CN210859416U

CN210859416U - Hydraulic position and pressure closed-loop control dynamic and static simulation test system

Info

Publication number: CN210859416U
Application number: CN201920701806.1U
Authority: CN
Inventors: 丘铭军; 郭星良; 艾春璇; 张永锋; 陈国防; 彭立广; 雷丛卉
Original assignee: China National Heavy Machinery Research Institute Co Ltd
Current assignee: China National Heavy Machinery Research Institute Co Ltd
Priority date: 2019-05-16
Filing date: 2019-05-16
Publication date: 2020-06-26
Anticipated expiration: 2029-05-16

Abstract

The utility model discloses a hydraulic pressure position and pressure closed-loop control sound attitude analogue test system includes sound attitude analogue test valve device (18), experimental pneumatic cylinder (13), displacement sensor (14), connecting rod (15), loading pneumatic cylinder (16) and loading valve device (17) at least, connecting rod (15) both ends are connected with experimental pneumatic cylinder (13) and loading pneumatic cylinder (16) respectively, and wherein displacement sensor (14) are installed to experimental pneumatic cylinder (13) other end, the pole chamber of loading pneumatic cylinder (16) is connected with the hydraulic fluid port B of loading valve device (17), and wherein the stopper chamber of loading pneumatic cylinder (16) is connected with the hydraulic fluid port A of loading valve device (17), sound attitude analogue test valve device is connected in experimental pneumatic cylinder (13).

Description

Hydraulic position and pressure closed-loop control dynamic and static simulation test system

Technical Field

The invention belongs to the technical field of hydraulic control test systems, and particularly relates to a dynamic and static simulation test system for hydraulic position and pressure closed-loop control.

Background

In the field of steel making, with the wide demand of the market for casting blanks, the specification of the poured casting blank is thicker and thicker, so that the center porosity and segregation of the casting blank are more and more serious, and the internal quality of the casting blank is greatly influenced.

The soft reduction technology, which is the most effective method for eliminating the above defects, is also widely applied to the continuous casting technology, and the position or pressure of a hydraulic cylinder needs to be accurately controlled in the soft reduction process so as to implement the soft reduction function on a casting blank, but the continuous casting blank is molded at high temperature, so that the actual working condition needs to be accurately simulated before the parameters of a soft reduction hydraulic control system are designed, a reliable basis is provided for the design, the design errors are reduced, the design efficiency is improved, and the safety production accidents caused by improper parameter design of the hydraulic position and pressure closed-loop control system are avoided, but the prior art has no pre-parameter simulation experiment on the soft reduction hydraulic control system and no related parameters, so that the prior soft reduction technology cannot obtain accurate parameters due to no simulation experiment, safety production accidents are easily caused, and resources are easily wasted, and the cost is high, so that the development of a hydraulic position and pressure closed-loop control dynamic and static simulation test system and method is necessary.

Disclosure of Invention

The invention aims to overcome the defects of the prior art, provides a hydraulic position and pressure closed-loop control dynamic and static simulation test system, and overcomes the defects that in the prior art, the pressure of a hydraulic position and pressure closed-loop control dynamic and static simulation test system is 1: the prior art does not relate to a pre-parameter simulation experiment of a hydraulic control system under light pressure, and does not have related parameters; 2: in the prior art, the soft reduction technology cannot obtain accurate parameters without a simulation experiment, so that safety production accidents are easily caused; 3: in the prior art, the soft reduction technology has the problems that accurate parameters cannot be obtained without a simulation experiment, so that resource waste is easily caused, the cost is high and the like.

In order to solve the technical problem, the technical scheme of the invention is as follows: the utility model provides a hydraulic pressure position and pressure closed-loop control sound attitude analogue test system, includes sound attitude analogue test valve device, experimental pneumatic cylinder, displacement sensor, connecting rod, loading pneumatic cylinder and loading valve device at least, the connecting rod both ends are connected with experimental pneumatic cylinder and loading pneumatic cylinder respectively, and wherein displacement sensor is installed to the experimental pneumatic cylinder other end, the pole chamber of loading pneumatic cylinder is connected with loading valve device's hydraulic fluid port B, and wherein loading pneumatic cylinder's stopper chamber is connected with loading valve device's hydraulic fluid port A, dynamic attitude analogue test valve device is connected to experimental pneumatic cylinder.

Preferably, the dynamic and static simulation test valve device comprises a servo valve, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a quick stop valve, a first electromagnetic ball seat valve, a second electromagnetic ball seat valve, a first normally closed logic valve, a second normally closed logic valve, a third normally closed logic valve, a fourth normally closed logic valve, a fifth normally closed logic valve, a sixth normally closed logic valve, a first externally controlled leakage hydraulic control one-way valve, a second externally controlled leakage hydraulic control one-way valve, a first hydraulic control one-way valve, a second hydraulic control one-way valve, a first adjustable restrictor, a second adjustable restrictor, a first overflow valve, a second overflow valve, a first one-way valve, a second one-way valve, a first pressure sensor and a second pressure sensor;

the hydraulic loop of the plug cavity of the test hydraulic cylinder is respectively connected with an oil port P of a first overflow valve, an oil port B of a first one-way valve, an oil port B of a fifth normally closed logic valve, an oil port B of a second normally closed logic valve and an oil port B of a third normally closed logic valve, wherein the oil port T of the first overflow valve, the oil port A of the first one-way valve and the oil port A of the fifth normally closed logic valve are respectively connected with an oil return port T0 from a hydraulic station, a loop between the hydraulic loop of the plug cavity of the test hydraulic cylinder and the first overflow valve and the first one-way valve is connected with a second pressure sensor, the oil port A of the second normally closed logic valve is connected with the oil port B of a servo valve, the oil port A of the third normally closed logic valve is connected with a second adjustable hydraulic control valve, the oil port B of the first one-way valve is respectively connected with the oil port B of a hydraulic control one-way valve of a second external control leakage one-way valve, the oil port B, the oil port A of the second external control leakage hydraulic control one-way valve is connected with the oil port B of the quick stop valve, the oil port A of the first hydraulic control one-way valve is connected with the oil port A of the second electromagnetic ball seat valve, and the oil port A of the second hydraulic control one-way valve is connected with the oil port B of the third electromagnetic valve; the rod cavity hydraulic circuit of the test hydraulic cylinder is respectively connected with an oil port P of a second overflow valve, an oil port B of a second one-way valve, an oil port B of a sixth normally-closed logic valve, an oil port B of a first normally-closed logic valve and an oil port B of a fourth normally-closed logic valve, wherein an oil port T of the second overflow valve, an oil port A of the second one-way valve and an oil port A of the sixth normally-closed logic valve are respectively connected with an oil return port T0 from a hydraulic station, a first pressure sensor is connected on a loop between the rod cavity hydraulic circuit of the test hydraulic cylinder and the second overflow valve and the second one-way valve, an oil port A of a first restrictor normally-closed logic valve is connected with an oil port A of a servo valve, an oil port A of the fourth normally-closed logic valve is connected with a first adjustable hydraulic control one-way valve, a first adjustable hydraulic control oil port B of the first hydraulic control one-way valve and an oil port B of the second hydraulic control one-, the hydraulic control check valve comprises a first external control external leakage hydraulic control check valve, a second external control external leakage hydraulic control check valve, a third electromagnetic ball seat valve, a third electromagnetic valve, a fourth electromagnetic valve, a;

the oil port A of the first electromagnetic valve is respectively connected with the control oil ports X of the third normally-closed logic valve and the fourth normally-closed logic valve, and the oil port B of the first electromagnetic valve is respectively connected with the control oil ports X of the first normally-closed logic valve and the second normally-closed logic valve;

an oil port A of the second electromagnetic valve is respectively connected with control oil ports X of a fifth normally closed logic valve and a sixth normally closed logic valve, an oil port B of the second electromagnetic valve is respectively connected with control oil ports X of a first external control leakage hydraulic control one-way valve and a second external control leakage hydraulic control one-way valve, and oil drainage ports Y of the first external control leakage hydraulic control one-way valve and the second external control leakage hydraulic control one-way valve are respectively connected with an oil return port T0 from a hydraulic station;

the oil port A of the third electromagnetic valve is respectively connected with the control oil port X of the second normally-closed logic valve and the control oil port X of the fourth normally-closed logic valve, and the oil port B of the third electromagnetic valve is respectively connected with the control oil port X of the first normally-closed logic valve and the control oil port X of the second normally-closed logic valve;

the pressure oil port P0 from the hydraulic station is respectively connected with oil ports P of a servo valve, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a quick stop valve, a first electromagnetic ball seat valve and a second electromagnetic ball seat valve; and an oil return port T0 from the hydraulic station is respectively connected with oil ports T of a servo valve, a first electromagnetic valve, a second electromagnetic valve, a third electromagnetic valve, a quick stop valve, a first electromagnetic ball seat valve and a second electromagnetic ball seat valve.

Preferably, the test hydraulic cylinder is connected with the dynamic and static simulation test valve device through a high-pressure rubber pipe, wherein the high-pressure rubber pipe comprises a first high-pressure rubber pipe and a second high-pressure rubber pipe;

one end of the first high-pressure rubber pipe is connected with a rod cavity of the test hydraulic cylinder, and the other end of the first high-pressure rubber pipe is connected with the servo valve, the first electromagnetic valve, the third electromagnetic valve, the quick stop valve, the first electromagnetic ball seat valve, the first normally closed logic valve, the fourth normally closed logic valve, the sixth normally closed logic valve, the first externally-controlled externally-leaking hydraulic control one-way valve, the first hydraulic control one-way valve, the second hydraulic control one-way valve, the first adjustable throttler, the second overflow valve, the second one-way valve and the first pressure sensor respectively;

one end of the second high-pressure rubber pipe is connected with a plug cavity of the test hydraulic cylinder, and the other end of the second high-pressure rubber pipe is connected with the servo valve, the first electromagnetic valve, the second electromagnetic valve, the third electromagnetic valve, the quick stop valve, the second electromagnetic ball seat valve, the second normally closed logic valve, the third normally closed logic valve, the fifth normally closed logic valve, the second externally-controlled leakage hydraulic control one-way valve, the first hydraulic control one-way valve, the second adjustable throttler, the first overflow valve, the first one-way valve and the second pressure sensor respectively.

Preferably, the quick shut-off valve is integrated by four independent shut-off valves.

Preferably, the connecting rod is a connecting rod with spherical hinge bearings at two ends and is used for connecting the test hydraulic cylinder and the loading hydraulic cylinder.

Compared with the prior art, the invention has the advantages that:

(1) the invention provides a dynamic and static simulation test system and a method for hydraulic position and pressure closed-loop control, which are particularly suitable for simulation tests for hydraulic position and pressure closed-loop control under light pressure in the field of continuous steel casting, are used for simulating the actual working condition under light pressure, provide basis for parameter design of hydraulic position and pressure closed-loop control, reduce design errors, improve design efficiency and avoid safety production accidents caused by the design errors;

(2) the hydraulic position and pressure closed-loop control dynamic and static characteristic simulation test system provided by the invention has the characteristics of high automation degree, accurate simulation working condition, safe and reliable operation, low cost and the like;

(3) according to the test method of the hydraulic position and pressure closed-loop control dynamic and static characteristic simulation test system, the servo valve, the quick stop valve, the first electromagnetic ball seat valve, the second electromagnetic ball seat valve and the third electromagnetic valve can independently realize closed-loop control over the hydraulic position and pressure of the test hydraulic cylinder, and the test method is particularly suitable for simulation tests of soft-reduction hydraulic position and pressure closed-loop control in steel making equipment.

Drawings

FIG. 1 is a schematic structural diagram of the present invention.

Description of reference numerals:

1-servo valve, 201-first solenoid valve, 202-second solenoid valve, 203-third solenoid valve, 3-quick stop valve, 401-first solenoid ball seat valve, 402-second solenoid ball seat valve, 501-first normally closed logic valve, 502-second normally closed logic valve, 503-third normally closed logic valve, 504-fourth normally closed logic valve, 505-fifth normally closed logic valve, 506-sixth normally closed logic valve, 601-first externally controlled bleed hydraulic control check valve, 602-second externally controlled bleed hydraulic control check valve, 701-first restrictor check valve, 702-second hydraulically controlled check valve, 801-first adjustable restrictor, 802-second adjustable, 901-first overflow valve, 902-second overflow valve, 1001-first check valve, 1002-second check valve, 1101-a first pressure sensor, 1102-a second pressure sensor, 1201-a first high-pressure rubber pipe, 1202-a second high-pressure rubber pipe, 13-a test hydraulic cylinder, 14-a displacement sensor, 15-a connecting rod, 16-a loading hydraulic cylinder, 17-a loading valve device and 18-a dynamic and static simulation test valve device.

Detailed Description

The following describes embodiments of the present invention with reference to examples:

it should be noted that the structures, proportions, sizes, and other embodiments disclosed herein are illustrative only and are not intended to limit the scope of the invention, which is defined by the claims, since the scope of the invention is not limited by the specific structures, proportions, and dimensions, or otherwise, unless otherwise specified, since various modifications, changes in the proportions and variations thereof, can be made by those skilled in the art without departing from the spirit and scope of the invention.

In addition, the terms "upper", "lower", "left", "right", "middle" and "one" used in the present specification are for clarity of description, and are not intended to limit the scope of the present invention, and the relative relationship between the terms and the terms is not to be construed as a scope of the present invention.

Example 1

As shown in fig. 1, the invention discloses a hydraulic position and pressure closed-loop control dynamic and static simulation test system, which at least comprises a dynamic and static simulation test valve device 18, a test hydraulic cylinder 13, a displacement sensor 14, a connecting rod 15, a loading hydraulic cylinder 16 and a loading valve device 17, wherein two ends of the connecting rod 15 are respectively connected with the test hydraulic cylinder 13 and the loading hydraulic cylinder 16, the other end of the test hydraulic cylinder 13 is provided with the displacement sensor 14, a rod cavity of the loading hydraulic cylinder 16 is connected with an oil port B of the loading valve device 17, a plug cavity of the loading hydraulic cylinder 16 is connected with an oil port a of the loading valve device 17, and the test hydraulic cylinder 13 is connected with the dynamic and static simulation test valve device.

Example 2

As shown in fig. 1, preferably, the dynamic-static simulation test valve device 18 includes a servo valve 1, a first electromagnetic valve 201, a second electromagnetic valve 202, a third electromagnetic valve 203, a quick stop valve 3, a first electromagnetic ball seat valve 401, a second electromagnetic ball seat valve 402, a first normally closed logic valve 501, a second normally closed logic valve 502, a third normally closed logic valve 503, a fourth normally closed logic valve 504, a fifth normally closed logic valve 505, a sixth normally closed logic valve 506, a first externally controlled externally-leaking liquid-controlled check valve 601, a second externally controlled externally-leaking liquid-controlled check valve 602, a first check valve 701, a second check valve 702, a first adjustable restrictor 801, a second adjustable restrictor 802, a first overflow valve 901, a second overflow valve 902, a first check valve 1001, a second check valve 1002, a first pressure sensor 1101, and a second pressure sensor 1102;

a cavity-plugging hydraulic circuit of the test hydraulic cylinder 13 is respectively connected with an oil port P of the first overflow valve 901, an oil port B of the first check valve 1001 and an oil port B of the fifth normally-closed logic valve 505, wherein an oil port T of the first overflow valve 901, an oil port a of the first check valve 1001 and an oil port a of the fifth normally-closed logic valve 505 are respectively connected with an oil return port T0 from a hydraulic station, and a second pressure sensor 1102 is connected on a circuit between the cavity-plugging hydraulic circuit of the test hydraulic cylinder 13 and the first overflow valve 901 and the first check valve 1001; the rod cavity hydraulic circuit of the test hydraulic cylinder 13 is respectively connected with an oil port P of the second overflow valve 902, an oil port B of the second check valve 1002 and an oil port B of the sixth normally-closed logic valve 506, wherein an oil port T of the second overflow valve 902, an oil port a of the second check valve 1002 and an oil port a of the sixth normally-closed logic valve 506 are respectively connected with an oil return port T0 from a hydraulic station, and a first pressure sensor 1101 is connected on the circuit between the rod cavity hydraulic circuit of the test hydraulic cylinder 13 and the second overflow valve 902 and the second check valve 1002;

the hydraulic circuit of the plug cavity of the test hydraulic cylinder 13 is connected with the oil port B of the second normally-closed logic valve 502, the oil port A of the second normally-closed logic valve 502 is connected with the oil port B of the servo valve 1, the hydraulic circuit of the rod cavity of the test hydraulic cylinder 13 is connected with the oil port B of the first normally-closed logic valve 501, and the oil port A of the first normally-closed logic valve 501 is connected with the oil port A of the servo valve 1;

the cavity-plugging hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a third normally closed logic valve 503, wherein an oil port a of the third normally closed logic valve 503 is connected with a second adjustable choke 802, the second adjustable choke 802 is connected with an oil port B of a second external control leakage hydraulic control one-way valve 602, and the oil port a of the second external control leakage hydraulic control one-way valve 602 is connected with the oil port B of the quick stop valve 3; a rod cavity hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a fourth normally closed logic valve 504, wherein an oil port A of the fourth normally closed logic valve 504 is connected with a first adjustable throttler 801, the first adjustable throttler 801 is connected with an oil port B of a first external control leakage hydraulic control one-way valve 601, and the oil port A of the first external control leakage hydraulic control one-way valve 601 is connected with an oil port A of the quick stop valve 3;

the cavity-plugging hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a third normally-closed logic valve 503, wherein an oil port a of the third normally-closed logic valve 503 is connected with a second adjustable choke 802, the second adjustable choke 802 is connected with an oil port B of a first hydraulic control one-way valve 701, and an oil port a of the first hydraulic control one-way valve 701 is connected with an oil port a of a second electromagnetic ball seat valve 402; a rod cavity hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a fourth normally closed logic valve 504, wherein an oil port a of the fourth normally closed logic valve 504 is connected with a first adjustable choke 801, the first adjustable choke 801 is connected with an oil port B of a first hydraulic control one-way valve 701, and an oil port a of the first hydraulic control one-way valve 701 is connected with an oil port a of a first electromagnetic ball seat valve 401;

the cavity-plugging hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a third normally-closed logic valve 503, wherein an oil port a of the third normally-closed logic valve 503 is connected with a second adjustable choke 802, the second adjustable choke 802 is connected with an oil port B of a second hydraulic check valve 702, and the oil port a of the second hydraulic check valve 702 is connected with an oil port B of a third electromagnetic valve 203; a rod cavity hydraulic circuit of the test hydraulic cylinder 13 is connected with an oil port B of a fourth normally-closed logic valve 504, wherein an oil port A of the fourth normally-closed logic valve 504 is connected with a first adjustable choke 801, the first adjustable choke 801 is connected with an oil port B of a second hydraulic check valve 702, and an oil port A of the second hydraulic check valve 702 is connected with an oil port A of a third electromagnetic valve 203;

the oil port a of the first electromagnetic valve 201 is connected with the control oil ports X of the third normally closed logic valve 503 and the fourth normally closed logic valve 504, and the oil port B of the first electromagnetic valve 201 is connected with the control oil ports X of the first normally closed logic valve 501 and the second normally closed logic valve 502;

an oil port a of the second electromagnetic valve 202 is connected with control oil ports X of the fifth normally closed logic valve 505 and the sixth normally closed logic valve 506 respectively, an oil port B of the second electromagnetic valve 202 is connected with control oil ports X of the first external control external leakage hydraulic control one-way valve 601 and the second external control external leakage hydraulic control one-way valve 602 respectively, wherein oil drain ports Y of the first external control external leakage hydraulic control one-way valve 601 and the second external control external leakage hydraulic control one-way valve 602 are connected with an oil return port T0 from the hydraulic station respectively;

an oil port A of the third electromagnetic valve 203 is respectively connected with a control oil port X of the second normally-closed logic valve 501 and a control oil port X of the fourth normally-closed logic valve 504, and an oil port B of the third electromagnetic valve 203 is respectively connected with a control oil port X of the first normally-closed logic valve 503 and a control oil port X of the second normally-closed logic valve 502;

the pressure oil port P0 from the hydraulic station is respectively connected with the oil ports P of the servo valve 1, the first electromagnetic valve 201, the second electromagnetic valve 202, the third electromagnetic valve 203, the quick stop valve 3, the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402; an oil return port T0 from the hydraulic station is respectively connected with oil ports T of the servo valve 1, the first electromagnetic valve 201, the second electromagnetic valve 202, the third electromagnetic valve 203, the quick stop valve 3, the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402.

As shown in fig. 1, preferably, the test hydraulic cylinder 13 is connected with the dynamic and static simulation test valve device through a high-pressure hose, wherein the high-pressure hose includes a first high-pressure hose 1201 and a second high-pressure hose 1202;

one end of the first high-pressure rubber hose 1201 is connected with a rod cavity of the test hydraulic cylinder 13, and the other end of the first high-pressure rubber hose 1201 is connected with the servo valve 1, the first electromagnetic valve 201, the third electromagnetic valve 203, the quick stop valve 3, the first electromagnetic ball seat valve 401, the first normally closed logic valve 501, the fourth normally closed logic valve 504, the sixth normally closed logic valve 506, the first externally controlled leakage hydraulic control one-way valve 601, the first hydraulic control one-way valve 701, the second hydraulic control one-way valve 702, the first adjustable restrictor 801, the second overflow valve 902, the second one-way valve 1002 and the first pressure sensor 1101 respectively;

one end of the second high-pressure rubber hose 1202 is connected with a plug cavity of the test hydraulic cylinder 13, and the other end of the second high-pressure rubber hose 1202 is connected with the servo valve 1, the first electromagnetic valve 201, the second electromagnetic valve 202, the third electromagnetic valve 203, the quick stop valve 3, the second electromagnetic ball seat valve 402, the second normally closed logic valve 502, the third normally closed logic valve 503, the fifth normally closed logic valve 505, the second external control leakage hydraulic control one-way valve 602, the first hydraulic control one-way valve 701, the second hydraulic control one-way valve 702, the second adjustable restrictor 802, the first overflow valve 901, the first one-way valve 1001 and the second pressure sensor 1102 respectively.

Example 3

Preferably, the quick shut-off valve 3 is integrated by four independent shut-off valves.

Preferably, the connecting rod 15 is a connecting rod with spherical hinge bearings at two ends and is used for connecting the test hydraulic cylinder 13 and the loading hydraulic cylinder 16.

Example 4

Preferably, in the test method of the dynamic and static simulation test system for closed-loop control of hydraulic position and pressure as described in any one of the above, the loading valve device 17 is used for simulating a load on the loading hydraulic cylinder 16, the loading hydraulic cylinder 16 is connected to the test hydraulic cylinder 13 through the connecting rod 15, wherein the test hydraulic cylinder 13 controls the simulated load through the dynamic and static simulation test valve device 18, and the hydraulic position control of the test hydraulic cylinder 13 automatically controls the servo valve 1 in real time by detecting the value of the displacement sensor 14, so as to realize the hydraulic position control of the test hydraulic cylinder 13 by the servo valve 1; the closed-loop control of the pressure of the test hydraulic cylinder 13 can be realized by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102 to control the servo valve 1 in real time, so that the closed-loop control of the pressure of the test hydraulic cylinder 13 by the servo valve 1 is realized.

Preferably, the hydraulic position control of the test hydraulic cylinder 13 automatically controls the quick stop valve 3 in real time by detecting the numerical value of the displacement sensor 14, and simultaneously, the hydraulic position control of the test hydraulic cylinder 13 by the quick stop valve 3 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802; the pressure closed-loop control of the test hydraulic cylinder 13 can control the quick stop valve 3 in real time by detecting the numerical values of the first pressure sensor 1101 and the second pressure sensor 1102, so that the pressure closed-loop control of the quick stop valve 3 on the test hydraulic cylinder 13 is realized.

Preferably, the hydraulic position control of the test hydraulic cylinder 13 can automatically control the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 in real time by detecting the numerical value of the displacement sensor 14, and simultaneously, the hydraulic position control of the test hydraulic cylinder 13 by the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802; the closed-loop control of the pressure of the test hydraulic cylinder 13 can control the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 in real time by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102, so that the closed-loop control of the pressure of the test hydraulic cylinder 13 by the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 is realized.

Preferably, the hydraulic position control of the test hydraulic cylinder 13 can automatically control the third electromagnetic valve 203 in real time by detecting the numerical value of the displacement sensor 14, and simultaneously, the hydraulic position control of the test hydraulic cylinder 13 by the third electromagnetic valve 203 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802; the pressure closed-loop control of the test hydraulic cylinder 13 can control the third electromagnetic valve 203 in real time by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102, so that the pressure closed-loop control of the test hydraulic cylinder 13 by the third electromagnetic valve 203 is realized.

Preferably, when all the hydraulic components are installed far away from the test hydraulic cylinder 13, a high-pressure rubber pipe needs to be configured; when all the hydraulic components are directly arranged on the test hydraulic cylinder 13, a high-pressure rubber tube does not need to be configured.

The servo valve 1 is a servo valve or a high-performance proportional valve, and the servo valve 1 is automatically controlled to realize closed-loop control of the hydraulic position and the pressure of the test hydraulic cylinder 13 by detecting the numerical value of the displacement sensor 14 of the test hydraulic cylinder 13 in real time.

The first electromagnetic valve 201 is used for controlling the on-off of a first normally closed logic valve 501, a second normally closed logic valve 502, a third normally closed logic valve 503 and a fourth normally closed logic valve 504; the second electromagnetic valve 202 is used for controlling the on-off of a fifth normally-closed logic valve 505, a sixth normally-closed logic valve 506, a first externally-controlled leakage hydraulic control one-way valve 601 and a second externally-controlled leakage hydraulic control one-way valve 602; by detecting the value of the displacement sensor 14 of the test hydraulic cylinder 13 in real time, the third electromagnetic valve 203 automatically controls the test hydraulic cylinder 13, and the hydraulic position and pressure closed-loop control of the test hydraulic cylinder 13 is realized.

The quick stop valve 3 is formed by integrally installing four independent non-leakage stop valves, an electromagnet a of the quick stop valve 3 is electrified, and an oil port P in the valve body is communicated with an oil port A; an electromagnet d of the quick stop valve 3 is electrified, and an oil port B in the valve body is communicated with an oil port T; an electromagnet c of the quick stop valve 3 is electrified, and an oil port P in the valve body is communicated with an oil port B; the electromagnet b of the quick stop valve 3 is electrified, and the oil port A inside the valve body is communicated with the oil port T. The position and pressure closed-loop control of the test hydraulic cylinder 13 is realized by automatically controlling the quick stop valve 3 through detecting the numerical value of the displacement sensor 14 of the test hydraulic cylinder 13 in real time, and the electromagnets a, b, c and d of the quick stop valve 3 are in a non-leakage stop state under the power-off state by relying on the acting force of a spring inside the valve body to realize the position holding function of the test hydraulic cylinder 13.

The first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 are light electromagnetic ball seat valves, and have high response speed and low driving power; the first electromagnetic ball seat valve 401 is used for controlling a rod cavity of the test hydraulic cylinder 13, and the second electromagnetic ball seat valve 402 is used for controlling a plug cavity of the test hydraulic cylinder 13; the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 are automatically controlled by detecting the value of the displacement sensor 14 of the test hydraulic cylinder 13 in real time to realize the closed-loop control of the hydraulic position and the pressure of the test hydraulic cylinder 13.

The third electromagnetic valve 203 is of a sliding valve structure, and the quick stop valve 3, the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 are of cone valve structures, so that the valve is insensitive to the cleanliness of oil, the working reliability of the system is improved, and the field work maintenance amount is reduced.

The first normally closed logic valve 501 is used for controlling the on-off of an oil path of an oil port A of the servo valve 1, and the second normally closed logic valve 502 is used for controlling the on-off of an oil path of an oil port B of the servo valve 1; the third normally-closed logic valve 503 is used for controlling the on-off of the oil passage of the plug cavity of the test hydraulic cylinder 13 by the quick stop valve 3, the second electromagnetic ball seat valve 402 and the third electromagnetic valve 203, and the fourth normally-closed logic valve 504 is used for controlling the on-off of the oil passage of the rod cavity of the test hydraulic cylinder 13 by the quick stop valve 3, the first electromagnetic ball seat valve 401 and the third electromagnetic valve 203; the fifth normally-closed logic valve 505 is used for controlling the loading and unloading of the plug cavity of the test hydraulic cylinder 13, and the sixth normally-closed logic valve 506 is used for controlling the loading and unloading of the rod cavity of the test hydraulic cylinder 13.

The first external control leakage hydraulic control check valve 601 and the second external control leakage hydraulic control check valve 602 are respectively used for controlling the on-off of the oil path a and the oil path B of the quick stop valve 3.

The first pilot check valve 701 is used for controlling the on-off of the oil passages a of the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402.

The second hydraulic check valve 702 is used to control the on/off of the oil passage A, B of the third electromagnetic valve 203.

The first adjustable restrictor 801 and the second adjustable restrictor 802 are used for controlling the speed of the test hydraulic cylinder 13, and the oil passing diameters of the first adjustable restrictor 801 and the second adjustable restrictor 802 are determined by the sizes of a piston rod and a piston cavity of the test hydraulic cylinder 13 and are generally obtained by calculation and tests so as to achieve the optimal control speed and control precision of the test hydraulic cylinder 13.

The first check valve 1001 is used for controlling oil supplement of a test hydraulic cylinder 13 plug cavity, and prevents the test hydraulic cylinder 13 plug cavity from being sucked to be empty to cause sealing damage; the second check valve 1002 is used for oil supplementing control of the rod cavity of the test hydraulic cylinder 13, and prevents the rod cavity of the test hydraulic cylinder 13 from being sucked to be empty, so that sealing damage is avoided.

The first overflow valve 901 is used for overpressure protection of the plug cavity of the test hydraulic cylinder 13, so that the seal damage caused by overlarge pressure of the plug cavity of the test hydraulic cylinder 13 is prevented; the second overflow valve 902 is used for overpressure protection of the rod cavity of the test hydraulic cylinder 13, and prevents the pressure of the rod cavity of the test hydraulic cylinder 13 from being too high, so that sealing damage is avoided.

The second pressure sensor 1102 is used for detecting the pressure of a plug cavity of the test hydraulic cylinder 13, and forms pressure closed-loop control with the first electromagnetic valve 201 and the oil port A of the servo valve 1; the first pressure sensor 1101 is used for detecting the pressure of the rod cavity of the test hydraulic cylinder 13, and forms pressure closed-loop control with the first electromagnetic valve 202 and the oil port B of the servo valve 1.

The test hydraulic cylinder 13 is a double-acting hydraulic cylinder and is used for testing various performances of a hydraulic position and a pressure closed-loop control system under soft pressure.

And the displacement sensor 14 is used for detecting the position of the test hydraulic cylinder 13.

The connecting rod 15 is a connecting rod with spherical hinge bearings at two ends and is used for connecting the test hydraulic cylinder 13 and the loading hydraulic cylinder 16.

And a plug cavity and a rod cavity of the loading hydraulic cylinder 16 are respectively connected with a loading valve device 17 and used for simulating the application of a soft pressing acting force.

The loading valve device 17 is a lightly pressed loading valve device, and the loading valve device 17 can realize the constant pressure control of a plug cavity or a rod cavity of the loading hydraulic cylinder 16 according to the test process requirements.

The testing working principle of the dynamic and static simulation test system for closed-loop control of hydraulic position and pressure of the simulation test under light pressure is as follows:

1) closed-loop control of the hydraulic position and pressure of the test hydraulic cylinder 13 by the servo valve 1

The electromagnet a of the first electromagnetic valve 201 is electrified, the first normally closed logic valve 501 and the second normally closed logic valve 502 are opened, the third normally closed logic valve 503 and the fourth normally closed logic valve 504 are closed, and the servo valve 1 is electrically and automatically controlled by detecting the numerical value of the displacement sensor 14 of the test hydraulic cylinder 13, so that the hydraulic position closed-loop control of the test hydraulic cylinder 13 is realized.

The electromagnet a of the first electromagnetic valve 201 is electrified, the first normally closed logic valve 501 and the second normally closed logic valve 502 are opened, the third normally closed logic valve 503 and the fourth normally closed logic valve 504 are closed, and the servo valve 1 is electrically and automatically controlled by detecting the numerical values of the first pressure sensor 1101 and the second pressure sensor 1102, so that the pressure closed-loop control of the test hydraulic cylinder 13 is realized.

2) Closed-loop control of hydraulic position and pressure of quick stop valve 3 on test hydraulic cylinder 13

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally closed logic valve 503 and the fourth normally closed logic valve 504 are opened, the first normally closed logic valve 501 and the second normally closed logic valve 502 are closed, the quick stop valve 3 is electrically and automatically controlled by detecting the value of the displacement sensor 14 of the test hydraulic cylinder 13, and the hydraulic position closed-loop control of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable throttler 801 and the second adjustable throttler 802.

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally-closed logic valve 503 and the fourth normally-closed logic valve 504 are opened, the first normally-closed logic valve 501 and the second normally-closed logic valve 502 are closed, the quick stop valve 3 is electrically and automatically controlled by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102, and the closed-loop control of the pressure of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802.

Electromagnets a, b, c and d of the quick stop valve 3 are in a non-leakage stop state by means of acting force of a spring in the valve body in a power-off state to realize the function of maintaining the position and force of the clamping test hydraulic cylinder 13, so that the energy consumption of the system is greatly reduced, and the reliability of the system is improved.

3) Closed-loop control of the hydraulic position and pressure of the test hydraulic cylinder 13 by the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally closed logic valve 503 and the fourth normally closed logic valve 504 are opened, the first normally closed logic valve 501 and the second normally closed logic valve 502 are closed, the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 are electrically and automatically controlled by detecting the numerical value of the displacement sensor 14 of the test hydraulic cylinder 13, and the hydraulic position closed-loop control of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802.

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally-closed logic valve 503 and the fourth normally-closed logic valve 504 are opened, the first normally-closed logic valve 501 and the second normally-closed logic valve 502 are closed, the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402 are electrically and automatically controlled by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102, and the closed-loop control of the pressure of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802.

The first hydraulic control check valve 701 is in a non-leakage stop state by means of acting force of a spring inside the valve body in the power-off state of the first electromagnetic ball seat valve 401 and the second electromagnetic ball seat valve 402, so that the position and force holding function of the clamping test hydraulic cylinder 13 is realized, the energy consumption of the system is greatly reduced, and the reliability of the system is improved.

4) Closed-loop control of hydraulic position and pressure of test hydraulic cylinder 13 by third electromagnetic valve 203

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally-closed logic valve 503 and the fourth normally-closed logic valve 504 are opened, the first normally-closed logic valve 501 and the second normally-closed logic valve 502 are closed, the third electromagnetic valve 203 is electrically and automatically controlled by detecting the value of the displacement sensor 14 of the test hydraulic cylinder 13, and the hydraulic position closed-loop control of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802.

The electromagnet b of the first electromagnetic valve 201 is electrified, the third normally-closed logic valve 503 and the fourth normally-closed logic valve 504 are opened, the first normally-closed logic valve 501 and the second normally-closed logic valve 502 are closed, the third electromagnetic valve 203 is electrically and automatically controlled by detecting the values of the first pressure sensor 1101 and the second pressure sensor 1102, and the closed-loop control of the pressure of the test hydraulic cylinder 13 is realized by adjusting the flow areas of the first adjustable restrictor 801 and the second adjustable restrictor 802.

The second hydraulic control check valve 702 is in a non-leakage stop state by means of the acting force of a spring in the valve body in the power-off state of the third electromagnetic valve 203 to realize the position and force maintaining function of the clamping hydraulic cylinder 13, so that the energy consumption of the system is greatly reduced, and the reliability of the system is improved.

A, B, P, T shown in FIG. 1 of the invention are all oil ports, X is a control oil port, Y is an oil discharge port, P, T is connected with pressure oil ports P0 and T0 from a hydraulic station respectively, and a, b, c and d are electromagnets, which are not described in detail herein.

The invention provides a dynamic and static simulation test system and a method for hydraulic position and pressure closed-loop control, which are particularly suitable for simulation tests for hydraulic position and pressure closed-loop control under light pressure in the field of continuous steel casting, are used for simulating the actual working condition under light pressure, provide basis for parameter design of hydraulic position and pressure closed-loop control, reduce design errors, improve design efficiency and avoid safety production accidents caused by the design errors; the hydraulic position and pressure closed-loop control dynamic and static characteristic simulation test system provided by the invention has the characteristics of high automation degree, accurate simulation working condition, safe and reliable operation, low cost and the like.

According to the test method of the hydraulic position and pressure closed-loop control dynamic and static characteristic simulation test system, the servo valve, the quick stop valve, the first electromagnetic ball seat valve, the second electromagnetic ball seat valve and the third electromagnetic valve can independently realize closed-loop control over the hydraulic position and pressure of the test hydraulic cylinder, and the test method is particularly suitable for simulation tests of soft-reduction hydraulic position and pressure closed-loop control in steel making equipment.

While the preferred embodiments of the present invention have been described in detail, the present invention is not limited to the above embodiments, and various changes can be made without departing from the spirit of the present invention within the knowledge of those skilled in the art.

Many other changes and modifications can be made without departing from the spirit and scope of the invention. It is to be understood that the invention is not to be limited to the specific embodiments, but only by the scope of the appended claims. The components and structures of the present embodiments that are not described in detail are well known in the art and do not constitute essential structural elements or elements.

Claims

1. The utility model provides a hydraulic pressure position and pressure closed-loop control dynamic and static simulation test system which characterized in that: at least, including dynamic and static simulation test valve device (18), experimental pneumatic cylinder (13), displacement sensor (14), connecting rod (15), loading hydraulic cylinder (16) and loading valve device (17), connecting rod (15) both ends are connected with experimental pneumatic cylinder (13) and loading hydraulic cylinder (16) respectively, and wherein displacement sensor (14) are installed to experimental pneumatic cylinder (13) other end, the pole chamber of loading hydraulic cylinder (16) is connected with the hydraulic fluid port B of loading valve device (17), and wherein the stopper chamber of loading hydraulic cylinder (16) is connected with the hydraulic fluid port A of loading valve device (17), dynamic and static simulation test valve device is connected in experimental pneumatic cylinder (13).

2. The hydraulic position and pressure closed-loop control dynamic and static simulation test system according to claim 1, wherein: the dynamic and static state simulation test valve device (18) comprises a servo valve (1), a first electromagnetic valve (201), a second electromagnetic valve (202), a third electromagnetic valve (203), a quick stop valve (3), a first electromagnetic ball seat valve (401), a second electromagnetic ball seat valve (402), a first normally closed logic valve (501), a second normally closed logic valve (502), a third normally closed logic valve (503), a fourth normally closed logic valve (504), a fifth normally closed logic valve (505), a sixth normally closed logic valve (506), a first externally-controlled externally-leaking hydraulic control one-way valve (601), a second externally-controlled externally-leaking hydraulic control one-way valve (602), a first hydraulically-controlled one-way valve (701), a second hydraulically-controlled one-way valve (702), a first adjustable restrictor (801), a second adjustable restrictor (802), a first overflow valve (901), a second overflow valve (902), a first one-way valve (1001), a second one-way valve (1002), A first pressure sensor (1101) and a second pressure sensor (1102);

a cavity-plugging hydraulic circuit of the test hydraulic cylinder (13) is respectively connected with an oil port P of a first overflow valve (901), an oil port B of a first one-way valve (1001), an oil port B of a fifth normally-closed logic valve (505), an oil port B of a second normally-closed logic valve (502) and an oil port B of a third normally-closed logic valve (503), wherein an oil port T of the first overflow valve (901), an oil port A of the first one-way valve (1001) and an oil port A of the fifth normally-closed logic valve (505) are respectively connected with an oil return port T0 from a hydraulic station, a second pressure sensor (1102) is connected on a circuit between the cavity-plugging hydraulic circuit of the test hydraulic cylinder (13) and the first overflow valve (901) and the first one-way valve (1001), wherein an oil port A of the second normally-closed logic valve (502) is connected with an oil port B of a servo valve (1), and an oil port A of the third logic valve (503) is connected with a second adjustable restrictor (802), the second adjustable throttler (802) is respectively connected with an oil port B of a second external control leakage hydraulic control one-way valve (602), an oil port B of a first hydraulic control one-way valve (701) and an oil port B of a second hydraulic control one-way valve (702), an oil port A of the second external control leakage hydraulic control one-way valve (602) is connected with an oil port B of a quick stop valve (3), an oil port A of the first hydraulic control one-way valve (701) is connected with an oil port A of a second electromagnetic ball seat valve (402), and an oil port A of the second hydraulic control one-way valve (702) is connected with an oil port B of a third electromagnetic valve (203); a rod cavity hydraulic circuit of the test hydraulic cylinder (13) is respectively connected with an oil port P of a second overflow valve (902), an oil port B of a second one-way valve (1002), an oil port B of a sixth normally-closed logic valve (506), an oil port B of a first normally-closed logic valve (501) and an oil port B of a fourth normally-closed logic valve (504), wherein an oil port T of the second overflow valve (902), an oil port A of the second one-way valve (1002) and an oil port A of the sixth normally-closed logic valve (506) are respectively connected with an oil return port T0 from a hydraulic station, a first pressure sensor (1101) is connected on a circuit between the rod cavity hydraulic circuit of the test hydraulic cylinder (13) and the second overflow valve (902) as well as the second one-way valve (1002), wherein an oil port A of the first normally-closed logic valve (501) is connected with an oil port A of a servo valve (1), and an oil port A of the fourth logic normally-closed valve (504) is connected with a first adjustable choke (801), the first adjustable throttler (801) is respectively connected with an oil port B of the first external control leakage hydraulic control one-way valve (601), an oil port B of the first hydraulic control one-way valve (701) and an oil port B of the second hydraulic control one-way valve (702), wherein an oil port A of the first external control leakage hydraulic control one-way valve (601) is connected with an oil port A of the quick stop valve (3), wherein an oil port A of the first hydraulic control one-way valve (701) is connected with an oil port A of the first electromagnetic ball seat valve (401), and wherein an oil port A of the second hydraulic control one-way valve (702) is connected with an oil port A of the third electromagnetic valve (203);

an oil port A of the first electromagnetic valve (201) is respectively connected with control oil ports X of a third normally-closed logic valve (503) and a fourth normally-closed logic valve (504), and an oil port B of the first electromagnetic valve (201) is respectively connected with control oil ports X of a first normally-closed logic valve (501) and a second normally-closed logic valve (502);

an oil port A of the second electromagnetic valve (202) is respectively connected with control oil ports X of a fifth normally closed logic valve (505) and a sixth normally closed logic valve (506), an oil port B of the second electromagnetic valve (202) is respectively connected with control oil ports X of a first external control leakage hydraulic control one-way valve (601) and a second external control leakage hydraulic control one-way valve (602), wherein oil drainage ports Y of the first external control leakage hydraulic control one-way valve (601) and the second external control leakage hydraulic control one-way valve (602) are respectively connected with an oil return port T0 from a hydraulic station;

an oil port A of the third electromagnetic valve (203) is respectively connected with a control oil port X of the second normally-closed logic valve (502) and a control oil port X of the fourth normally-closed logic valve (504), and an oil port B of the third electromagnetic valve (203) is respectively connected with a control oil port X of the third normally-closed logic valve (503) and a control oil port X of the second normally-closed logic valve (502);

the pressure oil port P0 from the hydraulic station is respectively connected with oil ports P of the servo valve (1), the first electromagnetic valve (201), the second electromagnetic valve (202), the third electromagnetic valve (203), the quick stop valve (3), the first electromagnetic ball seat valve (401) and the second electromagnetic ball seat valve (402); an oil return port T0 from the hydraulic station is respectively connected with oil ports T of the servo valve (1), the first electromagnetic valve (201), the second electromagnetic valve (202), the third electromagnetic valve (203), the quick stop valve (3), the first electromagnetic ball seat valve (401) and the second electromagnetic ball seat valve (402).

3. The hydraulic position and pressure closed-loop control dynamic and static simulation test system according to claim 2, wherein: the test hydraulic cylinder (13) is connected with a dynamic and static simulation test valve device (18) through a high-pressure rubber pipe, wherein the high-pressure rubber pipe comprises a first high-pressure rubber pipe (1201) and a second high-pressure rubber pipe (1202);

one end of the first high-pressure rubber hose (1201) is connected with a rod cavity of the test hydraulic cylinder (13), and the other end of the first high-pressure rubber hose (1201) is connected with the servo valve (1), the first electromagnetic valve (201), the third electromagnetic valve (203), the quick stop valve (3), the first electromagnetic ball seat valve (401), the first normally closed logic valve (501), the fourth normally closed logic valve (504), the sixth normally closed logic valve (506), the first externally-controlled leakage hydraulic control one-way valve (601), the first hydraulically-controlled one-way valve (701), the second hydraulically-controlled one-way valve (702), the first adjustable restrictor (801), the second overflow valve (902), the second one-way valve (1002) and the first pressure sensor (1101) respectively;

one end of the second high-pressure rubber pipe (1202) is connected with a plug cavity of the test hydraulic cylinder (13), wherein the other end of the second high-pressure rubber pipe (1202) is connected with the servo valve (1), the first electromagnetic valve (201), the second electromagnetic valve (202), the third electromagnetic valve (203), the quick stop valve (3), the second electromagnetic ball seat valve (402), the second normally closed logic valve (502), the third normally closed logic valve (503), the fifth normally closed logic valve (505), the second externally-controlled leakage hydraulic control one-way valve (602), the first hydraulic control one-way valve (701), the second hydraulic control one-way valve (702), the second adjustable restrictor (802), the first overflow valve (901), the first one-way valve (1001) and the second pressure sensor (1102) respectively.

4. The hydraulic position and pressure closed-loop control dynamic and static simulation test system according to claim 2, wherein: the rapid stop valve (3) is integrated by four independent stop valves.

5. The hydraulic position and pressure closed-loop control dynamic and static simulation test system according to claim 2, wherein: the connecting rod (15) is provided with spherical hinge bearings at two ends and is used for connecting the test hydraulic cylinder (13) and the loading hydraulic cylinder (16).