dual acting integrated hydro-pneumatic suspension hydraulic system for specialty vehicles of claim 4, wherein: the hydraulic oil return device is characterized in that a fourth balance pipeline is connected between the third bridge right oil return pipeline and the fourth bridge right oil return pipeline, a connecting point between the fourth balance pipeline and the third bridge right oil return pipeline is located on one side, close to the third bridge right oil-gas spring cylinder, of the twenty-fourth electromagnetic valve, a connecting point between the fourth balance pipeline and the fourth bridge right oil return pipeline is located on one side, close to the fourth bridge right oil-gas spring cylinder, of the thirty-second electromagnetic valve, and a thirty-sixth electromagnetic valve is connected to the fourth balance pipeline.

6. The dual acting integrated hydro-pneumatic suspension hydraulic system for specialty vehicles of claim 5, wherein: the integrated hydraulic pump station comprises an oil tank, a duplex pump and a three-position four-way electromagnetic reversing valve, wherein the oil supply port of the oil tank is connected with a total oil supply pipeline, the oil return port of the oil tank is connected with a total oil return pipeline, the duplex pump and the three-position four-way electromagnetic reversing valve are sequentially connected to the total oil supply pipeline along the oil supply direction, the duplex pump is driven by a servo motor, two ends of the total oil supply pipeline between the duplex pump and the three-position four-way electromagnetic reversing valve are respectively connected to a large-flow pump of the duplex pump and a first inlet of the three-position four-way electromagnetic reversing valve, the total oil supply pipeline, far away from one side of the duplex pump, of the three-position four-way electromagnetic reversing valve is connected to a first outlet of the three-position four-way electromagnetic reversing valve, a small-flow pump of the duplex pump is connected to a second inlet of the three-position four-way electromagnetic reversing valve through a first pump station pipeline, a second outlet of the three-position four-way electromagnetic reversing valve is connected to the total oil supply pipeline through a second pump station, a third pump station is connected between the total oil supply pipeline and the second pump station, and the third pump station is connected with an overflow valve.

7. The dual acting integrated hydro-pneumatic suspension hydraulic system for a specialty vehicle of claim 6, wherein: the oil tank is characterized in that an oil supply filter is connected to a total oil supply pipeline between the oil tank and the duplex pump, an oil return filter is connected to a total oil return pipeline, and a second pump station pipeline is connected to a total oil return pipeline of one side, far away from the oil tank, of the oil return filter.

8. The dual acting integrated hydro-pneumatic suspension hydraulic system for a specialty vehicle of claim 7, wherein: the oil tank is also provided with an air filter and a liquid level meter.

9. The dual acting integrated hydro-pneumatic suspension hydraulic system for a specialty vehicle of claim 8, wherein: the novel chassis measuring device comprises a chassis, and is characterized by further comprising a first angle sensor, a second angle sensor, a third angle sensor and a fourth angle sensor, wherein the first angle sensor is arranged near a left hydro-pneumatic spring cylinder of a first bridge, the second angle sensor is arranged near a right hydro-pneumatic spring cylinder of the first bridge, the third angle sensor is arranged near a left hydro-pneumatic spring cylinder of a fourth bridge, the fourth angle sensor is arranged near a right hydro-pneumatic spring cylinder of the fourth bridge, and the first angle sensor, the second angle sensor, the third angle sensor and the fourth angle sensor are all used for measuring the height of the chassis of the special vehicle.

10. The dual acting integrated hydro-pneumatic suspension hydraulic system for specialty vehicles of claim 9, wherein: the fourth, eighth, thirteenth, seventeenth, twenty-second, twenty-seventh, thirty-eighth, twenty-ninth, thirty-first, thirty-second, thirty-third, thirty-fifth and thirty-sixth solenoid valves are all normally open two-position, and the first, second, tenth, eleventh, twelfth, fourteenth, fifteenth, sixteenth, eighteenth, nineteenth, twenty-first, twenty-third, twenty-fourth, twenty-fifth, twenty-seventh, thirty-fifth, thirty-eighth, thirty-ninth, thirty-first, thirty-sixth solenoid valves are all normally open two-position, solenoid valves.