CN114542554A

CN114542554A - Dynamic and static loading comprehensive electro-hydraulic system of damping damper and control method thereof

Info

Publication number: CN114542554A
Application number: CN202210089294.4A
Authority: CN
Inventors: 强红宾; 王瑞; 徐倩; 刘凯磊; 康绍鹏; 叶霞; 单文桃; 孙文杰
Original assignee: Jiangsu University of Technology
Current assignee: Jiangsu University of Technology
Priority date: 2022-01-25
Filing date: 2022-01-25
Publication date: 2022-05-27

Abstract

The invention provides a dynamic and static loading comprehensive electro-hydraulic system of a damping damper and a control method thereof, and solves the problems that the conventional damping test bed is divided into a static loading test bed and a dynamic loading test bed, and the electro-hydraulic systems and the control methods of the static loading test bed and the dynamic loading test bed are independently designed, so that resources are wasted and the energy consumption is high, so that the static loading and the dynamic loading of the electro-hydraulic system of the damping damper test bed share one hydraulic system, the space is saved, and the materials are saved.

Description

Dynamic and static loading comprehensive electro-hydraulic system of damping damper and control method thereof

Technical Field

The invention relates to the technical field of shock absorber damper control, in particular to an electro-hydraulic system capable of realizing dynamic and static loading of a shock absorber damper and a control method.

Background

The vibration-damping damper is applied to the industries of aviation, aerospace, war industry, automobiles and the like at the earliest, and the technology is gradually transferred to structural engineering of bridges, buildings, railways and the like from the seventies of the twentieth century, so that the development is very rapid. The shock absorption and energy dissipation damper is used for absorbing shock energy generated by earthquake, wind and the like on a building, plays an important role in shock absorption of the building, can further improve the capability of the building for resisting natural disasters such as the earthquake and the like along with the development of the shock absorption and energy dissipation damper, and protects the life safety of human beings. The shock absorption damper test bed can test the comprehensive performance of the shock absorption damper and lay a foundation for further improving the performance of the shock absorption damper.

At present, damping damper test beds are mainly divided into static loading test beds and dynamic loading test beds, but the electro-hydraulic systems and the control methods of the static loading test beds and the dynamic loading test beds are independently designed, so that resources are wasted, and energy consumption is high.

Disclosure of Invention

The invention discloses a dynamic and static loading comprehensive electro-hydraulic system of a damping damper and a control method thereof, which solve the problems of resource waste and high energy consumption caused by the fact that the conventional damping test bed is divided into a static loading test bed and a dynamic loading test bed, and the electro-hydraulic systems and the control methods of the static loading test bed and the dynamic loading test bed are independently designed, so that the static loading and the dynamic loading of the electro-hydraulic system of the damping damper test bed share one hydraulic system, the space is saved, and the material is saved.

In order to achieve the purpose, the technical scheme of the invention is realized as follows:

the invention discloses a dynamic and static loading comprehensive electro-hydraulic system of a damping damper, which comprises an oil tank, an oil source valve group, a first oil absorption filter, a first motor, an energy accumulator, a pressure regulating valve group, a static hydraulic cylinder control valve group, a dynamic hydraulic cylinder control valve group, a control oil valve group, a first hydraulic pump, a second motor, a first displacement sensor, a first force sensor, a second displacement sensor, a second force sensor, a cooler, a first oil filter, an overflow pressure reducing valve, a second hydraulic pump, a second oil absorption filter, a third motor, a first stop valve, a second stop valve and a first one-way valve, wherein the oil tank is used for storing oil required by the system; the oil source valve group comprises an electric proportional variable pump, a regulating hydraulic cylinder, a three-dimensional four-way electromagnetic proportional valve and a hydraulic cylinder position feedback sensor, wherein the electric proportional variable pump sucks oil from the oil tank through rotation and supplies the oil to the regulating valve group; the hydraulic cylinder is adjusted to control the flow of the electric proportional pump; the three-position four-way electromagnetic proportional valve is used for controlling and adjusting the position of a piston rod of the hydraulic cylinder; the hydraulic cylinder position feedback sensor is used for detecting and adjusting the position of a piston rod of the hydraulic cylinder; the first oil suction filter is used for filtering oil sucked by the oil source valve group from the oil tank; the first motor is connected with the oil source valve group through a coupler and drives the electric proportional variable pump to rotate; the energy accumulator is used for providing instantaneous large flow during dynamic loading; the pressure regulating valve group is used for regulating the pressure of the system; the static load hydraulic cylinder is used for applying a static load; the static load hydraulic cylinder control valve group is used for supplying oil to the static load hydraulic cylinder so as to control the movement direction of a piston rod of the static load hydraulic cylinder; the dynamic load hydraulic cylinder is used for applying dynamic load; the dynamic load hydraulic cylinder control valve group is used for supplying oil to the dynamic load hydraulic cylinder so as to control the movement direction of a piston rod of the dynamic load hydraulic cylinder; the control oil valve group is used for supplying oil to the oil source valve group; the first hydraulic pump sucks oil from the oil tank through rotation and supplies oil to the control oil valve group; the second motor is connected with the first hydraulic pump through a coupler and drives the first hydraulic pump to rotate; the first displacement sensor is used for measuring the movement speed of the piston rod of the static hydraulic cylinder; the first force sensor is used for measuring the force borne by the piston rod of the static hydraulic cylinder during movement; the second displacement sensor is used for measuring the movement speed of the piston rod of the dynamic load hydraulic cylinder; the second force sensor is used for measuring the force borne by the piston rod of the dynamic load hydraulic cylinder during movement; the cooler is used for cooling oil in the oil tank; the first pressure oil filter is used for supplying oil to the cooler; the overflow pressure reducing valve is used for preventing the system from overloading; the second hydraulic pump sucks oil from the oil tank through rotation and supplies oil to the first oil filter and the overflow pressure reducing valve; the second oil suction filter is used for filtering oil sucked by the second hydraulic pump from the oil tank; the third motor is connected with the second hydraulic pump through a coupler and drives the second hydraulic pump to rotate; the first stop valve is used for controlling the connection and the closing of the oil way; the second stop valve is used for controlling the opening and closing of the oil tank; the first one-way valve is used for differential pressure protection, and when the cooler is blocked, the first one-way valve is used for circulation.

Furthermore, the dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper further comprises a heater, an air filter, a liquid level relay, a temperature transmitter, a liquid level meter and a first pressure sensor, wherein the heater is fixedly installed inside the oil tank and used for ensuring that oil in the oil tank is not condensed; the air filter is fixedly arranged at the upper part of the oil tank and is used for preventing particle pollutants from entering a system through the oil tank; the liquid level relay is used for controlling the height of oil in the oil tank; the temperature transmitter is used for measuring the temperature of the oil in the oil tank; the liquid level meter is fixedly arranged on the side surface of the oil tank and used for measuring the height of oil in the oil tank; the first pressure sensor is used for measuring the pressure value of the oil outlet of the second hydraulic pump.

Furthermore, an oil inlet P of the first oil suction filter, an oil return port T of the oil source valve group, an oil suction port S of the first hydraulic pump, an oil return port T of the control oil valve group, an oil return port T of the pressure regulating valve group, an oil discharge port L of the pressure regulating valve group, an oil return port T of the static load hydraulic cylinder control valve group, an oil discharge port L of the static load hydraulic cylinder control valve group, an oil inlet P of the second oil suction filter, an oil discharge port L of the overflow reducing valve, an oil outlet A of the cooler and an oil outlet A of the first check valve are connected with the oil tank through hydraulic pipelines; an output shaft of the first motor is connected with an input shaft of the oil source valve bank through a coupler, and an oil outlet A of the first oil suction filter is connected with an oil suction port S of the oil source valve bank through a hydraulic pipeline; the output shaft of the second motor is connected with the input shaft of the first hydraulic pump through a coupling; an oil outlet A of the first hydraulic pump is connected with an oil inlet P of the control oil valve group through a hydraulic pipeline; an oil inlet P of the oil source valve group is connected with an oil outlet A of the control oil valve group through a hydraulic pipeline, the oil outlet A of the oil source valve group is connected with an oil inlet P of the pressure regulating valve group through a hydraulic pipeline, an oil outlet B of the pressure regulating valve group is connected with an oil inlet P of the energy accumulator through a hydraulic pipeline, the oil outlet A of the pressure regulating valve group is connected with an oil inlet P of the static hydraulic cylinder control valve group and an oil inlet P of the dynamic hydraulic cylinder control valve group through hydraulic pipelines, the oil outlet A of the static hydraulic cylinder control valve group is connected with an oil inlet of a left rod cavity of the static hydraulic cylinder through a hydraulic pipeline, and the oil outlet B of the static hydraulic cylinder control valve group is connected with an oil inlet P of a right rod cavity of the static hydraulic cylinder through a hydraulic pipeline; an oil outlet A of the dynamic hydraulic cylinder control valve group is connected with an oil inlet of a left rod cavity of the dynamic hydraulic cylinder through a hydraulic pipeline, and an oil outlet B of the dynamic hydraulic cylinder control valve group is connected with an oil inlet of a right rod cavity of the dynamic hydraulic cylinder through a hydraulic pipeline; an oil return port T of the static load hydraulic cylinder control valve group, an oil return port T of the dynamic load hydraulic cylinder control valve group and an oil return port T of the pressure regulating valve group are connected through a hydraulic pipeline; and an oil drainage port L of the static load hydraulic cylinder control valve group, an oil drainage port L of the dynamic load hydraulic cylinder control valve group and an oil drainage port L of the pressure regulating valve group are connected through a hydraulic pipeline.

Furthermore, an oil outlet A of the second oil suction filter is connected with an oil inlet P of the first cut-off valve through a hydraulic pipeline, an oil outlet A of the first cut-off valve is connected with an oil suction port S of the second hydraulic pump through a hydraulic pipeline, an output shaft of the third motor is connected with an input shaft of the second hydraulic pump through a coupler, an oil outlet A of the second hydraulic pump is connected with an oil inlet P of the first oil pressing filter, an oil inlet P of the overflow reducing valve and an oil inlet P of the first pressure sensor through hydraulic pipelines, an oil outlet A of the first oil pressing filter is connected with an oil inlet P of the first one-way valve and an oil inlet P of the cooler through hydraulic pipelines, and an oil outlet of the first one-way valve is connected with an oil outlet A of the cooler through a hydraulic pipeline.

Furthermore, an oil inlet P of the electric proportional variable pump is connected with an oil suction port S of the oil source valve group through an internal flow channel of the oil source valve group, an oil outlet L of the electric proportional variable pump is connected with an oil outlet A of the oil source valve group through an internal flow channel of the oil source valve group, an oil drain port L of the electric proportional variable pump is connected with an oil return port T of the oil source valve group through an internal flow channel of the oil source valve group, an oil inlet of the three-position four-way electromagnetic proportional valve is connected with an oil inlet P of the oil source valve group through an internal flow channel of the oil source valve group, an oil return port T of the three-position four-way electromagnetic proportional valve is connected with an oil return port T of the oil source valve group through an internal flow channel of the oil source valve group, an outlet A of the three-position four-way electromagnetic proportional valve is connected with an oil inlet P1 of the adjusting hydraulic cylinder through an internal flow channel of the oil source valve group, and an oil outlet B of the three-position four-way electromagnetic proportional valve is connected with an oil inlet P2 of the adjusting hydraulic cylinder through an internal flow channel of the oil source valve group.

Furthermore, the control valve group comprises a second pressure oil filter, a first two-position two-way electromagnetic valve, a second pressure sensor and an overflow valve, wherein the second pressure oil filter is used for filtering oil sucked by the control valve group; the first two-position two-way electromagnetic valve is used for controlling the flow direction of oil; the second pressure sensor is used for measuring the pressure of the oil inlet of the control valve group; the overflow valve is used for ensuring that the pressure of the control valve group does not exceed a specified range; the oil inlet P of the second pressure oil filter is connected with the oil inlet P of the control oil valve group through an internal flow channel of the control oil valve group, the oil outlet A of the second pressure oil filter, the oil inlet P of the first two-position two-way electromagnetic valve, the oil inlet P of the second pressure sensor, the oil inlet P of the overflow valve is connected through the internal flow channel of the control oil valve group, the oil outlet A of the first two-position two-way electromagnetic valve is connected with the oil outlet A of the control oil valve group through the internal flow channel of the control oil valve group, the oil outlet B of the first two-position two-way electromagnetic valve, the oil outlet A of the overflow valve and the oil return port T of the control oil valve group are connected through the internal flow channel of the control oil valve group.

Furthermore, the pressure regulating valve group comprises a third pressure sensor, a second one-way valve, a third pressure oil filter, an unloading pressure reducing valve, a second two-position two-way electromagnetic valve and a proportional overflow valve, and the third pressure sensor is used for measuring the pressure of an oil inlet of the pressure regulating valve group; the second check valve is used for preventing the oil from flowing back to the oil source valve group; the third pressure oil filter is used for filtering oil sucked by the pressure regulating valve group; the unloading pressure reducing valve is used for automatically controlling unloading or loading of the pump; the second two-position two-way electromagnetic valve is used for controlling the working state of the unloading pressure reducing valve; the proportional overflow valve is used for controlling the system pressure and preventing the system from overloading; an oil inlet P of a third pressure sensor, an oil inlet P of a second check valve and an oil inlet P of a pressure regulating valve group are connected through an internal flow passage of the pressure regulating valve group, an oil outlet A of the second check valve is connected with an oil inlet P of a third pressure oil filter through an internal flow passage of the pressure regulating valve group, an oil outlet A of the third pressure oil filter, an oil outlet B of the pressure regulating valve group, an oil outlet A of the pressure regulating valve group, an oil inlet P of an unloading pressure reducing valve and an oil inlet P of a proportional overflow valve are connected through an internal flow passage of the pressure regulating valve group, an oil outlet A of the unloading pressure reducing valve is connected with an oil inlet P of a second two-position two-way electromagnetic valve through an internal flow passage of the pressure regulating valve group, an oil return port T of the unloading pressure reducing valve, an oil discharge port L of the unloading pressure reducing valve, an oil return port T of the second two-position two-way electromagnetic valve, an oil return port T of the proportional overflow valve and an oil return port T of the pressure regulating valve group are connected through an internal flow passage of the pressure regulating valve group, and an oil drainage port L of the proportional overflow valve is connected with an oil drainage port L of the pressure regulating valve group through an internal flow passage of the pressure regulating valve group.

Furthermore, the static load hydraulic cylinder control valve group comprises a fourth pressure sensor, a first three-position four-way servo valve, a fifth pressure sensor, a first cartridge valve, a first control cover plate reversing valve, a sixth pressure sensor, a second control cover plate reversing valve, a second cartridge valve, an eighth pressure sensor and a ninth pressure sensor, wherein the fourth pressure sensor is used for measuring the pressure of an oil inlet of the static load hydraulic cylinder control valve group; the first three-position four-way servo valve is used for controlling the motion direction of a piston rod of the static hydraulic cylinder; the fifth pressure sensor is used for measuring the pressure of the oil inlet of the first cartridge valve and the pressure of the oil inlet of the reversing valve of the first control cover plate; the first plug-in valve is used for controlling the flow of oil flowing into the left rod cavity of the static hydraulic cylinder; the first control cover plate reversing valve is used for controlling the working state of the first cartridge valve; the sixth pressure sensor is used for measuring the pressure of the left rod cavity of the static hydraulic cylinder; the seventh pressure sensor is used for measuring the pressure of the right rod cavity of the static hydraulic cylinder; the second control cover plate reversing valve is used for controlling the working state of the second cartridge valve; the second cartridge valve is used for controlling the flow of oil flowing into the right rod cavity of the static hydraulic cylinder; the eighth pressure sensor is used for measuring the pressure of the oil inlet of the second cartridge valve and the oil inlet of the reversing valve of the second control cover plate; the ninth pressure sensor is used for measuring the pressure of an oil return port of the control valve group of the static load hydraulic cylinder; an oil inlet P of the first three-position four-way servo valve, an oil inlet M of the fourth pressure sensor and an oil inlet P of the static load hydraulic cylinder control valve group are connected through an internal flow passage of the static load hydraulic cylinder control valve group, an oil return port T of the first three-position four-way servo valve, an oil inlet M of the ninth pressure sensor and an oil return port T of the static load hydraulic cylinder control valve group are connected through an internal flow passage of the static load hydraulic cylinder control valve group, an oil outlet A of the first three-position four-way servo valve, an oil inlet M of the fifth pressure sensor, an oil inlet A of the first cartridge valve and an oil inlet X of the first control cover plate reversing valve are connected through an internal flow passage of the static load hydraulic cylinder control valve group, an oil outlet B of the first three-position four-way servo valve, an oil inlet M of the eighth pressure sensor, an oil inlet A of the second cartridge valve and an oil inlet X of the second control cover plate reversing valve are connected through an internal flow passage of the static load hydraulic cylinder control valve group, the oil return port T of the first control cover plate reversing valve, the oil outlet B of the first cartridge valve, the oil inlet P of the sixth pressure sensor and the oil outlet A of the static hydraulic cylinder control valve group are connected through an internal flow channel of the static hydraulic cylinder control valve group, and the oil return port T of the second control cover plate reversing valve, the oil outlet B of the second cartridge valve, the oil inlet M of the seventh pressure sensor and the oil outlet B of the static hydraulic cylinder control valve group are connected through an internal flow channel of the static hydraulic cylinder control valve group.

Further, the dynamic hydraulic cylinder control valve group comprises a second three-position four-way servo valve, a tenth pressure sensor, an eleventh pressure sensor, a twelfth pressure sensor and a thirteenth pressure sensor. The second three-position four-way servo valve is used for controlling the movement direction of the piston rod of the dynamic load hydraulic cylinder; the tenth pressure sensor is used for measuring the pressure of an oil inlet of the control valve group of the dynamic load hydraulic cylinder; the eleventh pressure sensor is used for measuring the pressure of the left rod cavity of the dynamic load hydraulic cylinder; the twelfth pressure sensor is used for measuring the pressure of the right rod cavity of the dynamic load hydraulic cylinder; the thirteenth pressure sensor is used for measuring the pressure of an oil outlet of the control valve group of the dynamic hydraulic cylinder; an oil inlet P of a second three-position four-way servo valve, an oil inlet M of a tenth pressure sensor and an oil inlet P of a dynamic load hydraulic cylinder control valve group are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group, an oil outlet A of the second three-position four-way servo valve, an oil inlet M of an eleventh pressure sensor and an oil outlet A of the dynamic load hydraulic cylinder control valve group are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group, an oil outlet B of the second three-position four-way servo valve, an oil inlet M of a twelfth pressure sensor and an oil outlet B of the dynamic load hydraulic cylinder control valve group are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group, an oil return port T of the second three-position four-way servo valve, an oil inlet M of a thirteenth pressure sensor and an oil return port T of the dynamic load hydraulic cylinder control valve group are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group, and an oil discharge port L of the second three-position four-way servo valve is connected with an oil discharge port L of the dynamic load hydraulic cylinder control valve group through an internal flow channel of the dynamic load hydraulic cylinder control valve group The part flow passages are connected.

The invention discloses a control method of a dynamic and static loading comprehensive electro-hydraulic system of a shock absorber damper, which comprises the following steps of:

step 1: initializing the system, if the system is normal, continuing to execute downwards, and if the system is abnormal, not executing downwards;

step 2: judging static loading/dynamic loading: switching by a static loading/dynamic loading button on the operation panel, and if the static loading is performed, entering the step 3.1; if the dynamic loading is carried out, entering 3.2;

step 3.1: manual/automatic mode determination: judging whether the operation mode is an automatic mode or not through a manual/automatic switching button on the operation panel, and if the operation mode is the manual mode, entering the step 4.1.1; if the mode is the automatic mode, entering 4.2.1;

step 4.1.1: manually adjusting the flow of the system, adjusting a displacement knob of the electric proportional variable pump on an operation panel, wherein an error value occurs between the input quantity and the measured value of a hydraulic cylinder position feedback sensor, and the error value triggers a three-position four-way electromagnetic proportional valve to work, so that the hydraulic cylinder is adjusted to work, and the displacement of the electric proportional variable pump is the same as the input value;

step 4.1.2: manually adjusting the pressure of the system, adjusting a pressure knob of a proportional overflow valve on an operation panel, and setting the overflow pressure of the system;

step 4.1.3: manually controlling the extension of the static load cylinder: adjusting an input value of a first three-position four-way servo valve on an operation panel, when the operation panel is adjusted in a forward direction, the left position of the first three-position four-way servo valve works, pressure oil enters a second cartridge valve and then enters a left rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move rightwards, and hydraulic oil in a right rod cavity of the static hydraulic cylinder enters the left position of the first three-position four-way servo valve through the first cartridge valve and flows back to an oil tank; when the hydraulic oil is reversely adjusted, the right position of the first three-position four-way servo valve works, the pressure oil enters the first cartridge valve and then enters the right rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move leftwards, and the hydraulic oil in the left rod cavity of the static hydraulic cylinder enters the right bit flow oil return tank of the first three-position four-way servo valve through the second cartridge valve; when the neutral position is adjusted back, the neutral position of the first three-position four-way servo valve works, the reversing valve of the first control cover plate is electrified, the left position works, the first cartridge valve is closed, the reversing valve of the second control cover plate is electrified, the left position works, the second cartridge valve is closed, the static load hydraulic cylinder is static, and the pressure maintaining state is entered;

step 4.1.4: manually opening the energy accumulator for pressure maintaining: an energy accumulator stop valve button on an operation panel is opened, an energy accumulator stop valve is opened, hydraulic oil in an energy accumulator enters a hydraulic system, leakage of the system is supplemented, and pressure maintaining time is prolonged;

step 4.1.5: and (3) manually saving data: when the pressure maintaining time is reached, the loading test is finished, a data storage button on the operation panel is opened, and the control program is finished;

step 4.2.1: inputting initial parameters: the loading speed is input through the operation panel, according to the formula (1),

wherein, I is the input current value of the electric proportional variable pump, v is the loading speed of the static load hydraulic cylinder, A is the effective area of the static load hydraulic cylinder, and Q_maxMaximum flow rate of the electric proportional variable pump, I_maxThe maximum input current value of the electric proportional variable pump;

the controller automatically calculates to obtain a displacement signal of the electric proportional variable pump, an error value occurs between the signal and the measurement value of the hydraulic cylinder position feedback sensor, and the error value triggers the three-position four-way electromagnetic proportional valve to work, so that the hydraulic cylinder is adjusted to work, and the displacement of the electric proportional variable pump is the same as the signal value;

inputting loading force through an operation panel, automatically calculating by a controller according to a formula (2) to obtain a pressure signal of a proportional overflow valve, and setting the overflow pressure of the system;

wherein U is the input voltage value of the proportional overflow valve, F is the loading force of the static hydraulic cylinder, A is the effective area of the static hydraulic cylinder, and P is the effective area of the static hydraulic cylinder_maxIs the maximum pressure of the proportional relief valve, U_maxThe maximum input voltage value of the proportional overflow valve is obtained;

step 4.2.2: inputting a loading displacement curve: inputting a static loading displacement curve through an operation panel, detecting an error value of a first displacement sensor and the loading displacement curve, controlling the opening degree of a valve port of a first three-position four-way servo valve by adopting an adaptive PID algorithm, when the difference value between the first displacement sensor and the loading displacement curve is less than zero, the first three-position four-way servo valve works at the left position, pressure oil enters a second cartridge valve and then enters a left rod cavity of a static load hydraulic cylinder to push the static load hydraulic cylinder to move rightwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in a right rod cavity of the static load hydraulic cylinder enters the left position of the first three-position four-way servo valve through the first cartridge valve and flows back to an oil tank; when the difference value between the first displacement sensor and the loading displacement curve is larger than zero, the right position of the first three-position four-way servo valve works, pressure oil enters the first cartridge valve and then enters the right rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move leftwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in the left rod cavity of the static hydraulic cylinder enters a right bit flow oil return tank of the first three-position four-way servo valve through the second cartridge valve; when loading is finished, the difference value between the first displacement sensor and a loading displacement curve is equal to zero, the middle position of the first three-position four-way servo valve works, the reversing valve of the first control cover plate is electrified, the left position works, the first cartridge valve is closed, the reversing valve of the second control cover plate is electrified, the left position works, the second cartridge valve is closed, the static load hydraulic cylinder is static, and the pressure maintaining state is entered;

step 4.2.3: automatically opening an energy accumulator for pressure maintaining: after the first control cover plate reversing valve and the second control cover plate reversing valve are electrified, the energy accumulator stop valve is automatically electrified, the stop valve is opened, hydraulic oil in the energy accumulator enters a hydraulic system, leakage of the system is supplemented, and the pressure maintaining time is prolonged;

step 4.2.4: automatically saving data: when the pressure maintaining time is reached, the loading test is finished, the data are automatically stored, and the control program is finished;

step 3.2: manual/automatic mode determination: judging whether the operation mode is an automatic mode or not through a manual/automatic switching button on the operation panel, and if the operation mode is the manual mode, entering the step 4.3.1; if the mode is the automatic mode, entering 4.4.1;

step 4.3.1: manually adjusting the flow of the system, adjusting a displacement knob of the electric proportional variable pump on an operation panel, wherein an error value occurs between the input quantity and the measured value of a hydraulic cylinder position feedback sensor, and the error value triggers a three-position four-way electromagnetic proportional valve to work, so that the hydraulic cylinder is adjusted to work, and the displacement of the electric proportional variable pump is the same as the input value;

step 4.3.2: manually adjusting the pressure of the system, adjusting a pressure knob of a proportional overflow valve on an operation panel, and setting the overflow pressure of the system;

step 4.3.3: manually opening the accumulator to increase flow: opening an energy accumulator stop valve button on the operation panel, opening an energy accumulator stop valve, and allowing hydraulic oil in the energy accumulator to enter a hydraulic system to increase the flow of the hydraulic system;

step 4.3.4: manually controlling the dynamic loading cylinder to stretch: adjusting the input value of a second three-position four-way servo valve on the operation panel, when the operation panel is adjusted in the forward direction, the left position of the second three-position four-way servo valve works, pressure oil enters a left rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move rightwards, and hydraulic oil in a right rod cavity of the static hydraulic cylinder flows back to an oil tank through the left position of the second three-position four-way servo valve; when the hydraulic oil is reversely adjusted, the right position of the second three-position four-way servo valve works, the pressure oil enters a right rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move leftwards, and the hydraulic oil in the left rod cavity of the static hydraulic cylinder returns to an oil tank through the right position of the second three-position four-way servo valve; when the neutral position is adjusted back, the neutral position of the second three-position four-way servo valve works, and the static load hydraulic cylinder is static and stops working;

step 4.3.5: and (3) manually saving data: opening a data storage button on the operation panel and ending the control program;

step 4.4.1: inputting initial parameters: inputting a loading speed through an operation panel, automatically calculating by a controller to obtain a displacement signal of the electric proportional variable pump according to a formula (1), wherein an error value is generated between the displacement signal and a measurement value of a hydraulic cylinder position feedback sensor, and the error value triggers a three-position four-way electromagnetic proportional valve to work so as to adjust the hydraulic cylinder to work and realize that the displacement of the electric proportional variable pump is the same as the signal value;

step 4.4.2: inputting a loading displacement curve: inputting a dynamic loading displacement curve through an operation panel, detecting an error value between a first displacement sensor and the loading displacement curve, automatically powering on an energy accumulator stop valve after detecting the error value, opening the stop valve, and enabling hydraulic oil in the energy accumulator to enter a hydraulic system to increase the flow of the hydraulic system; according to the detected error value, the opening degree of a valve port of the first three-position four-way servo valve is controlled by adopting a self-adaptive PID algorithm, when the difference value between the first displacement sensor and a loading displacement curve is less than zero, the left position of the second three-position four-way servo valve works, pressure oil enters a left rod cavity of the static load hydraulic cylinder to push the static load hydraulic cylinder to move rightwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in a right rod cavity of the static load hydraulic cylinder flows back to an oil tank through the left position of the second three-position four-way servo valve; when the difference value between the first displacement sensor and the loading displacement curve is larger than zero, the right position of the second three-position four-way servo valve works, pressure oil enters a right rod cavity of the static load hydraulic cylinder to push the static load hydraulic cylinder to move leftwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in the left rod cavity of the static load hydraulic cylinder returns to an oil tank through the right bit flow of the second three-position four-way servo valve; when the loading is finished and the difference value between the first displacement sensor and the loading displacement curve is equal to zero, the middle position of the second three-position four-way servo valve works, and the static load hydraulic cylinder is static and stops working;

step 4.4.3: automatically saving data: and (5) after the loading test is finished, automatically storing related data and finishing the control program.

The beneficial technical effects are as follows:

1. the invention discloses a dynamic and static loading comprehensive electro-hydraulic system of a damping damper and a control method thereof, which solve the problems of resource waste and high energy consumption caused by the fact that the conventional damping test bed is divided into a static loading test bed and a dynamic loading test bed, and the electro-hydraulic systems and the control methods of the static loading test bed and the dynamic loading test bed are independently designed, so that the static loading and the dynamic loading of the electro-hydraulic system of the damping damper test bed share one hydraulic system, the space is saved, and the material is saved;

2. in the invention, the pressure maintaining measure of the static loading hydraulic system adopts the dual functions of the two-way cartridge valve and the energy accumulator, thereby effectively prolonging the pressure maintaining time;

3. in the invention, the dynamically loaded hydraulic system adopts a combination of a small-flow pump station and an energy accumulator, and the energy accumulator provides instantaneous large flow for the hydraulic system, thus meeting the requirement of high speed of dynamic loading and saving energy;

4. according to the control method of the dynamic and static loading comprehensive test bed of the damping damper, the overflow flow of an overflow valve is ensured to be minimum according to the displacement signal of the hydraulic pressure pump, and energy is saved; according to the loading force, the controller automatically solves a pressure signal for solving the proportional overflow valve, so that the overflow pressure of the overflow valve is ensured to be lowest, and energy is saved;

5. the invention has the functions of manual and automatic switching, namely manual control under special working conditions, realization of loading tests under different conditions, and realization of automatic control under the conventional conditions, thereby reducing labor force and improving automation level.

Drawings

In order to more clearly illustrate the technical solution of the present invention, the drawings used in the description of the embodiments will be briefly described below.

FIG. 1 is a hydraulic schematic diagram of a dynamic and static loading comprehensive electro-hydraulic system of a shock absorber damper;

FIG. 2 is a hydraulic schematic diagram of an oil source valve bank in a dynamic and static loading comprehensive electro-hydraulic system of a shock absorption damper according to the invention;

FIG. 3 is a hydraulic schematic diagram of a control valve group in a dynamic and static loading comprehensive electro-hydraulic system of a shock absorber damper according to the present invention;

FIG. 4 is a hydraulic schematic diagram of a pressure regulating valve bank in the dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper;

FIG. 5 is a hydraulic schematic diagram of a control valve bank of a static hydraulic cylinder in the dynamic and static loading comprehensive electro-hydraulic system of the damping damper according to the invention;

FIG. 6 is a hydraulic schematic diagram of a dynamic hydraulic cylinder control valve group in the dynamic and static loading comprehensive electro-hydraulic system of the damping damper according to the present invention;

FIG. 7 is a structural block diagram of a dynamic and static loading comprehensive electro-hydraulic system of a shock absorber damper according to the present invention;

FIG. 8 is a flow chart of a control method of the dynamic and static loading comprehensive electro-hydraulic system of the shock absorber damper.

Wherein, 1-an oil tank, 2-an oil source valve group, 21-an electric proportional variable pump, 22-a regulating hydraulic cylinder, 23-a three-position four-way electromagnetic proportional valve, 24-a hydraulic cylinder position feedback sensor, 3-a first oil suction filter, 4-a first motor, 5-an energy accumulator, 6-a pressure regulating valve group, 61-a third pressure sensor, 62-a second one-way valve, 63-a third oil filter, 64-an unloading pressure reducing valve, 65-a second two-position two-way electromagnetic valve, 66-a proportional overflow valve, 7-a static load hydraulic cylinder, 8-a static load hydraulic cylinder control valve group, 81-a fourth pressure sensor, 82-a first three-position four-way servo valve, 83-a fifth pressure sensor, 84-a first cartridge valve and 85-a first control cover plate reversing valve, 86-sixth pressure sensor, 87-seventh pressure sensor, 88-second control cover plate reversing valve, 89-second cartridge valve, 8 a-eighth pressure sensor, 8 b-ninth pressure sensor, 9-dynamic load hydraulic cylinder, 10-dynamic load hydraulic cylinder control valve group, 101-second three-position four-way servo valve, 102-tenth pressure sensor, 103-eleventh pressure sensor, 104-twelfth pressure sensor, 105-thirteenth pressure sensor, 11-control valve group, 111-second pressure oil filter, 112-first two-position two-way electromagnetic valve, 113-second pressure sensor, 114-overflow valve, 12-first hydraulic pump, 13-second motor, 14-first displacement sensor, 15-first force sensor, 16-a second displacement sensor, 17-a second force sensor, 18-a cooler, 19-a first pressure oil filter, 20-an overflow pressure reducing valve, 21-a second hydraulic pump, 22-a second oil suction filter, 23-a third motor, 24-a first cut-off valve, 25-a second cut-off valve, 26-a heater, 27-an air filter, 28-a liquid level relay, 29-a temperature transmitter, 30-a liquid level meter, 31-a first pressure sensor, 32-a first one-way valve.

Detailed Description

Reference will now be made in detail to embodiments of the present invention, examples of which are illustrated in the accompanying drawings, wherein like or similar reference numerals refer to the same or similar elements or elements having the same or similar function throughout. The embodiments described below with reference to the accompanying drawings are illustrative only for the purpose of explaining the present invention, and are not to be construed as limiting the present invention.

Embodiments of the present invention will be described in detail below with reference to the accompanying drawings.

The invention discloses a dynamic and static loading comprehensive electro-hydraulic system of a damping damper, which comprises an oil tank 1, an oil source valve group 2, an electric proportional variable pump 21, a regulating hydraulic cylinder 22, a three-position four-way electromagnetic proportional valve 23, a hydraulic cylinder position feedback sensor 24, a first oil absorption filter 3, a first motor 4, an energy accumulator 5, a pressure regulating valve group 6, a third pressure sensor 61, a second one-way valve 62, a third oil compression filter 63, an unloading pressure reducing valve 64, a second two-position two-way electromagnetic valve 65, a proportional overflow valve 66, a static load hydraulic cylinder 7, a static load hydraulic cylinder control valve group 8, a fourth pressure sensor 81, a first four-way three-position servo valve 82, a fifth pressure sensor 83, a first cartridge valve 84, a first control cover plate reversing valve 85, a sixth pressure sensor 86, a seventh pressure sensor 87, A second control cover plate reversing valve 88, a second cartridge valve 89, an eighth pressure sensor 8a, a ninth pressure sensor 8b, a dynamic load hydraulic cylinder 9, a dynamic load hydraulic cylinder control valve group 10, a second three-position four-way servo valve 101, a tenth pressure sensor 102, an eleventh pressure sensor 103, a twelfth pressure sensor 104, a thirteenth pressure sensor 105, a control valve group 11, a second pressure oil filter 111, a first two-position two-way electromagnetic valve 112, a second pressure sensor 113, an overflow valve 114, a first hydraulic pump 12, a second motor 13, a first displacement sensor 14, a first force sensor 15, a second displacement sensor 16, a second force sensor 17, a cooler 18, a first pressure oil filter 19, an overflow pressure reducing valve 20, a second hydraulic pump 21, a second oil suction filter 22, a third motor 23, a first stop valve 24, a second stop valve 25, a heater 26, An air filter 27, a liquid level relay 28, a temperature transmitter 29, a liquid level meter 30, a first pressure sensor 31 and a first check valve 32; the oil tank 1 is used for storing oil required by the system; preferably, the oil source valve group 2 comprises an electric proportional variable pump 21, a regulating hydraulic cylinder 22, a three-position four-way electromagnetic proportional valve 23 and a hydraulic cylinder position feedback sensor, the electric proportional variable pump 21 sucks oil from the oil tank 1 through rotation, and supplies oil to the pressure regulating valve group 6; the hydraulic cylinder 22 is adjusted to control the flow of the electric proportional pump 21; the three-position four-way electromagnetic proportional valve 23 is used for controlling and adjusting the position of a piston rod of the hydraulic cylinder 22; the hydraulic cylinder position feedback sensor 24 is used for detecting and adjusting the position of the piston rod of the hydraulic cylinder 22; the first oil suction filter 3 is used for filtering oil sucked from the oil tank 1 by the oil source valve group 2; the first motor 4 is connected with the oil source valve group 2 through a coupler and drives the electric proportional variable pump 21 to rotate; the accumulator 5 is used for providing instantaneous large flow during dynamic loading; the pressure regulating valve group 6 is used for regulating the pressure of the system; the static load hydraulic cylinder 7 is used for applying static load; the static load hydraulic cylinder control valve group 8 is used for supplying oil to the static load hydraulic cylinder 7 so as to control the movement direction of a piston rod of the static load hydraulic cylinder 7; the dynamic load hydraulic cylinder 9 is used for applying dynamic load; the dynamic load hydraulic cylinder control valve group 10 is used for supplying oil to the dynamic load hydraulic cylinder 9 so as to control the movement direction of a piston rod of the dynamic load hydraulic cylinder 9; the control oil valve group 11 is used for supplying oil to the oil source valve group 2; the first hydraulic pump 12 sucks oil from the oil tank 1 through rotation and supplies oil to the control valve group 11; the second motor 13 is connected with the first hydraulic pump 12 through a coupler and drives the first hydraulic pump 12 to rotate; the first displacement sensor 14 is used for measuring the movement speed of the piston rod of the static hydraulic cylinder 7; the first force sensor 15 is used for measuring the force borne by the piston rod of the static hydraulic cylinder 7 during movement; the second displacement sensor 16 is used for measuring the movement speed of the piston rod of the dynamic load hydraulic cylinder 9; the second force sensor 17 is used for measuring the force borne by the piston rod of the dynamic load hydraulic cylinder 9 during movement; the cooler 18 is used for cooling oil in the oil tank 1; a first pressurized oil filter 19 for supplying oil to the cooler 18; the relief valve 20 is used to prevent system overload; the second hydraulic pump 21 sucks oil from the oil tank 1 by rotation and supplies the oil to the first oil filter 19 and the relief valve 20; the second oil suction filter 22 is used for filtering oil sucked by the second hydraulic pump 21 from the oil tank 1; the third motor 23 is connected with the second hydraulic pump 21 through a coupler and drives the second hydraulic pump 21 to rotate; the first stop valve 24 is used for controlling the connection and the closing of the oil path; the second stop valve 25 is used for controlling the opening and closing of the oil tank 1; the heater 26 is fixedly arranged inside the oil tank 1 and used for ensuring that oil in the oil tank 1 is not condensed; an air cleaner 27 is fixedly installed at an upper portion of the oil tank 1 to prevent particulate contaminants from entering the system through the oil tank 1; the liquid level relay 28 is used for controlling the height of oil in the oil tank 1; the temperature transmitter 29 is used for measuring the temperature of the oil in the oil tank 1; the liquid level meter 30 is fixedly arranged on the side surface of the oil tank 1 and used for measuring the height of oil in the oil tank 1; the first pressure sensor 31 is used for measuring the pressure value of the oil outlet of the second hydraulic pump 21; the first check valve 32 is used for differential pressure protection and when the cooler 18 is blocked, flow is passed through the first check valve 32.

As an embodiment of the present invention, the connection relationship of the hydraulic pipelines is that an oil inlet P of the first oil suction filter 3, an oil return port T of the oil source valve group 2, an oil suction port S of the first hydraulic pump 12, an oil return port T of the control oil valve group 11, an oil return port T of the pressure regulating valve group 6, an oil drainage port L of the pressure regulating valve group 6, an oil return port T of the static hydraulic cylinder control valve group 8, an oil drainage port L of the static hydraulic cylinder control valve group 8, an oil inlet P of the second oil suction filter 22, an oil drainage port L of the overflow pressure reducing valve 20, an oil outlet a of the cooler 18, and an oil outlet a of the first check valve 32 are connected to the oil tank 1 through hydraulic pipelines; an output shaft of the first motor 4 is connected with an input shaft of the oil source valve group 2 through a coupler, and an oil outlet A of the first oil suction filter 3 is connected with an oil suction port S of the oil source valve group 2 through a hydraulic pipeline; an output shaft of the second motor 13 is connected with an input shaft of the first hydraulic pump 12 through a coupler; an oil outlet A of the first hydraulic pump 12 is connected with an oil inlet P of the control valve group 11 through a hydraulic pipeline; an oil inlet P of the oil source valve group 2 is connected with an oil outlet A of the control oil valve group 11 through a hydraulic pipeline, an oil outlet A of the oil source valve group 12 is connected with an oil inlet P of the pressure regulating valve group 6 through a hydraulic pipeline, an oil outlet B of the pressure regulating valve group 6 is connected with an oil inlet P of the energy accumulator 5 through a hydraulic pipeline, an oil outlet A of the pressure regulating valve group 6 is connected with an oil inlet P of the static hydraulic cylinder control valve group 8 and an oil inlet P of the dynamic hydraulic cylinder control valve group 10 through hydraulic pipelines, an oil outlet A of the static hydraulic cylinder control valve group 8 is connected with a left rod cavity oil inlet of the static hydraulic cylinder 7 through a hydraulic pipeline, and an oil outlet B of the static hydraulic cylinder control valve group 8 is connected with a right rod cavity oil inlet P of the static hydraulic cylinder 7 through a hydraulic pipeline; an oil outlet A of the dynamic hydraulic cylinder control valve group 10 is connected with an oil inlet of a left rod cavity of the dynamic hydraulic cylinder 9 through a hydraulic pipeline, and an oil outlet B of the dynamic hydraulic cylinder control valve group 10 is connected with an oil inlet of a right rod cavity of the dynamic hydraulic cylinder 9 through a hydraulic pipeline; an oil return port T of the static load hydraulic cylinder control valve group 8, an oil return port T of the dynamic load hydraulic cylinder control valve group 10 and an oil return port T of the pressure regulating valve group 6 are connected through hydraulic pipelines; an oil drainage port L of the static load hydraulic cylinder control valve group 8, an oil drainage port L of the dynamic load hydraulic cylinder control valve group 10 and an oil drainage port L of the pressure regulating valve group are connected through hydraulic pipelines; an oil outlet A of the second oil suction filter 22 is connected with an oil inlet P of the first stop valve 24 through a hydraulic pipeline, an oil outlet A of the first stop valve 24 is connected with an oil suction port S of the second hydraulic pump 21 through a hydraulic pipeline, an output shaft of the third motor 23 is connected with an input shaft of the second hydraulic pump 21 through a coupler, an oil outlet A of the second hydraulic pump 21 is connected with an oil inlet P of the first oil suction filter 19, an oil inlet P of the overflow reducing valve 20 and an oil inlet P of the first pressure sensor 31 through hydraulic pipelines, an oil outlet A of the first oil suction filter 19 is connected with an oil inlet P of the first check valve 32 and an oil inlet P of the cooler 18 through hydraulic pipelines, and an oil outlet of the first check valve 32 is connected with an oil outlet A of the cooler 18 through hydraulic pipelines.

As a preferred embodiment of the present invention, the dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper further comprises a heater 26, an air filter 27, a liquid level relay 28, a temperature transmitter 29, a liquid level meter 30 and a first pressure sensor 31, wherein the heater 26 is fixedly installed inside the oil tank 1 to ensure that oil in the oil tank 1 is not condensed; an air filter 27 is fixedly installed at the upper portion of the oil tank 1 to prevent particulate contaminants from entering the system through the oil tank 1; the liquid level relay 28 is used for controlling the height of oil in the oil tank 1; the temperature transmitter 29 is used for measuring the temperature of the oil in the oil tank 1; the liquid level meter 30 is fixedly arranged on the side surface of the oil tank 1 and is used for measuring the height of oil in the oil tank 1; the first pressure sensor 31 is used for measuring the pressure value of the oil outlet of the second hydraulic pump 21.

As an embodiment of the present invention, the oil source valve group 2 includes an electric proportional variable pump 21, a regulating hydraulic cylinder 22, a three-position four-way electromagnetic proportional valve 23 and a hydraulic cylinder position feedback sensor 24, an oil suction port S, an oil outlet a, an oil inlet P and an oil return port T are drilled on the source valve group 2, the hydraulic pipeline connection relationship of the oil source valve group 2 is shown in fig. 2, specifically, the oil inlet P of the electric proportional variable pump 21 is connected with the oil suction port S of the oil source valve group 2 through an internal flow channel of the oil source valve group 2, the oil outlet L of the electric proportional variable pump 21 is connected with the oil outlet a of the oil source valve group 2 through an internal flow channel of the oil source valve group 2, the oil discharge port L of the electric proportional variable pump 21 is connected with the oil return port T of the oil source valve group 2 through an internal flow channel of the oil source valve group 2, the oil inlet of the three-position four-way electromagnetic proportional valve 23 is connected with the oil inlet P of the oil source valve group 2 through an internal flow channel of the oil source valve group 2, an oil return port T of the three-position four-way electromagnetic proportional valve 23 is connected with an oil return port T of the oil source valve group 2 through an internal flow passage of the oil source valve group 2, an outlet A of the three-position four-way electromagnetic proportional valve 23 is connected with an oil inlet P1 of the adjusting hydraulic cylinder 22 through the internal flow passage of the oil source valve group 2, and an oil outlet B of the three-position four-way electromagnetic proportional valve is connected with an oil inlet P2 of the adjusting hydraulic cylinder 22 through the internal flow passage of the oil source valve group 2.

As an embodiment of the present invention, the control valve group 11 includes a second pressure oil filter 111, a first two-position two-way solenoid valve 112, a second pressure sensor 113 and an overflow valve 114, the second pressure oil filter 111 is used for filtering oil sucked into the control valve group 11; the first two-position two-way electromagnetic valve 112 is used for controlling the flow direction of oil; the second pressure sensor 113 is used for measuring the pressure at the oil inlet of the control valve group 11; the relief valve 114 is used to ensure that the pressure of the control valve group 11 does not exceed a specified range; an oil inlet P and an oil outlet A and an oil return port T are respectively drilled on the control oil valve group 30, and a hydraulic pipeline connection relation of the control oil valve group 11 is shown in FIG. 3, specifically, an oil inlet P of a second pressure oil filter 111 is connected with an oil inlet P of the control oil valve group 11 through an internal flow channel of the control oil valve group 11, an oil outlet A of the second pressure oil filter 111, an oil inlet P of a first two-position two-way electromagnetic valve 112, an oil inlet P of a second pressure sensor 113 and an oil inlet P of an overflow valve 114 are connected through an internal flow channel of the control oil valve group 11, an oil outlet A of the first two-position two-way electromagnetic valve 112 is connected with an oil outlet A of the control oil valve group 11 through an internal flow channel of the control oil valve group 11, and an oil outlet B of the first two-position two-way electromagnetic valve 112, an oil outlet A of the overflow valve 114 and an oil return port T of the control oil valve group 11 are connected through an internal flow channel of the control oil valve group 11.

As an embodiment of the present invention, the pressure regulating valve group 6 includes a third pressure sensor 61, a second check valve 62, a third pressure oil filter 63, an unloading pressure reducing valve 64, a second two-position two-way solenoid valve 65 and a proportional overflow valve 66, wherein the third pressure sensor 61 is used for measuring the pressure at the oil inlet of the pressure regulating valve group 6; the second check valve 62 is used for preventing the oil from flowing back to the oil return source valve set 2; the third pressure oil filter 63 is used for filtering oil sucked by the pressure regulating valve group 6; the unloading pressure reducing valve 64 is used for automatically controlling unloading or loading of the pump; the second two-position two-way solenoid valve 65 is used for controlling the working state of the unloading and reducing valve 64; the proportional relief valve 66 is used for controlling the system pressure and preventing the system from overloading; an oil inlet P and an oil outlet A and an oil return port T are respectively drilled on the pressure regulating valve group 6, the hydraulic pipeline connection relation of the control oil valve group 11 is shown in FIG. 4, specifically, an oil inlet P of a third pressure sensor 61, an oil inlet P of a second check valve 62 and an oil inlet P of the pressure regulating valve group 6 are connected through an internal flow channel of the pressure regulating valve group 6, an oil outlet A of the second check valve 62 is connected with an oil inlet P of a third pressure oil filter 63 through an internal flow channel of the pressure regulating valve group 6, an oil outlet A of the third pressure oil filter 63, an oil outlet B of the pressure regulating valve group 6, an oil outlet A of the pressure regulating valve group 6, an oil inlet P of an unloading and reducing valve 64 and an oil inlet P of a proportional overflow valve 66 are connected through an internal flow channel of the pressure regulating valve group 6, an oil outlet A of the unloading and reducing valve 64 is connected with an oil inlet P of a second two-way electromagnetic valve 65 through an internal flow channel of the pressure regulating valve group 6, an oil return port T of the unloading and reducing valve 64, The oil drain port L of the unloading pressure reducing valve 64, the oil return port T of the second two-position two-way solenoid valve 65, the oil return port T of the proportional overflow valve 66 and the oil return port T of the pressure regulating valve group 6 are connected through an internal flow passage of the pressure regulating valve group 6, and the oil drain port L of the proportional overflow valve 66 and the oil drain port L of the pressure regulating valve group 6 are connected through an internal flow passage of the pressure regulating valve group 6.

As an embodiment of the present invention, the static hydraulic cylinder control valve group 8 includes a fourth pressure sensor 81, a first three-position four-way servo valve 82, a fifth pressure sensor 83, a first cartridge valve 84, a first control cover plate reversing valve 85, a sixth pressure sensor 86, a seventh pressure sensor 87, a second control cover plate reversing valve 88, a second cartridge valve 89, an eighth pressure sensor 8a and a ninth pressure sensor 8b, wherein the fourth pressure sensor 81 is used for measuring the pressure at the oil inlet of the static hydraulic cylinder control valve group 8; the first three-position four-way servo valve 82 is used for controlling the motion direction of the piston rod of the static hydraulic cylinder 7; the fifth pressure sensor 83 is used for measuring the pressure of the oil inlet of the first cartridge valve 84 and the oil inlet of the first control cover plate reversing valve 85; the first cartridge valve 84 is used for controlling the flow of oil flowing into the left rod cavity of the static hydraulic cylinder 7; the first control cover reversing valve 85 is used for controlling the working state of the first cartridge valve 84; the sixth pressure sensor 86 is used for measuring the pressure of the left rod cavity of the static hydraulic cylinder 7; the seventh pressure sensor 87 is used for measuring the pressure of the right rod cavity of the static hydraulic cylinder 7; the second control cover plate reversing valve 88 is used for controlling the working state of the second cartridge valve 89; the second cartridge valve 89 is used for controlling the flow of oil flowing into the right rod cavity of the static hydraulic cylinder 7; the eighth pressure sensor 8a is used for measuring the pressure of the oil inlet of the second cartridge valve 89 and the oil inlet of the second control cover plate reversing valve 88; the ninth pressure sensor 8b is used for measuring the pressure of an oil return port of the control valve group 8 of the static hydraulic cylinder; an oil inlet P, an oil outlet A, an oil return port T and an oil drain port L are respectively drilled on the static load hydraulic cylinder control valve group 8, the connection relation of hydraulic pipelines of the static load hydraulic cylinder control valve group 8 is shown in FIG. 5, specifically, the oil inlet P of the first three-position four-way servo valve 82, the oil inlet M of the fourth pressure sensor 81 and the oil inlet P of the static load hydraulic cylinder control valve group 8 are connected through an internal flow passage of the static load hydraulic cylinder control valve group 8, the oil return port T of the first three-position four-way servo valve 82, the oil inlet M of the ninth pressure sensor 8b and the oil return port T of the static load hydraulic cylinder control valve group 8 are connected through an internal flow passage of the static load hydraulic cylinder control valve group 8, the oil outlet A of the first three-position four-way servo valve 82, the oil inlet M of the fifth pressure sensor 83, the oil inlet A of the first cartridge valve 84 and the oil inlet X of the first control cover plate reversing valve 85 are connected through an internal flow passage of the static load hydraulic cylinder control valve group 8, an oil outlet B of the first three-position four-way servo valve 82, an oil inlet M of the eighth pressure sensor 8a, an oil inlet A of the second cartridge valve 89 and an oil inlet X of the second control cover plate reversing valve 88 are connected through an internal flow channel of the static hydraulic cylinder control valve group 8, an oil return port T of the first control cover plate reversing valve 85, an oil outlet B of the first cartridge valve 84, an oil inlet P of the sixth pressure sensor 86 and an oil outlet A of the static hydraulic cylinder control valve group 8 are connected through an internal flow channel of the static hydraulic cylinder control valve group 8, an oil return port T of the second control cover plate reversing valve 88, an oil outlet B of the second cartridge valve 89, an oil inlet M of the seventh pressure sensor 87 and an oil outlet B of the static hydraulic cylinder control valve group 8 are connected through an internal flow channel of the static hydraulic cylinder control valve group 8.

As an embodiment of the invention, the control valve group 10 of the dynamic load hydraulic cylinder comprises a second three-position four-way servo valve 101, a tenth pressure sensor 102, an eleventh pressure sensor 103, a twelfth pressure sensor 104 and a thirteenth pressure sensor 105, wherein the second three-position four-way servo valve 101 is used for controlling the movement direction of the piston rod of the dynamic load hydraulic cylinder 9; the tenth pressure sensor 102 is used for measuring the pressure of an oil inlet of the dynamic hydraulic cylinder control valve group 10; the eleventh pressure sensor 103 is used for measuring the pressure of the left rod cavity of the dynamic hydraulic cylinder 9; the twelfth pressure sensor 104 is used for measuring the pressure of the right rod cavity of the dynamic hydraulic cylinder 9; the thirteenth pressure sensor 105 is used for measuring the pressure at the oil outlet of the control valve group 10 of the dynamic hydraulic cylinder; an oil inlet P, an oil outlet A, an oil return port T and an oil drain port L are respectively drilled on the dynamic hydraulic cylinder control valve group 10, the connection relation of hydraulic pipelines of the dynamic hydraulic cylinder control valve group 10 is shown in FIG. 6, specifically, the oil inlet P of the second three-position four-way servo valve 101, the oil inlet M of the tenth pressure sensor 102 and the oil inlet P of the dynamic hydraulic cylinder control valve group 10 are connected through an internal flow passage of the dynamic hydraulic cylinder control valve group 10, the oil outlet A of the second three-position four-way servo valve 101, the oil inlet M of the eleventh pressure sensor 103 and the oil outlet A of the dynamic hydraulic cylinder control valve group 10 are connected through an internal flow passage of the dynamic hydraulic cylinder control valve group 10, the oil outlet B of the second three-position four-way servo valve 101, the oil inlet M of the twelfth pressure sensor 104 and the oil outlet B of the dynamic hydraulic cylinder control valve group 10 are connected through an internal flow passage of the dynamic hydraulic cylinder control valve group 10, an oil return port T of the second three-position four-way servo valve 101, an oil inlet M of the thirteenth pressure sensor 105 and an oil return port T of the dynamic load hydraulic cylinder control valve group 10 are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group 10, and an oil drainage port L of the second three-position four-way servo valve 101 is connected with an oil drainage port L of the dynamic load hydraulic cylinder control valve group 10 through an internal flow channel of the dynamic load hydraulic cylinder control valve group 10.

The invention discloses a control method of a dynamic and static loading comprehensive electro-hydraulic system of a shock absorber damper, which specifically comprises the following steps of:

specifically, whether input and output parameters of a controller, a displacement sensor, a force sensor, a control oil valve group, an oil source valve group, a pressure regulating valve group, a static load cylinder control valve group, a static load hydraulic cylinder, a dynamic load cylinder control valve group, a dynamic load hydraulic cylinder, a cooling and filtering system and the like are normal or not is checked, if not, the operation is not performed downwards, and an alarm signal is sent to an abnormal alarm indicator lamp; if normal, execution continues down.

step 4.1.3: manually controlling the extension of the static load cylinder: the input value of a first three-position four-way servo valve on the operation panel is adjusted, when the operation panel is adjusted in the forward direction, the left position of the first three-position four-way servo valve works, pressure oil enters a second cartridge valve and then enters a left rod cavity of the static load hydraulic cylinder to push the static load hydraulic cylinder to move rightwards, and hydraulic oil in a right rod cavity of the static load hydraulic cylinder enters the left position of the first three-position four-way servo valve through the first cartridge valve and flows back to an oil tank; when the hydraulic oil is reversely adjusted, the right position of the first three-position four-way servo valve works, the pressure oil enters the first cartridge valve and then enters the right rod cavity of the static hydraulic cylinder to push the static hydraulic cylinder to move leftwards, and the hydraulic oil in the left rod cavity of the static hydraulic cylinder enters the right bit flow oil return tank of the first three-position four-way servo valve through the second cartridge valve; when the neutral position is adjusted back, the neutral position of the first three-position four-way servo valve works, the reversing valve of the first control cover plate is electrified, the left position works, the first cartridge valve is closed, the reversing valve of the second control cover plate is electrified, the left position works, the second cartridge valve is closed, the static load hydraulic cylinder is static, and the pressure maintaining state is entered;

wherein, U is the input voltage value of the proportional overflow valve, F is the loading force of the static hydraulic cylinder, A is the effective area of the static hydraulic cylinder, and P is_maxIs the maximum pressure of the proportional relief valve, U_maxThe maximum input voltage value of the proportional overflow valve is obtained;

step 4.2.4: automatically saving data: when the pressure maintaining time is reached, the loading test is finished, the data is automatically stored, and the control program is finished;

step 4.3.2: manually adjusting the system pressure, adjusting a pressure knob of a proportional overflow valve on an operation panel, and setting the system overflow pressure;

step 4.4.2: inputting a loading displacement curve: inputting a dynamic loading displacement curve through an operation panel, detecting an error value between a first displacement sensor and the loading displacement curve, automatically electrifying a stop valve of the energy accumulator after detecting the error value, opening the stop valve, and allowing hydraulic oil in the energy accumulator to enter a hydraulic system to increase the flow of the hydraulic system; according to the detected error value, the opening degree of a valve port of the first three-position four-way servo valve is controlled by adopting a self-adaptive PID algorithm, when the difference value between the first displacement sensor and a loading displacement curve is less than zero, the left position of the second three-position four-way servo valve works, pressure oil enters a left rod cavity of the static load hydraulic cylinder to push the static load hydraulic cylinder to move rightwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in a right rod cavity of the static load hydraulic cylinder flows back to an oil tank through the left position of the second three-position four-way servo valve; when the difference value between the first displacement sensor and the loading displacement curve is larger than zero, the right position of the second three-position four-way servo valve works, pressure oil enters a right rod cavity of the static load hydraulic cylinder to push the static load hydraulic cylinder to move leftwards, the difference value between the first displacement sensor and the loading displacement curve is reduced, and hydraulic oil in the left rod cavity of the static load hydraulic cylinder returns to an oil tank through the right bit flow of the second three-position four-way servo valve; when the loading is finished and the difference value between the first displacement sensor and the loading displacement curve is equal to zero, the middle position of the second three-position four-way servo valve works, the static load hydraulic cylinder is static, and the second three-position four-way servo valve stops working;

step 4.4.3: automatically saving data: and (5) after the loading test is finished, automatically storing the related data, and finishing the control program.

The dynamic and static loading comprehensive electro-hydraulic system of the damping damper disclosed by the invention has the advantages that the static loading and the dynamic loading share one set of hydraulic station, so that the space and the material are saved; the pressure maintaining measure of the static loading hydraulic system adopts the dual functions of a two-way cartridge valve and an energy accumulator, so that the pressure maintaining time is prolonged; the dynamic loading hydraulic system adopts a combination form of a small-flow pump station and an energy accumulator, and the energy accumulator provides instantaneous large flow for the hydraulic system, so that the requirement of high speed of dynamic loading can be met, and energy can be saved; the dynamic and static loading control method of the damping damper ensures that the overflow flow of the overflow valve is minimum according to the displacement signal of the hydraulic pump, thereby saving energy; according to the loading force, the controller automatically solves a pressure signal for solving the proportional overflow valve, so that the overflow pressure of the overflow valve is ensured to be lowest, and energy is saved; the automatic loading test device has the functions of manual and automatic switching, namely, the manual control under special working conditions can be realized, the loading tests under different conditions can be realized, the automatic control under the conventional condition can also be realized, the labor force is reduced, and the automation level is improved.

In the description herein, references to the description of the term "one embodiment," "some embodiments," "an example," "a specific example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the invention. In this specification, the schematic representations of the terms used above do not necessarily refer to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

The above examples are only for describing 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 to the technical solution of the present invention by those skilled in the art without departing from the spirit of the present invention should fall within the protection scope defined by the claims of the present invention.

Claims

1. The utility model provides a dynamic and static loading comprehensive electro-hydraulic system of shock absorber damper which characterized in that includes:

the oil tank (1) is used for storing oil liquid required by the system;

-an oil source valve group (2), the oil source valve group (2) comprising:

the electric proportional variable pump (21) sucks oil from the oil tank (1) through rotation, and supplies oil to the pressure regulating valve group (6);

the adjusting hydraulic cylinder (22) is used for controlling the flow of the electric proportional pump (21);

the three-position four-way electromagnetic proportional valve (23) is used for controlling and adjusting the position of a piston rod of the hydraulic cylinder (22);

a hydraulic cylinder position feedback sensor (24) for detecting the position of the piston rod of the adjusting hydraulic cylinder (22);

the first oil suction filter (3) is used for filtering oil sucked by the oil source valve group (2) from the oil tank (1);

the first motor (4) is connected with the oil source valve group (2) through a coupler, and drives the electric proportional variable pump (21) to rotate;

an accumulator (5) to provide a large instantaneous flow rate at dynamic loading;

the pressure regulating valve group (6) is used for regulating the pressure of the system;

a static load hydraulic cylinder (7) for applying a static load;

the static load hydraulic cylinder control valve group (8) is used for supplying oil to the static load hydraulic cylinder (7) so as to control the motion direction of a piston rod of the static load hydraulic cylinder (7);

a dynamic load hydraulic cylinder (9) for applying a dynamic load;

the dynamic load hydraulic cylinder control valve group (10) is used for supplying oil to the dynamic load hydraulic cylinder (9) so as to control the movement direction of a piston rod of the dynamic load hydraulic cylinder (9);

the control oil valve bank (11) is used for supplying oil to the oil source valve bank (2);

a first hydraulic pump (12), wherein the first hydraulic pump (12) sucks oil from the oil tank (1) through rotation and supplies oil to the control oil valve group (11);

the second motor (13) is connected with the first hydraulic pump (12) through a coupling and drives the first hydraulic pump (12) to rotate;

a first displacement sensor (14) for measuring the movement speed of the piston rod of the static hydraulic cylinder (7);

the first force sensor (15) is used for measuring the force borne by the piston rod of the static hydraulic cylinder (7) during movement;

the second displacement sensor (16) is used for measuring the movement speed of a piston rod of the dynamic load hydraulic cylinder (9);

the second force sensor (17) is used for measuring the force borne by the piston rod of the dynamic load hydraulic cylinder (9) during movement;

a cooler (18) for cooling the oil in the oil tank (1);

a first pressurized oil filter (19) for supplying oil to the cooler (18);

a relief valve (20) to prevent overloading of the system;

a second hydraulic pump (21), wherein the second hydraulic pump (21) sucks oil from the oil tank (1) through rotation and supplies oil to the first oil filter (19) and the overflow pressure reducing valve (20);

a second oil suction filter (22) for filtering the oil sucked by the second hydraulic pump (21) from the oil tank (1);

the third motor (23) is connected with the second hydraulic pump (21) through a coupler, and drives the second hydraulic pump (21) to rotate;

a first shut-off valve (24) for controlling the opening and closing of the oil passage;

a second stop valve (25) for controlling the opening and closing of the tank (1);

a first check valve (32) for pressure differential protection, which is configured to communicate through the first check valve (32) when the cooler (18) is blocked.

2. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, further comprising:

the heater (26), the said heater (26) is fixedly mounted inside the said oil tank (1), in order to guarantee the oil liquid in the said oil tank (1) does not condense;

an air filter (27), wherein the air filter (27) is fixedly arranged at the upper part of the oil tank (1) and is used for preventing particle pollutants from entering a system through the oil tank (1);

the liquid level relay (28) is used for controlling the height of oil in the oil tank (1);

a temperature transmitter (29) for measuring the temperature of the oil in the tank (1);

the liquid level meter (30) is fixedly arranged on the side surface of the oil tank (1) and used for measuring the height of oil in the oil tank (1);

a first pressure sensor (31) for measuring a pressure value at an oil outlet of said second hydraulic pump (21).

3. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, wherein an oil inlet P of the first oil absorption filter (3), an oil return port T of the oil source valve group (2), an oil suction port S of the first hydraulic pump (12), an oil return port T of the control oil valve group (11), an oil return port T of the pressure regulating valve group (6), an oil drainage port L of the pressure regulating valve group (6), an oil return port T of the static hydraulic cylinder control valve group (8), an oil drainage port L of the static hydraulic cylinder control valve group (8), an oil inlet P of the second oil absorption filter (22), an oil drainage port L of the overflow reducing valve (20), an oil outlet A of the cooler (18) and an oil outlet A of the first check valve (32) are connected with the oil tank (1) through hydraulic pipelines; an output shaft of the first motor (4) is connected with an input shaft of the oil source valve bank (2) through a coupler, and an oil outlet A of the first oil suction filter (3) is connected with an oil suction port S of the oil source valve bank (2) through a hydraulic pipeline; the output shaft of the second motor (13) is connected with the input shaft of the first hydraulic pump (12) through a coupling; an oil outlet A of the first hydraulic pump (12) is connected with an oil inlet P of the control valve group (11) through a hydraulic pipeline; an oil inlet P of an oil source valve group (2) is connected with an oil outlet A of a control oil valve group (11) through a hydraulic pipeline, an oil outlet A of an oil source valve group (12) is connected with an oil inlet P of a pressure regulating valve group (6) through a hydraulic pipeline, an oil outlet B of the pressure regulating valve group (6) is connected with an oil inlet P of an energy accumulator (5) through a hydraulic pipeline, an oil outlet A of the pressure regulating valve group (6) is connected with an oil inlet P of a static load hydraulic cylinder control valve group (8) and an oil inlet P of a dynamic load hydraulic cylinder control valve group (10) through hydraulic pipelines, an oil outlet A of the static load hydraulic cylinder control valve group (8) is connected with an oil inlet of a left rod cavity of a static load hydraulic cylinder (7) through a hydraulic pipeline, and an oil outlet B of the static load hydraulic cylinder control valve group (8) is connected with an oil inlet P of a right rod cavity of the static load hydraulic cylinder (7) through a hydraulic pipeline; an oil outlet A of the dynamic hydraulic cylinder control valve group (10) is connected with an oil inlet of a left rod cavity of the dynamic hydraulic cylinder (9) through a hydraulic pipeline, and an oil outlet B of the dynamic hydraulic cylinder control valve group (10) is connected with an oil inlet of a right rod cavity of the dynamic hydraulic cylinder (9) through a hydraulic pipeline; an oil return port T of the static load hydraulic cylinder control valve group (8), an oil return port T of the dynamic load hydraulic cylinder control valve group (10) and an oil return port T of the pressure regulating valve group (6) are connected through hydraulic pipelines; an oil drainage port L of the static load hydraulic cylinder control valve group (8), an oil drainage port L of the dynamic load hydraulic cylinder control valve group (10) and an oil drainage port L of the pressure regulating valve group are connected through hydraulic pipelines.

4. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, characterized in that an oil outlet A of a second oil suction filter (22) is connected with an oil inlet P of a first cut-off valve (24) through a hydraulic pipeline, an oil outlet A of the first cut-off valve (24) is connected with an oil suction port S of a second hydraulic pump (21) through a hydraulic pipeline, an output shaft of a third motor (23) is connected with an input shaft of the second hydraulic pump (21) through a coupler, an oil outlet A of the second hydraulic pump (21) is connected with an oil inlet P of a first hydraulic oil filter (19), an oil inlet P of an overflow reducing valve (20) and an oil inlet P of a first pressure sensor (31) through a hydraulic pipeline, an oil outlet A of the first hydraulic oil filter (19) is connected with an oil inlet P of a first one-way valve (32) and an oil inlet P of a cooler (18) through hydraulic pipelines, the oil outlet of the first one-way valve (32) is connected with the oil outlet A of the cooler (18) through a hydraulic pipeline.

5. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, characterized in that an oil inlet P of the electric proportional variable pump (21) is connected with an oil suction port S of the oil source valve group (2) through an internal flow passage of the oil source valve group (2), an oil outlet L of the electric proportional variable pump (21) is connected with an oil outlet A of the oil source valve group (2) through an internal flow passage of the oil source valve group (2), an oil drainage port L of the electric proportional variable pump (21) is connected with an oil return port T of the oil source valve group (2) through an internal flow passage of the oil source valve group (2), an oil inlet of the three-position four-way electromagnetic proportional valve (23) is connected with an oil inlet P of the oil source valve group (2) through an internal flow passage of the oil source valve group (2), an oil return port T of the three-position four-way electromagnetic proportional valve (23) is connected with an oil return port T of the oil source valve group (2) through an internal flow passage of the oil source valve group (2), an outlet A of the three-position four-way electromagnetic proportional valve (23) is connected with an oil inlet P1 of the adjusting hydraulic cylinder (22) through an internal flow channel of the oil source valve group (2), and an oil outlet B of the three-position four-way electromagnetic proportional valve is connected with an oil inlet P2 of the adjusting hydraulic cylinder (22) through an internal flow channel of the oil source valve group (2).

6. The dynamic and static loading comprehensive electro-hydraulic system of the shock-absorbing damper as claimed in claim 1, wherein the control valve group (11) comprises:

the second oil pressing filter (111) is used for filtering oil sucked by the control oil valve group (11);

a first two-position two-way solenoid valve (112) for controlling the flow direction of the oil;

the second pressure sensor (113) is used for measuring the pressure of an oil inlet of the control valve group (11);

a relief valve (114) for ensuring that the pressure of the control valve group (11) does not exceed a prescribed range;

an oil inlet P of a second pressure oil filter (111) is connected with an oil inlet P of a control oil valve group (11) through an internal flow channel of the control oil valve group (11), an oil outlet A of the second pressure oil filter (111), an oil inlet P of a first two-position two-way electromagnetic valve (112), an oil inlet P of a second pressure sensor (113) and an oil inlet P of an overflow valve (114) are connected through the internal flow channel of the control oil valve group (11), an oil outlet A of the first two-position two-way electromagnetic valve (112) is connected with the oil outlet A of the control oil valve group (11) through the internal flow channel of the control oil valve group (11), and an oil outlet B of the first two-position two-way electromagnetic valve (112), an oil outlet A of the overflow valve (114) and an oil return port T of the control oil valve group (11) are connected through the internal flow channel of the control oil valve group (11).

7. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, wherein the pressure regulating valve group (6) comprises:

the third pressure sensor (61) is used for measuring the pressure of an oil inlet of the pressure regulating valve group (6);

a second check valve (62) for preventing the oil from flowing back into the oil source valve group (2);

the third pressure oil filter (63) is used for filtering oil sucked by the pressure regulating valve group (6);

an unloading pressure reducing valve (64) for automatically controlling unloading or loading of the pump;

the second two-position two-way electromagnetic valve (65) is used for controlling the working state of the unloading pressure reducing valve (64);

a proportional relief valve (66) to control system pressure to prevent system overload;

an oil inlet P of a third pressure sensor (61), an oil inlet P of a second one-way valve (62) and an oil inlet P of a pressure regulating valve group (6) are connected through an internal flow channel of the pressure regulating valve group (6), an oil outlet A of the second one-way valve (62) is connected with an oil inlet P of a third pressure oil filter (63) through an internal flow channel of the pressure regulating valve group (6), an oil outlet A of the third pressure oil filter (63), an oil outlet B of the pressure regulating valve group (6), an oil outlet A of the pressure regulating valve group (6), an oil inlet P of an unloading reducing valve (64) and an oil inlet P of a proportional overflow valve (66) are connected through an internal flow channel of the pressure regulating valve group (6), an oil outlet A of the unloading reducing valve (64) is connected with an oil inlet P of a second two-position two-way electromagnetic valve (65) through an internal flow channel of the pressure regulating valve group (6), an oil return port T of the unloading reducing valve (64), an oil return port L of the unloading reducing valve (64), The oil return port T of the second two-position two-way solenoid valve (65), the oil return port T of the proportional overflow valve (66) and the oil return port T of the pressure regulating valve group (6) are connected through an internal flow channel of the pressure regulating valve group (6), and the oil drainage port L of the proportional overflow valve (66) is connected with the oil drainage port L of the pressure regulating valve group (6) through an internal flow channel of the pressure regulating valve group (6).

8. The dynamic and static loading comprehensive electro-hydraulic system of the shock absorption damper as claimed in claim 1, wherein the static loading hydraulic cylinder control valve group (8) comprises:

the fourth pressure sensor (81) is used for measuring the pressure of an oil inlet of the control valve group (8) of the static hydraulic cylinder;

the first three-position four-way servo valve (82) is used for controlling the motion direction of a piston rod of the static hydraulic cylinder (7);

a fifth pressure sensor (83) for measuring the pressure of the oil inlet of the first cartridge valve (84) and the oil inlet of the first control cover plate reversing valve (85)

The first cartridge valve (84) is used for controlling the flow of oil flowing into a left rod cavity of the static hydraulic cylinder (7);

a first control cover plate reversing valve (85) used for controlling the working state of the first cartridge valve (84);

a sixth pressure sensor (86) for measuring the pressure in the left rod cavity of the static hydraulic cylinder (7);

a seventh pressure sensor (87) for measuring the pressure in the right rod cavity of the static hydraulic cylinder (7);

a second control cover plate reversing valve (88) used for controlling the working state of the second cartridge valve (89);

the second cartridge valve (89) is used for controlling the flow of oil flowing into the right rod cavity of the static hydraulic cylinder (7);

the eighth pressure sensor (8a) is used for measuring the pressure of the oil inlet of the second cartridge valve (89) and the pressure of the oil inlet of the second control cover plate reversing valve (88);

the ninth pressure sensor (8b) is used for measuring the pressure of an oil return opening of the static hydraulic cylinder control valve group (8);

an oil inlet P of a first three-position four-way servo valve (82), an oil inlet M of a fourth pressure sensor (81) and an oil inlet P of a static hydraulic cylinder control valve group (8) are connected through an internal flow channel of the static hydraulic cylinder control valve group (8), an oil return port T of the first three-position four-way servo valve (82), an oil return port M of a ninth pressure sensor (8B) and the oil return port T of the static hydraulic cylinder control valve group (8) are connected through the internal flow channel of the static hydraulic cylinder control valve group (8), an oil outlet A of the first three-position four-way servo valve (82), an oil inlet M of a fifth pressure sensor (83), an oil inlet A of a first cartridge valve (84) and an oil inlet X of a first control cover plate reversing valve (85) are connected through the internal flow channel of the static hydraulic cylinder control valve group (8), an oil outlet B of the first three-position four-way servo valve (82), an oil inlet M of an eighth pressure sensor (8a), an oil return port M of the eighth pressure sensor (8a), An oil inlet A of the second cartridge valve (89) is connected with an oil inlet X of the second control cover plate reversing valve (88) through an internal flow channel of the static hydraulic cylinder control valve group (8), an oil return port T of the first control cover plate reversing valve (85), an oil outlet B of the first cartridge valve (84), an oil inlet P of the sixth pressure sensor (86) is connected with an oil outlet A of the static hydraulic cylinder control valve group (8) through an internal flow channel of the static hydraulic cylinder control valve group (8), an oil return port T of the second control cover plate reversing valve (88), an oil outlet B of the second cartridge valve (89), an oil inlet M of the seventh pressure sensor (87) and an oil outlet B of the static hydraulic cylinder control valve group (8) are connected through an internal flow channel of the static hydraulic cylinder control valve group (8).

9. The dynamic and static loading comprehensive electro-hydraulic system of the shock-absorbing damper as claimed in claim 1, wherein the dynamic hydraulic cylinder control valve group (10) comprises:

the second three-position four-way servo valve (101) is used for controlling the motion direction of a piston rod of the dynamic hydraulic cylinder (9);

the tenth pressure sensor (102) is used for measuring the pressure of an oil inlet of the control valve group (10) of the dynamic hydraulic cylinder;

the eleventh pressure sensor (103) is used for measuring the pressure of the left rod cavity of the dynamic load hydraulic cylinder (9);

a twelfth pressure sensor (104) for measuring the pressure of the right rod cavity of the dynamic hydraulic cylinder (9);

the thirteenth pressure sensor (105) is used for measuring the pressure of an oil outlet of the control valve group (10) of the dynamic hydraulic cylinder;

an oil inlet P of a second three-position four-way servo valve (101), an oil inlet M of a tenth pressure sensor (102) and an oil inlet P of a dynamic load hydraulic cylinder control valve group (10) are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group (10), an oil outlet A of the second three-position four-way servo valve (101), an oil inlet M of an eleventh pressure sensor (103) and an oil outlet A of the dynamic load hydraulic cylinder control valve group (10) are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group (10), an oil outlet B of the second three-position four-way servo valve (101), an oil inlet M of a twelfth pressure sensor (104) and an oil outlet B of the dynamic load hydraulic cylinder control valve group (10) are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group (10), an oil return port T of the second three-position four-way servo valve (101), an oil inlet M of the thirteenth pressure sensor (105) and an oil return port T of the dynamic load hydraulic cylinder control valve group (10) are connected through an internal flow channel of the dynamic load hydraulic cylinder control valve group (10) The oil drainage port L of the second three-position four-way servo valve (101) is connected with the oil drainage port L of the dynamic load hydraulic cylinder control valve group (10) through an internal flow passage of the dynamic load hydraulic cylinder control valve group (10).

10. A control method of a dynamic and static loading comprehensive electro-hydraulic system of a shock absorption damper is characterized by comprising the following steps:

wherein I is the input current value of the electric proportional variable pump, v is the loading speed of the static load hydraulic cylinder, A is the effective area of the static load hydraulic cylinder, and Q_maxMaximum flow rate of the electric proportional variable pump, I_maxThe maximum input current value of the electric proportional variable pump;